CN108167085A - Cylinder head - Google Patents
Cylinder head Download PDFInfo
- Publication number
- CN108167085A CN108167085A CN201711276745.0A CN201711276745A CN108167085A CN 108167085 A CN108167085 A CN 108167085A CN 201711276745 A CN201711276745 A CN 201711276745A CN 108167085 A CN108167085 A CN 108167085A
- Authority
- CN
- China
- Prior art keywords
- cylinder
- cylinder head
- cooling chamber
- axis
- bore axis
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 238000001816 cooling Methods 0.000 claims abstract description 77
- 238000002485 combustion reaction Methods 0.000 claims description 5
- 230000002093 peripheral effect Effects 0.000 claims description 4
- 239000004744 fabric Substances 0.000 claims 1
- 238000000034 method Methods 0.000 abstract 1
- 239000002826 coolant Substances 0.000 description 14
- 230000000694 effects Effects 0.000 description 6
- 230000035882 stress Effects 0.000 description 6
- 239000000463 material Substances 0.000 description 4
- 230000008646 thermal stress Effects 0.000 description 3
- 238000007789 sealing Methods 0.000 description 2
- 230000007704 transition Effects 0.000 description 2
- 238000009825 accumulation Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 239000012141 concentrate Substances 0.000 description 1
- 239000000498 cooling water Substances 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 239000003507 refrigerant Substances 0.000 description 1
- 239000007921 spray Substances 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Classifications
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- 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
- F02F1/38—Cylinder heads having cooling means for liquid cooling the cylinder heads being of overhead valve type
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P3/00—Liquid cooling
- F01P3/02—Arrangements for cooling cylinders or cylinder heads
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P3/00—Liquid cooling
- F01P3/12—Arrangements for cooling other engine or machine parts
- F01P3/14—Arrangements for cooling other engine or machine parts for cooling intake or exhaust valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P3/00—Liquid cooling
- F01P3/12—Arrangements for cooling other engine or machine parts
- F01P3/16—Arrangements for cooling other engine or machine parts for cooling fuel injectors or sparking-plugs
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P3/00—Liquid cooling
- F01P3/02—Arrangements for cooling cylinders or cylinder heads
- F01P2003/024—Cooling cylinder heads
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Cylinder Crankcases Of Internal Combustion Engines (AREA)
Abstract
The present invention relates to a kind of cylinder head of liquid-cooled engine, the cylinder head (1) has cooling cavity structure (5), it abuts fire-proof plate (3), and the intermediate plate (4) by being basically parallel to fire-proof plate arrangement is divided into lower part cooling chamber and top cooling chamber on fire-proof plate side, the direction of top cooling chamber along cylinder-bore axis is arranged on the side of the intermediate plate of fire-proof plate, and top cooling chamber (5b) and lower part cooling chamber (5a) flow connection via at least one overflow openings extended around cylinder-bore axis, the overflow openings, which are preferably arranged in, receives near sleeve.There is the cylinder head most preferably cooled down to high heat load region the purpose of the present invention is to provide a kind of.This purpose is realized by such method：For overflow openings at least one ring segment part (6a) annularly extended around cylinder-bore axis and derived from the protrusion part (6b) of ring segment part, protrusion part deviates from cylinder-bore axis in radial directions.
Description
Technical field
The present invention relates to the cylinder head of liquid-cooled engine, wherein cylinder head has cooling cavity structure, and cooling cavity structure is adjacent
Fire-proof plate is connect, and the intermediate plate by being basically parallel to fire-proof plate arrangement is divided into lower part cooling chamber and top on fire-proof plate side
Cooling chamber, the direction of middle and upper part cooling chamber along cylinder-bore axis are arranged on the side of the intermediate plate of fire-proof plate, and on
Portion's cooling chamber and lower part cooling chamber flow connection via at least one overflow openings extended around cylinder-bore axis, and overflow openings are excellent
Selection of land, which is arranged in, receives on sleeve.The invention further relates to the internal combustion engines with this cylinder head.
Background technology
Known a kind of cylinder head from 005 939 U1 of AT of applicant, wherein cooling agent is via intermediate plate and in being used for
The annular overflow openings received between sleeve of center portion part flow into lower part cooling chamber from top cooling chamber.It is cold from lower part cooling chamber
But agent is discharged into the cooling chamber of crankcase via overflow openings.In this case, air valve bridge is moved through to uniform flow, still
There is no any special directional effect, this can cause cooling effect to be damaged in some applications.503 182 A2 of AT show phase
As solution.
