WO2005042955A2

WO2005042955A2 - Internal combustion engine

Info

Publication number: WO2005042955A2
Application number: PCT/AT2004/000371
Authority: WO
Inventors: Georg Pogatsch; Mad Rivas Navarro; Karl Kirchweger; Andreas Janach
Original assignee: Avl List Gmbh
Priority date: 2003-11-03
Filing date: 2004-10-28
Publication date: 2005-05-12
Also published as: DE112004002081D2; WO2005042955A3; DE112004002081B4

Abstract

The invention relates to a liquid-cooled internal combustion engine comprising a cylinder head with two intake port openings and two outlet port openings per cylinder, said openings being essentially symmetrical in relation to at least one transversal plane of the cylinder head, in addition to a first cooling chamber that adjoins a fireproof cover and a second cooling chamber that at least partially adjoins the first cooling chamber. The first and second cooling chambers have a fluidic connection via at least one flow connection per cylinder.

Description

Internal combustion engine

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

Furthermore, 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. In particular in the case of highly loaded direct-injection diesel internal combustion engines with high heat input, a continuous cooling space for a cooling medium flowing through the cylinder head in the longitudinal direction does not reach in order to ensure adequate cooling of the fire deck. Inadequate heat discharge from the cylinder head can lead to distortion, leaks and cracks.

AT 005.301 Ul describes a cylinder head for a plurality of cylinders with a lower and an upper partial cooling space, the coolant in the lower partial cooling space essentially flowing transversely to the cylinder head. The coolant passes on the one hand via an annular passage around an insert tube for a fuel injection device, and on the other hand via lateral overflow openings in the region of a side wall from the lower part of the cooling space into the upper part of the cooling space. The cross-flow cooling in the lower part of the cooling chamber enables uniform cooling of the individual cylinders. However, this arrangement has the disadvantage that targeted cooling of thermally critical areas, for example the valve webs between the outlet valves, is not possible, and areas which are subjected to high thermal stress can only be insufficiently cooled.

From CH 614 995 A a single cylinder cylinder head for a diesel internal combustion engine is known, 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.

From US 4,304,199 A a cylinder head for several cylinders of a diesel internal combustion engine is known, 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.

From EP 1 126 152 A2 a cylinder head with a lower and an upper partial cooling space is known, the flow transfer between the lower and upper partial cooling space being formed by an annular gap between an injection nozzle collar and an intermediate deck, the entire coolant flow flowing through this gap. This arrangement also has the disadvantage that targeted cooling of thermally critical areas, for example the valve webs between two outlet valves, is not possible and so-called "hot spots" are only insufficiently cooled.

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. There is no dominant cross-flow in the lower part of the cold room. Although 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.

From JP 2000-310157 A 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.

Furthermore, from the Austrian utility model application GM 741/2002 a cylinder head with a lower and an upper partial cooling space is known, with bypass openings between the insert pipe and gas exchange channels in the intermediate deck, which are designed as castings made Bores of the receiving bore for the insert tube are formed. However, these bypass openings are relatively difficult to manufacture.

Further cylinder heads with two cooling compartments and an overflow duct in the area of the injection nozzle are known from the publications GB 828 014 A, DE 35 164 53 A and US 4,889,080 A.

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. In the intake-side cooling space, 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. In the area of the longitudinal partition wall to the outlet-side cooling space, 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.

According to the invention, this is achieved in that 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. Furthermore, it is advantageous if 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. In a further embodiment of the invention, it can be provided that 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. Coming from the cooling jacket of the cylinder block, 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. On the other hand, the coolant flows from the first cooling space directly into the second cooling space via the second radial bore. In order to ensure sufficient cooling of the thermally highly stressed parts around the outlet duct openings, it is advantageous if 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.

In a further embodiment, it can be provided that 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.

In a particularly preferred embodiment variant of the invention it is provided that 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.

To increase the rigidity of the cylinder head, it is particularly advantageous if 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.

In order to further improve the cooling, it is provided according to the invention that 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. Between the gas exchange channels and the insert tube, in particular within an area spanned by the valve axes of the gas exchange valves, 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. In order to enable a precisely defined cooling between the gas exchange channels, it is particularly advantageous if 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.

