Liquid-cooled cylinder head

Abstract

Various embodiments of the present disclosure are directed to liquid-cooled cylinder heads. In one example embodiment, a cylinder head is disclosed including a component which extends into a combustion chamber, an upper cooling jacked, a lower cooling jacket, a plurality of valves arranged around the component, a plurality of cylinder head screws, an oil deck, a fire deck, a plurality of valve guides, and a fixed connection. The fixed connection is arranged from each valve guide to the component, and is a ring having at least one support. The support and the ring extend at least from the oil deck to the fire deck thereby hounding the combustion chamber, and the component is connected to the plurality of cylinder head screws.

Claims

1. Liquid-cooled cylinder head comprising: a component which extends into a combustion chamber, an upper cooling jacket, a lower cooling jacket, and a plurality of valves are arranged around the component, a plurality of cylinder head screws, an oil deck, a fire deck, a plurality of valve guides, and a fixed connection is arranged from each valve guide of the plurality of valve guides to the component, the fixed connection is a ring having at least one support, wherein: the support and the ring extend at least from the oil deck to the fire deck bounding the combustion chamber, the component is connected to the plurality of cylinder head screws, the at least one support forms an intake port wall and/or an exhaust port wall or is directly connected to the intake port wall and/or the exhaust port wall, and the oil deck extends in a tapered manner in a direction of the supports and is configured and arranged for introducing forces, and the oil deck encloses an angle (α) to the component which is greater than 90°.

2. The liquid-cooled cylinder head of claim 1, wherein the cylinder head screws are indirectly connected to the plurality of valve guides.

3. The liquid-cooled cylinder head of claim 1, wherein the ring radially surrounds the component, wherein the ring is connected to the support in the region of the valve guides.

4. The liquid-cooled cylinder head of claim 3, wherein the ring and the support are formed from a single piece of material.

5. The liquid-cooled cylinder head of claim 1, wherein the support extends parallel to a cylinder axis of the cylinder head.

6. The liquid-cooled cylinder head of claim 1, wherein the supports are partition walls which at least partially separate the upper cooling jacket and the lower cooling jacket.

7. The liquid-cooled cylinder head of claim 1, further including a plurality of walls, each wall positioned between two cylinder head screws of the plurality of cylinder head screws, and wherein each wall extends from the oil deck of the cylinder head to the fire deck bounding the combustion chamber.

8. The liquid-cooled cylinder head of claim 7, further including at least one rib, and wherein at least one cylinder head screw of the plurality of cylinder head screws is connected to the at least one support via the at least one rib.

9. The liquid-cooled cylinder head of claim 8, wherein the rib connects two cylinder head screws of the plurality of cylinder head screws, each via the wall, to the ring, wherein the rib is configured and arranged to introduce forces to the ring from the two cylinder head screw.

10. The liquid-cooled cylinder head of claim 8, wherein the at least one rib includes three ribs provided in each case along a cylinder axis between every two cylinder head screws of the plurality of cylinder head screws.

11. The liquid-cooled cylinder head of claim 8, further including an intermediate deck of the cylinder head a further rib arranged in the intermediate deck of the cylinder head, and wherein the at least one support is directly connected to the further rib.

12. The liquid-cooled cylinder head of claim 11, wherein the further rib is arranged in an intermediate deck of the cylinder head.

13. The liquid-cooled cylinder head of claim 8, further including at least one rib, and wherein—at least two mutually opposite cylinder head screws are each connected to a support via a rib.

14. The liquid-cooled cylinder head of claim 1, wherein the plurality of cylinder head screws include at least four cylinder head screws for connection to a cylinder block.

15. The liquid-cooled cylinder head of claim 14, wherein the plurality of cylinder head screws are arranged on a common pitch circle and the pitch circle has its center in the region of a cylinder axis.

16. The liquid-cooled cylinder head of claim 15, wherein the plurality of cylinder head screws are arranged uniformly on said pitch circle.

17. The liquid-cooled cylinder head of claim 14, wherein the plurality of cylinder head screws include six cylinder head screws for connection to a cylinder block.

18. The liquid-cooled cylinder head of claim 14, wherein the plurality of cylinder head screws include eight cylinder head screws for connection to a cylinder block.