In 510 857 B1 of AT, flow channel is set between top cooling chamber and lower part cooling chamber, flow channel exists
Central area has annular or the entrance opening of ring segment shape.Therefore seek to the local heat demand of subsequent air valve bridge access
It adapts to, to improve the heat dissipation in the region of exhaust valve seat and air valve bridge.
Known arrangement has the disadvantage that, i.e., may only insufficiently adapt to the larger region of heat load to cylinder head
It is cooled down, this can be proved to be necessary in some applications.Assignment of traffic across different radial cooling channels can be with
Only set by the size of the overflow openings to cylinder shell.Therefore, the diameter of the radial cooling channels of entrance side and outlet side
It is equally cooled to cooling duct, but this is unfavorable for the Temperature Distribution on fire-proof plate.It is generated not on fire-proof plate
Uniform Temperature Distribution leads to the material stress in cylinder head.Simultaneously as the reason of cylinder head intensity, it can be by overflow openings
Cross-sectional area only widen limited extension so that it can lead to the insufficient or unfavorable pressure condition of cooling agent.
Further, since cooling water flows through overflow openings to fire-proof plate in vertical direction, and then flow directly into and radially cool down
Channel, so can not possibly have around the target flowing for receiving sleeve in the cooling chamber of lower part by circular ring shape overflow openings.
Invention content
The purpose of the present invention is avoiding these shortcomings, and ensure fire-proof plate and the height of sleeve is received to be heated stress area
Best cooling.
The purpose realizes that wherein overflow openings have around cylinder axis by the cylinder head according to the present invention being initially mentioned
At least one round ring segment part of wire loop extension and derived from the circle ring segment part and in radial directions away from cylinder axis
The protrusion part of line.In other words, therefore, overflow openings have first part and second part, and first part surrounds cylinder axis
Line is extended in a manner of round ring segment, and second part, derived from the first part, which is designed in radial direction side
Deviate from the radially protruding part of cylinder-bore axis upwards.
Circle ring segment in the sense of the present invention is circle (shape) ring segment extended on the angular range less than 360 °.
For purposes of this disclosure, cylinder-bore axis is interpreted as to the longitudinal center axis of cylinder, the cylinder-bore axis is substantially
It is orthogonal to fire-proof plate or the extension of cylinder head sealing plane.
Due to the limited extension of ring segment part and protrusion part, so increasing in transition part of the flow velocity between cooling chamber
Add, and increase the flow thus concentrated.Especially because protrusion part so that on fire-proof plate and in air valve bridge range
The cooling in high heat load region increases, and therefore temperature reduces.
In the variant of the present invention, ring segment part extends around cylinder-bore axis in first angle, this first jiao
Degree is between 20 ° and 180 °, preferably between 30 ° and 90 °, and more preferably between 40 ° to 50 °.It encloses protrusion part
Second angle is extended through around cylinder-bore axis, the second angle is between 5 ° and 45 °, preferably between 5 ° and 20 °.It is suitable
Ground, second angle are less than first angle.
When since the overflow openings receiving sleeve are arranged on the direction of exit passageway, preferably two exhaust
It is particularly advantageous when extending between door.Therefore, the entire cooling agent flowing in the cooling chamber of top concentrates on outlet side, and real
The improved cooling of exit passageway wall and exhaust valve guide part is showed.Further, since the concentration by outlet side flows, so logical
The flow for crossing entrance side is slightly reduced.This causes the temperature of entrance air valve bridge slightly elevated, this leads to the temperature on entire fire-proof plate
It is that degree level balances very much as a result, and material stress therefore can be greatly reduced.
If the width of ring segment part extended in radial directions is less than the protrusion part extended in peripheral direction
Width, then can realize the flowing especially concentrated with good cooling effect.In other words, the width of ring segment part
It is defined as its extension in radial directions, and the width for protruding part is defined as around cylinder-bore axis at periphery (circumference)
Extension on direction.