In certain embodiments of the cylinder head, a coolant flow between two adjacent subchannels can be advantageous for cooling thermally critical areas. In order to make this possible, 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.

In order to enable particularly good heat dissipation from thermally critical areas of the fire deck, in particular the valve webs between two adjacent gas exchange valves, 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.

In order to improve the cooling in the area of the exhaust ducts, it is further provided according to the invention that 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.

It is preferably provided that 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. On the outlet side, 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. The fact that the first and second cooling compartments can be produced by separate cast cores simplifies the manufacturing effort. The invention is explained in more detail below with reference to the figures. Show it

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.

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.

9 shows the cylinder head in a section along the line IX-IX in FIG. 3;

Figure 10 shows the cylinder head in a section along the line X-X in Fig. 3.

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.

14 shows the cylinder head in a section along the line XIV-XIV in FIG. 7;

15 shows a water core arrangement for the cylinder head according to the invention in an oblique view from below;

16 shows the water core arrangement in an oblique view from above;

17 shows the water core arrangement in a side view;

18 shows the water core arrangement in a view from below; 19 shows the water core arrangement in a section along the line XIX-XIX in FIG. 18;

Figure 20 in the water core assembly in a section along the line XX-XX in Fig. 18 .;

21 shows the water core arrangement in a section along the line XXI-XXI in FIG. 20;

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 .;

24 shows the water core arrangement in a section along the line XXIV-XXIV in FIG. 18;

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;

27 shows the water core arrangement in a section along the line XXVII-XXVII in FIG. 18;

28 shows the water core arrangement in a side view;

29 shows the cylinder head according to the invention in a section along the line XXIX-XXIX in FIG. 30;

30 shows the cylinder head in a section along the line XXX-XXX in FIG. 29;

31 shows the cylinder head in a section along the line XXXI-XXXI in FIG. 29;

32 shows the cylinder head in a section along the line XXXII-XXXII 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;

36 shows the cylinder head in a section along the line XXXVI-XXXVI in FIG. 30;

37 shows the cooling rooms of a cylinder head according to the invention in an oblique view;

38 is a top view of the cold stores;

39 is a side view of the cold stores;

40 shows the cold rooms in section along the line XL-XL in FIG. 39; and

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 εi 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). Furthermore, 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. In addition, 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.

In the area of transverse planes ε ₂ on the camshaft axes in the area of the bores 27 for the cylinder head screws, 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. During the casting process, 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. Furthermore, 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. Furthermore, 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.

109 in the vicinity of an insert tube 110, indicated by dashed lines in FIGS. 29 and 34, which serves to accommodate a fuel injection device, not shown in any more detail. 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

110 limited. As can be seen from FIGS. 30, 31, 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. As an alternative to this, a 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.

In order to enable ventilation and outflow of steam bubbles from the lower partial cooling space 105 even when the internal combustion engine is tilting, 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. In order to enable optimal cooling of the valve webs 130, 131 between the two inlet valves 124 and the two outlet valves 125, and between the inlet and outlet valves 116, 117, 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 On an end face 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.

As can be seen from FIG. 32, 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.

As can be seen from FIG. 39, 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. There, 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.

The patent claims submitted with the application are proposals for formulation without prejudice for the achievement of further patent protection. The applicant reserves the right to claim further features previously only disclosed in the description and / or drawings. Back-references used in sub-claims indicate the further development of the subject matter of the main claim through the features of the respective sub-claim; they are not to be understood as a waiver of the achievement of independent, objective protection for the characteristics of the related subclaims.

However, the subjects of these subclaims also form independent inventions which have a design which is independent of the subjects of the preceding subclaims.

The invention is also not restricted to the exemplary embodiment (s) of the description. Rather, numerous changes and modifications are possible within the scope of the invention, in particular those variants, elements and combinations and / or materials which e.g. are inventive by combining or modifying individual features in connection with the features or elements or procedural steps described in the general description and embodiments and the claims and contained in the drawings and lead to a new object or to new procedural steps or procedural step sequences through combined features, also insofar as they relate to manufacturing, testing and working processes.