19. The liquid-cooled cylinder head of claim 1, wherein at least two cylinder head screws of the plurality of cylinder head screws are arranged in an exhaust port wall.

20. The liquid-cooled cylinder head of claim 1, wherein at least two cylinder head screws of the plurality of cylinder head screws are arranged in an intake port wall.

21. The liquid-cooled cylinder head of claim 1, further including two intake valves, and two exhaust valves are provided, wherein at least two cylinder head screws of the plurality of cylinder head screws are arranged on an axis which mutually connects two valve bridges between intake and exhaust.

22. The liquid-cooled cylinder head of claim 1, wherein the plurality of cylinder head screws are connected by walls, wherein each wall is arranged in a plane parallel to a cylinder axis.

Description

(1) The invention is described in more detail below with reference to the non-limiting embodiments in the figures, wherein:

(2) FIG. 1 shows a liquid-cooled cylinder head according to the invention in a first embodiment in a sectional view along a normal plane through the cylinder axis;

(3) FIG. 2 shows the cylinder head in a section parallel to FIG. 1;

(4) FIG. 3 shows the cylinder head in a section along line III-III according to FIG. 1,

(5) FIG. 4 shows the cylinder head in a section along line IV-IV according to FIG. 3;

(6) FIG. 5 shows the cylinder head in a section along the line V-V according to FIG. 3;

(7) FIG. 6 shows the cylinder head in a section along line VI-VI according to FIG. 3;

(8) FIG. 7 shows the cylinder head in a section along line VII-VII according to FIG. 3;

(9) FIG. 8 shows a cylinder head according to the invention in a second embodiment in a view analogous to FIG. 2;

(10) FIG. 9 shows the cylinder head in the second embodiment in a section analogous to FIG. 3;

(11) FIG. 10 shows a section of the cylinder head with a schematic force curve in a first embodiment; and

(12) FIG. 11 shows a section analogous to FIG. 10 in a second embodiment.

DETAILED DESCRIPTION

(13) FIG. 1 shows a cooled cylinder head Z connected by six cylinder head screws 1 to 6 to a cylinder block (not shown). The resulting internal combustion engine has a cylinder. The cylinder head screws 1 to 6 have walls 7 between them. All cylinder head screws 1 to 6 form a so-called cylinder head star. In FIG. 1, walls 7 can be seen between a first cylinder head screw 1 and a fifth cylinder head screw 5 and from the latter to a third cylinder head screw 3. Furthermore, walls 7 are shown between a second cylinder head screw 2 and a sixth cylinder head screw 6 and from the latter to the fourth cylinder head screw 4. These walls 7 are oriented substantially parallel to an axis of the cylinder. An intake port E is arranged between third and fourth cylinder head screws 3, 4. An exhaust port A is arranged between first and second cylinder head screws 1, 2. It can be seen from FIG. 2 that a wall 7 is also provided between first and second cylinder head screws 1, 2 in a region above the exhaust port A and between third and fourth cylinder head screws 3, 4 in a region above the intake port E in each case. In FIG. 1, the arrows with reference sign K indicate the distribution of the force in this plane. In FIG. 2, this reference sign K is assigned to the hexagon with the cylinder head screws 1 to 6 as corner points. This represents the uniform force distribution along the walls between the cylinder head screws 1 to 6.

(14) Within the hexagon formed by cylinder head screws 1 to 6, an upper cooling jacket O for coolant, valve guides V and a component B can be seen. Four valve guides V are arranged evenly around component B and the valve guide bores of the valve guides V are arranged parallel to the axis of the cylinder. All valve guides V form a valve star. The axis of rotation of component B is also arranged parallel to the axis of the cylinder. The valve guides V and component B are connected via a ring 10 with supports 11.

(15) The cylinder head star is arranged offset to the valve star, i.e. the cylinder head screws 1 to 6 do not lie on a common straight line with the valve guides V and the component B as can be clearly seen from FIG. 1 and FIG. 2.

(16) The cylinder head screws 1 to 6 lie on a common pitch circle T and are approximately the same distance apart.