Ring segment part has than elongation in radial directions (in radial direction side in a circumferential direction around cylinder-bore axis
Upward elongation and the hereinafter referred to as width of ring segment part) big elongation (hereinafter referred to as ring segment portion
The length divided).In contrast, protrusion part has than elongation in a circumferential direction in radial directions around cylinder-bore axis
(elongation in a circumferential direction is hereinafter referred to as protruding the width of part) big elongation (hereinafter referred to as protrusion
The length divided).When overflow openings in a circumferential direction, are substantially extending to two differences around cylinder-bore axis from cylinder-bore axis
Between two connecting lines of each valve axis in valve, preferably from cylinder-bore axis to the exhaust valve of two exhaust valves
When extending between the connecting line of axis, the arrangement for being conducive to flow regime is obtained.In the variant of the present invention, part is protruded
Fire-proof plate extension is orthogonal to along valve symmetrical plane, the valve symmetrical plane is between two valve axis, preferably in each row
Extend between the valve axis of valve.Advantageously, the extension for protruding part is terminated in radial directions between two valve axis
Connection plane front.It is thereby achieved that the balance beneficial between the cooling effect of cylinder head and intensity.
Advantageously, protrusion lease making is by extending through the radial cooling channels of exhaust valve bridge in the side far from cylinder-bore axis
It upwardly extends.Therefore, the height that can particularly effectively cool down exhaust valve bridge is heated stress area.
For good cooling, if overflow openings are via the distribution ring being arranged in around receiving sleeve in the cooling chamber of lower part
Cooling duct is fluidly coupled to, then is also advantageous, these cooling ducts are far from the distribution ring radial directed in the cooling chamber of lower part.
Therefore, the receiving sleeve flow which can in a targeted way in the cooling chamber of lower part.
Internal combustion engine of the purpose of the present invention also by having the beginning of the cylinder head of one in above-mentioned variant to refer to
To realize.
Description of the drawings
The present invention is explained in greater detail below with reference to the non-restrictive illustrative embodiment being shown in the drawings, wherein：
Fig. 1 shows the schematic diagram along the cylinder head according to the present invention intercepted of the line I-I in Fig. 2；
Fig. 2 illustrates the cylinder head of Fig. 1 with the section along the top of the line II-II in Fig. 1 cooling chamber region；And
Fig. 3 illustrates the cylinder head of Fig. 1 with the section along the lower part of the line III-III in Fig. 1 cooling chamber region.
Specific embodiment
Fig. 1 shows the liquid-cooled cylinder head 1 at least one cylinder (not shown) in the section of internal combustion engine 100, should
Cylinder is arranged along cylinder-bore axis 2.Cylinder head 1 has fire-proof plate 3 on the direction of the combustion chamber of cylinder.Intermediate plate 4 is by cooling chamber
Structure 5 is divided into the top cooling chamber 5b adjacent close to the lower part cooling chamber 5a of fire-proof plate 3 and on the direction of cylinder-bore axis 2.
Intermediate plate 4 has per at least one overflow openings 6 of cylinder, between top cooling chamber 5b and lower part cooling chamber 5a
Flowing connection, overflow openings plate 4 formed between and receive sleeve 7 between.Sleeve 7 is received for example for fuel to be received to spray
Jet device or spark plug, and substantially concentrically arranged with cylinder-bore axis 2.According to fig. 2, the overflow since cylinder-bore axis 2
Opening 6 is adjacent in radial directions to receive sleeve 7, and have round ring segment part 6a, the circle ring segment portion according to the present invention
Point 6a is at least partly around cylinder-bore axis 2 or sleeve 7 is received to extend, and overflow openings 6 have and extend in radial directions
Other protrusion part 6b.In the embodiment as top-down cooling, i.e., when cooling agent is flowed into from top cooling chamber 5b
During the cooling chamber 5a of lower part, particularly with height thermal stress region, the advantageous distribution of cooling agent and cooling can be realized.
Ring segment part 6a has the shape of round ring segment and surrounds cylinder-bore axis 2 or receive sleeve 7 along the circumferential direction
Extend on first angle α.First angle α between 20 ° and 180 °, wherein, in the illustrated exemplary embodiment, realize big
About 65 ° of angle.Generally radially extending protrusion part 6b along the circumferential direction extends on second angle β, the second angle
Between 5 ° and 45 °, wherein implementing about 16 ° in the illustrated exemplary embodiment.
Second angle β is preferably smaller than first angle α.In this way, cooling agent can be directed into a targeted way
By the region of the valve axis of high heat load, particularly at outlet side (exhaust side).