Claims

PATENT CLAIMS

1. Liquid-cooled internal combustion engine with at least one cylinder head, with at least two inlet and two outlet channel 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 Bounding 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 through-opening, and wherein a receiving shaft for an injection device, which is molded with the cylinder head, at least partially from is surrounded by the second cooling space, characterized in that 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 egg NEN connecting channel is connected.

2. Internal combustion engine, in particular according to claim 1, characterized in that the annular cooling space is at least one first radial bore in a region directly adjacent to the fire deck area of the cylinder head with at least one passage opening and / or with the first cooling space.

3. Internal combustion engine, in particular according to claim 1 or 2, characterized in that at least one first connection channel is arranged in the region between an inlet and an outlet channel, a first connection channel being preferably provided between each inlet and outlet channel.

4. Internal combustion engine, in particular according to claims 1 to 3, characterized in that at least one second connecting channel, which is formed essentially in the direction of the cylinder axis, is arranged at least between two inlet channels.

5. Internal combustion engine, in particular according to one of claims 1 to 4, characterized in that the first cooling space is connected to the second cooling space via at least one second radial bore, wherein the second radial bore is preferably arranged directly above the first radial bore.

6. Internal combustion engine, in particular according to claim 5, characterized in that the second radial bore is arranged in the region between the outlet channels, the second radial bore preferably opening into an extension of the second cooling space formed between the outlet channels.

7. Internal combustion engine, in particular according to one of claims 1 to 6, characterized in that the first and / or second radial bore is arranged substantially parallel to the cylinder head plane.

8. Internal combustion engine, in particular according to one of claims 1 to 7, characterized in that the first and / or second radial bore is arranged on the outlet side, preferably in a region between the two outlet channels and the fire deck.

9. Internal combustion engine, in particular according to one of claims 1 to 8, characterized in that an overflow channel is arranged between the first and second cooling chamber on both sides of the outlet channels in the region of the outlet flange surface.

10. Internal combustion engine, in particular according to one of claims 1 to 9, characterized in that the first cooling space is formed by a first water core.

11. Internal combustion engine, in particular according to one of claims 1 to 10, characterized in that the second cooling space, the annular cooling space and at least one connecting channel between the annular cooling space and the second cooling space is formed by a second water core.

12. Internal combustion engine, in particular according to one of claims 1 to 11, characterized in that in the area of at least one transverse plane through the at least one bore for a cylinder head screw at least one support column is arranged with a preferably cross-shaped cross section.

13. Water core arrangement for producing a cylinder head for a liquid-cooled internal combustion engine, with two inlet and two outlet channel openings per cylinder, which are 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 on the first cooling space bordering the second cooling space, the first and second cooling space being fluidly connected to one another via at least one flow connection per cylinder, the first cooling space having at least one passage opening with a cooling jacket of a cylinder is connectable to the housing and a receiving shaft for the injection device, which is molded with the cylinder head, is at least partially surrounded by the second cooling space, characterized in that the water core arrangement has a first water core for forming the first cooling space and a second water core for forming the second cooling space, one of which is the annular cooling space bordering the fire deck and surrounding the receiving shaft, and at least one connecting channel between the annular cooling space and the second cooling space are formed by corresponding shaped areas of the second water core.

14. Water core arrangement according to claim 13, characterized in that a first passage opening in the fire deck is formed by a shaped area of the second water core and at least one second passage opening directly connected to the first cooling space is formed by a shaped area of the first water core.

15. Water core arrangement according to claim 13 or 14, characterized in that at least one overflow channel in the area of the outlet side, preferably two overflow channels on both sides of a common outlet channel, is formed by a shaped area of the first water core.

16. Water core arrangement according to one of claims 13 to 15, characterized in that at least one first connecting channel in the area between an inlet and an outlet channel is formed by a shaped area of the first water core.

17. Water core arrangement according to one of claims 13 to 16, characterized in that a second connecting channel in the area between two inlet channels is formed by a shaped area of the second water core.

18. Water core arrangement according to one of claims 13 to 17, characterized in that a shaped area for an extension of the second cooling space between the outlet channels is formed by the second water core.