(17) The first cylinder head screw 1 and the second cylinder head screw 2 are each connected to a valve guide V via the exhaust port wall 13a and are further connected to component B via the supports 11. Similarly, the third cylinder head screw 3 and the fourth cylinder head screw 4 are each connected to a valve guide V via the intake port wall 13e and are connected to component B via the supports 11.

(18) The fifth and sixth cylinder head screws 5, 6 are arranged along an axis a which connects the two valve bridges between intake and exhaust. The valve bridges are not visible in FIG. 1.

(19) FIG. 3 shows a section along this axis a, which is also marked with line in FIG. 1. In it, it can be seen that a rib 8 leads from the fifth cylinder head screw 5 as well as from the sixth cylinder head screw 6 to the component B in an oil deck 9, and the force introduction along the arrows K is directed from the cylinder head screw 5 and 6 via the rib 8 into the component B and down via the supports 11. The ribs 8 have a thickness D in the area around the component B, where the ribs 8 merge into the ring 10, which also extends over a thickness D.

(20) The rib 8 represents a thickening of the oil deck 9, and the oil deck 9 has an angle α to the axis of rotation of the component B in the region of the rib 8, which is approximately 135°. The ribs 8 run conically to the walls 7 along the angle α just described.

(21) Similarly, the introduction of force is carried out along the arrows K along a fire deck 12 and along an intermediate deck 13. The supports 11 are arranged next to the component B in FIG. 3, are not intersected in this section and can be seen as part of the wall of the upper cooling jacket O. The upper cooling jacket O and a lower cooling jacket U are separated from each other by the intermediate deck 13.

(22) The ribs are provided in three planes, so that the force is introduced in three planes of the cylinder head: in the oil deck 9, in the intermediate deck 13 and in the fire deck 12. The ribs provided for the force introduction into the oil deck 9 are given the reference sign 8. The ribs for the force introduction in the intermediate deck 13 are given the reference sign 15 and the ribs to the fire deck 12 have the reference sign 16. In FIG. 4, the force path K from the rib 8 into the supports 11 is shown. The oil deck 9 has an average oil deck thickness d that is smaller than the thickness D of the rib 8. In FIG. 5 to FIG. 7, sections are shown along the lines V-V, VI and VII-VII shown in FIG. 3. In FIG. 5, the force path K can again be seen extending from the ribs 8 to the component B and around it in a circle to the supports 11. Two of the ribs 8 in FIG. 5 are formed by channel walls 13a and 13e. A seat ring cooling S is provided for cooling the seat rings of the valves, which can be seen in FIG. 7. This seat ring cooling S is part of the lower cooling jacket U.

(23) The ribs 8 and cylinder head screws 1 to 6 are always arranged symmetrically to each other.

(24) In embodiments with six or eight screws, some of them are directly connected to the intake port wall 13e or the exhaust port wall 13a, which is not the case when four cylinder head screws 14 are used. According to the invention, it is provided that the ribs 8 are not connected to the valve guides V. A force acting on the cylinder head Z is transmitted to the cylinder head screws 1 to 6 or 14 and from these to the ribs 8 and only then to the cylinder head Z itself, whereby a load is better distributed and deformation is avoided. The main load on the cylinder head screws 1 to 6 or 14 is distributed around the valve guide V.

(25) A second embodiment with four cylinder head screws 14 is explained below. Components with the same function have the same reference signs and only the differences are explained. For an understanding of the mode of operation, reference is made to the first embodiment in FIG. 1 to FIG. 7.

(26) A second embodiment of cylinder head Z is shown in FIG. 8. Here, the four cylinder head screws 14 are connected via walls 7. The force introduction K is carried out from the walls 7 along the ribs 8. A sectional view of the force introduction K is shown in FIG. 9.

(27) FIG. 10 and FIG. 11 show two basic embodiments of the cylinder head Z according to the invention. It can be seen that the ring 10 is arranged around the component B, which is connected to the cylinder head screw slugs and the cylinder head screws via ribs 8.

(28) It is further provided that the vertical supports 11 can merge into the channel walls 13a, 13e. If no channel walls 13a, 13b are provided, an additional rib 8, 15, 16 may be provided which directs the force K into the intermediate deck Z. The supports 11 are partially connected directly to the channel wall 13a, 13e.