In addition to above-mentioned other than the angular range of cylinder-bore axis 2 in a circumferential direction, it is also necessary to consider from cylinder-bore axis 2
The extension in radial directions started：In all embodiment variants, ring segment part 6a is in circumferencial direction (peripheral direction)
The upper extension with than bigger in radial directions.In this case, extension in radial directions is ring segment part 6a
Width.It can be differently designed to according to embodiment variant by part 6b is protruded：The width of part 6b is protruded, i.e., it surrounds gas
The elongation of cylinder axis 2 in a circumferential direction can less than, greater than or equal to protrusion part 6b in radial direction (from cylinder-bore axis
2 start) on elongation.With in exemplary embodiment shown in Fig. 3, protruding the width of part 6b substantially etc. according to fig. 2
In the length, i.e., elongation in radial directions.If as implemented in the illustrated exemplary embodiment, in radial direction
The width of the ring segment part 6a of upper extension is less than the width of protrusion part 6b extended in a circumferential direction around cylinder-bore axis 2
Degree, then can realize the advantageous refrigerant distribution when flowing through overflow openings 6.
For the pressure loss when flowing through overflow openings 6 and height be heated stress area (such as receive sleeve 7
And air valve bridge) in cooling effect between realize possible optimum balance, the size selection of overflow openings 6 is as follows：Overflow openings
6, particularly ring segment part 6a is arranged between two connecting line A, this two connecting line A reach two not from cylinder-bore axis 2
With corresponding valve axis 8a, 8b of valve.In principle, these can be exhaust valve axis 8a and inlet valve axis 8b or
The corresponding connecting line A of exhaust valve axis 8a and inlet valve axis 8b can also be extended into.However, shown according to fig. 2
In exemplary embodiment, connecting line A is arranged between cylinder-bore axis 2 and exhaust valve axis 8a.This is favourable, because operating
Period highest thermal stress is appeared on outlet side (exhaust side).Corresponding valve axis 8a, 8b are connected to cylinder by connecting line A
Axis 2.Meanwhile it (is in the illustrated exemplary embodiment, to arrange to protrude part 6b along between two valve axis 8a, 8b
Between valve axis 8a) the valve symmetrical plane Z of extension is orthogonal to fire-proof plate 3 and extends.In this case, valve symmetrical plane
Z is orthogonal to fire-proof plate 3 or the extension of cylinder head sealing plane, and is parallel to valve axis 8a, 8b extension by cylinder-bore axis 2.
In radial directions, the extension of overflow openings 6, particularly protrusion part 6b end at and valve symmetrical plane Z associated two
The front of connecting line between valve axis 8a, 8b, in the illustrated exemplary embodiment, two valve axis are exhaust valve
Axis 8a.
Attached drawing shows the flowing of the cooling agent in cylinder head 1 according to the present invention by arrow P.Corresponding in Fig. 1
Arrow P, cooling agent enter top cooling chamber 5b, then from pressure source (not shown), such as coolant pump across coolant entrance
Overflow openings 6 are flowed through in vertical direction and enter lower part cooling chamber 5a, and wherein cooling agent is directly impacted on fire-proof plate 3 simultaneously
Cool down fire-proof plate 3.
It is radially cooled down as shown in figure 3, cooling agent is assigned to such as four in the cooling chamber 5a of lower part via distribution ring 10
Channel 9a, 9b, 9c, 9d, and flow through opening 11a, 11b, 11c, 11d and travel further into crankcase.It is understood that also may be used
To set less radial cooling channels and less opening.
Via distribution ring 10 so that can realize around the target flowing for receiving sleeve 7 and therefore receive the cold of sleeve 7
But.In this case, radial cooling channels 9a, 9b, 9c, 9d is specifically arranged in the region of air valve bridge.Due to ring
The design of the overflow openings 6 of shape section part 6a and protrusion part 6b, realizes the guiding of coolant flow, and particularly exhaust valve
The first radial cooling channels 9a between bridge 90, i.e. exit passageway 8 is cooled efficiently.Such as combine Fig. 3 as can see from Figure 2
As, protrusion part 6b via extend through the first radial cooling channels 9a of exhaust valve bridge 90, radially away from cylinder axis
The side of line 2 upwardly extends.The positioning " via " of this paper should be understood in the direction guided along cylinder-bore axis 2 far from fire-proof plate 3
On.First radial cooling channels 9a is a part of lower part cooling chamber 5a, and protrudes the region of part 6b plates 4 formed between
In.Therefore, on the one hand, on the other hand larger amount of water is supplied to the first cooling duct 9a, and, in the region of intermediate plate 4
In extraly cool down exhaust valve bridge 90.
Guiding effect is improved by positioning each opening 11a, 11b, 11c, 11d, the cooling agent from cylinder head 1 passes through this
A little openings flow into crankcase.