19. Manufacturing method for a cylinder head for a liquid-cooled internal combustion engine, with two inlet and two outlet channel openings per cylinder, which are 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 Bounding second cooling space, the first and second cooling space with each other via at least one flow connection are connected to the flow, the first cooling space being connectable to a cooling jacket of the 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, characterized in that the first cooling space is surrounded by a first water core and the second cooling space, as well as an annular cooling space adjacent to the fire deck around the central receiving shaft for a central injection device, and at least one connecting channel between the annular cooling space and the second cooling space is formed by a second water core.

20. The method according to claim 19, characterized in that after the casting process, a passage opening and / or the first cooling space with the annular cooling space through a radial bore in the cylinder head between the exhaust ports and the fire deck are connected to each other.

21. The method according to claim 19 or 20, characterized in that between the outlet channels and the first radial bore at least a second radial bore is formed in the cylinder head, which fluidly connects the first cooling space and the second cooling space, preferably the second radial bore in the Extension of the second cold room opens.

22. Liquid-cooled multi-cylinder internal combustion engine with at least one cylinder head with at least two gas exchange channels per cylinder controlled by intake and / or exhaust valves, 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 space on the fire deck side and one at This upper partial cooling chamber adjoining in the direction of the cylinder axis is subdivided, the lower and upper partial cooling chambers 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 in the lower part of the cooling chamber opens out at least one inflow opening per cylinder for the coolant and from the upper part of the cooling chamber at least one outflow opening for the coolant ht, characterized in that the cast-overflow duct produced on the cylinder head side is delimited at least by one wall of a gas exchange duct, the walls of the overflow duct on the cylinder head side preferably being formed only by the walls of at least two gas exchange ducts.

23. Internal combustion engine, in particular according to claim 22, characterized in that the overflow channel is divided in the flow direction by at least one web, preferably by a plurality of webs, in particularly preferably four sub-channels.

24. Internal combustion engine, in particular according to claim 22 or 23, characterized in that the overflow channel essentially has a star-shaped profile.

25. Internal combustion engine, in particular according to claim 23 or 24, characterized in that the webs are designed as a guide for the insert tube, the insert tube preferably abutting at least one web.

26. Internal combustion engine, in particular according to one of claims 23 to 25, characterized in 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.

27. Internal combustion engine, in particular according to one of claims 22 to 26, wherein a radial flow channel is formed between each two gas exchange channels in the lower partial cooling space, characterized in that in the region of the flow channel between two gas exchange channels, a flow guide wall connected to the intermediate deck is arranged, which the radial Coolant flowing in the direction of the overflow duct in the lower cooling compartment is diverted to the fire deck.

28. Internal combustion engine, in particular according to one of claims 22 to 27, characterized in that at least within an area spanned by the valve axes of the gas exchange valves, the cylinder head is designed without an intermediate cover.

29. 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 on a fire deck and a second cooling space bordering on the first cooling space, the first and second cooling space being separated by at least one transition opening per cylinder is fluidly connected to one another, 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, characterized in that at least one first opening and at least one transition opening in the area of a normal on the crank shaft-shaped engine transverse plane is arranged between two adjacent cylinders, a longitudinal wall being arranged in the first cooling space in the area between two outlet channel openings of adjacent cylinders and a coolant channel between the outlet channels in the area of the outlet channel openings of each cylinder.

30. Internal combustion engine according to claim 29, characterized in that the first and second cooling space are arranged one above the other in the region of the outlet channels.

31. Internal combustion engine according to claim 29 or 30, characterized in that the second cooling space substantially has 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 ,

32. Internal combustion engine according to one of claims 29 to 31, characterized in that on the inlet side of the first and second cooling space are separated from one another by at least one intermediate wall.

33. Internal combustion engine according to one of claims 29 to 32, characterized in that the transition opening between the first and second cooling space is drilled.

34. Internal combustion engine according to one of claims 29 to 33, characterized in that the first cooling space on the one hand and the second cooling space on the other hand can be produced by means of independent casting cores.

35. Internal combustion engine according to one of claims 29 to 34, characterized in that the first and second cooling space in the region of the outlet side have substantially the same height.