The geometry and the outlet side positioning of overflow openings 6 shown in exemplary embodiment in the accompanying drawings, causes
It is concentrated and is cooled down in top cooling chamber 5b and lower part cooling chamber 5a in mouth side.This realizes that the exit passageway 8 or multiple outlets are logical
Road, exhaust valve guiding piece 7a, 7b (referring to Fig. 2) and subsequent fire-proof plate 3 in the high heat load region of exhaust valve bridge 90
Best cooling.This causes the uniform temperature on entire fire-proof plate 3 horizontal, and therefore occurs relatively low material in cylinder head 1
Expect stress.Term " air valve bridge " or " exhaust valve bridge 90 " mean the material between gas exchange valve (not shown) and exhaust valve
Accumulation.Exhaust valve bridge 90 is high heat load.
Other than the variant shown in the examples in the drawings, other variants are also possible, wherein, for example, protrusion
Part 6b is arranged in the region of the air inlet raft of pontoons or the inlet/exhaust raft of pontoons or further setting is respective or is partially attached to
Protrude the ring segment part of part.
Therefore, the present invention allows the flow velocity in the transition part between cooling chamber 5a, 5b to increase, and due to this concentration
Flowing, especially because protrusion part 6b so that on fire-proof plate 3 and in the range of air valve bridge (particularly exhaust valve bridge 90)
High heat load region improved cooling, and therefore temperature reduce.It is therefore prevented that thermal stress and consequential to cylinder head
Damage.
Claims (10)
1. a kind of cylinder head of liquid-cooled engine (1), wherein, the cylinder head (1) has cooling cavity structure (5), described cold
But the adjacent fire-proof plate (3) of cavity configuration (5), and the intermediate plate (4) by being basically parallel to the fire-proof plate (3) arrangement is divided into institute
The lower part cooling chamber (5a) and top cooling chamber (5b) on fire-proof plate side are stated, wherein the top cooling chamber (5b) is along cylinder axis
The direction of line (2) is arranged on the side of the intermediate plate (4) of the fire-proof plate (3), and the top cooling chamber
(5b) and the lower part cooling chamber (5a) are flowed via at least one overflow openings (6) extended around the cylinder-bore axis (2)
Connection, the overflow openings (6), which are preferably arranged in, receives near sleeve (7), and the cylinder head (1) is characterized in that, institute
Overflow openings (6) are stated at least one ring segment part (6a) annularly extended around the cylinder-bore axis (2) and are derived from
The protrusion part (6b) of the ring segment part (6a), the protrusion part (6b) deviate from the cylinder in the radial direction described
Axis (2).
2. cylinder head (1) according to claim 1, which is characterized in that the ring segment part (6a) is around the cylinder
Axis (2) extends in first angle (α), the first angle (α) between 20 ° and 180 °, preferably 30 ° and 90 ° it
Between, and particularly preferably between 40 ° to 50 °.
3. cylinder head (1) according to claim 1 or 2, which is characterized in that the protrusion part (6b) is around the cylinder
Axis (2) extends in second angle (β), and the second angle (β) is between 5 ° and 45 °, preferably between 5 ° and 20 °.
4. cylinder head (1) according to any one of claim 1 to 3, which is characterized in that the protrusion part (6b) surrounds
The cylinder-bore axis (2) extends in second angle (β), and the second angle (β) is less than the first angle (α).
5. cylinder head (1) according to any one of claim 1 to 4, which is characterized in that it is described in the radial direction, i.e.
The width of the protrusion part (6b) upwardly extended derived from the side of the cylinder-bore axis (2) is less than what is extended in peripheral direction
The width of the protrusion part (6b).
6. cylinder head (1) according to any one of claim 1 to 5, which is characterized in that
The overflow openings (6) are substantially in the corresponding valve axis that two different air valves are reached from the cylinder-bore axis (2)
Between two connecting lines (A) of (8a, 8b), preferably in the exhaust door-hinge that two exhaust valves are reached from the cylinder-bore axis (2)
Extend in peripheral direction between the connecting line (A) of line (8a), around the cylinder-bore axis (2).
7. cylinder head (1) according to any one of claim 1 to 6, which is characterized in that the part (6b) of protruding is along gas
Door symmetrical plane (Z) is orthogonal to the fire-proof plate (3) extension, and the valve symmetrical plane (Z) is in two valve axis (8a, 8b)
Between, preferably extend between the exhaust valve axis (8a) of the exhaust valve.
8. cylinder head (1) according to any one of claim 1 to 7, which is characterized in that it is described protrusion part (6b) via
Radial cooling channels (9a, 9b, 9c, 9d) are upwardly extended in the side far from the cylinder-bore axis (2), the radial cooling channels
(9a, 9b, 9c, 9d) extends through air valve bridge, particularly outlet air valve bridge (90).
9. cylinder head (1) according to any one of claim 1 to 8, which is characterized in that the overflow openings (6) via
Distribution ring (10) is fluidly coupled to cooling duct (9a, 9b, 9c, 9d), and the distribution ring (10) is around described receiving sleeve (7) cloth
It puts in the lower part cooling chamber (5a), the cooling duct (9a, 9b, 9c, 9d) is far from the lower part cooling chamber (5a)
Distribution ring (10) radial directed.
10. one kind has the internal combustion engine (100) of cylinder head according to any one of claim 1 to 9 (1).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| ATA51113/2016A AT518998B1 (en) | 2016-12-07 | 2016-12-07 | CYLINDER HEAD |
| ATA51113/2016 | 2016-12-07 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN108167085A true CN108167085A (en) | 2018-06-15 |
Family
ID=60331516
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201711276745.0A Pending CN108167085A (en) | 2016-12-07 | 2017-12-06 | Cylinder head |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP3333398B1 (en) |
| KR (1) | KR102401326B1 (en) |
| CN (1) | CN108167085A (en) |
| AT (1) | AT518998B1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112689706A (en) * | 2018-09-14 | 2021-04-20 | Avl李斯特有限公司 | Cylinder head |
| CN115298423A (en) * | 2020-03-16 | 2022-11-04 | Avl李斯特有限公司 | Cylinder head |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11181032B2 (en) * | 2018-09-18 | 2021-11-23 | Deere & Company | Cylinder head with improved valve bridge cooling |
| AT523950B1 (en) * | 2020-06-18 | 2022-03-15 | Avl List Gmbh | Cylinder head for an internal combustion engine |
| AT526344B1 (en) | 2022-08-23 | 2024-02-15 | Avl List Gmbh | Liquid-cooled cylinder head |
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|---|---|---|---|---|
| RU2039881C1 (en) * | 1992-04-20 | 1995-07-20 | Производственное объединение "Барнаултрансмаш" | Cylinder head of internal combustion engine with liquid cooling |
| CN201306225Y (en) * | 2008-11-07 | 2009-09-09 | 无锡动力工程股份有限公司 | High-strength cylinder cover with two layers of water channels |
| CN103953454A (en) * | 2014-04-03 | 2014-07-30 | 中国北方发动机研究所(天津) | Water cavity structure of air cylinder cover of internal combustion engine |
Family Cites Families (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS63186923U (en) * | 1987-05-26 | 1988-11-30 | ||
| JP2941123B2 (en) * | 1992-08-24 | 1999-08-25 | ダイハツ工業株式会社 | Structure of cylinder head in four-valve internal combustion engine |
| JP2866259B2 (en) * | 1992-08-24 | 1999-03-08 | ダイハツ工業株式会社 | Structure of cylinder head in four-valve internal combustion engine |
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2016
- 2016-12-07 AT ATA51113/2016A patent/AT518998B1/en active
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2017
- 2017-11-16 EP EP17202118.0A patent/EP3333398B1/en active Active
- 2017-12-06 CN CN201711276745.0A patent/CN108167085A/en active Pending
- 2017-12-07 KR KR1020170167419A patent/KR102401326B1/en active IP Right Grant
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| RU2039881C1 (en) * | 1992-04-20 | 1995-07-20 | Производственное объединение "Барнаултрансмаш" | Cylinder head of internal combustion engine with liquid cooling |
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| CN103953454A (en) * | 2014-04-03 | 2014-07-30 | 中国北方发动机研究所(天津) | Water cavity structure of air cylinder cover of internal combustion engine |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112689706A (en) * | 2018-09-14 | 2021-04-20 | Avl李斯特有限公司 | Cylinder head |
| CN115298423A (en) * | 2020-03-16 | 2022-11-04 | Avl李斯特有限公司 | Cylinder head |
| CN115298423B (en) * | 2020-03-16 | 2024-02-06 | Avl李斯特有限公司 | Cylinder head |
Also Published As
| Publication number | Publication date |
|---|---|
| AT518998B1 (en) | 2018-03-15 |
| KR102401326B1 (en) | 2022-05-23 |
| KR20180065940A (en) | 2018-06-18 |
| EP3333398B1 (en) | 2020-02-12 |
| EP3333398A1 (en) | 2018-06-13 |
| AT518998A4 (en) | 2018-03-15 |
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