• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a cylinder head for an internal combustion engine with at least an upper partial cooling chamber (O) and a lower partial cooling chamber (U), which are separated from one another by an intermediate deck (Z), with an element (1) extending into a combustion chamber that connects the intermediate deck ( Z) penetrates, at least one flow connection being formed between the two partial cooling spaces (O, U) in the area of the element (1) in order to allow the coolant to flow from the upper partial cooling space (O) to the lower partial cooling space (U). The object of the invention is to provide a cylinder head with improved cooling. This object is achieved according to the invention in that the flow connection is formed by at least one recess (2) on the element (1) which is single-walled and that the flow connection to the lower partial cooling chamber (U) tapers - preferably continuously.
    公开号:AT521514A4
    申请号:T50789/2018
    申请日:2018-09-14
    公开日:2020-02-15
    发明作者:Martin Klampfer Ing；Andreas Zurk Ing
    申请人:Avl List Gmbh；
    IPC主号:
    专利说明:

    The invention relates to a cylinder head for an internal combustion engine with at least an upper partial cooling space and a lower partial cooling space, which are separated from one another by an intermediate deck, wherein a coolant flows from the upper partial cooling space to the lower partial cooling space, with an element that extends into a combustion chamber and that penetrates the intermediate deck. wherein at least one flow connection is formed between the two partial cooling chambers in the area of the element.
    In order to keep the high temperatures in the cylinder head within the range tolerable for the material, it is customary to cool the cylinder head via cold rooms. For this purpose, it is provided that the coolant either flows through the cylinder head coming from a crankcase from the lower partial cooling space to the upper partial cooling space or, as in the present invention, flows through from the upper partial cooling space to the lower partial cooling space, which is also known as top-down cooling.
    These two different approaches result in very different flow conditions and cooling conditions in the cylinder head and in the partial cooling rooms.
    Such arrangements are known for example from AT 510 857 B1. It shows an overflow opening around a receiving plaster for a spark plug or an injection nozzle that extends into the combustion chamber. The overflow opening is predetermined by the contour of the intermediate deck and limited by the possibilities of manufacture. Post-processing of the intermediate deck after casting is no longer easy. As a result, the cooling of thermally critical areas is made more difficult, especially for cleaning up. The flows and the cooling of the intake plaster depend on the geometry of the opening in the intermediate deck.
    A similar cylinder head is also known from DE 10 2005 031 243 B4. This shows a cooling insert around a component that can represent an injector or a spark plug. This insert is designed so that it only represents an insert around the actual component or around its receiving sleeve. The cooling insert is double-walled and its outer walls essentially form a hollow cylinder around the component. This insert is also hollow inside. The coolant flows from the upper part of the cooling space through windows in the outer wall of the cooling insert into the interior of the cooling insert and towards the lower part of the cooling space. The coolant in turn flows out of the cooling insert into the lower partial cooling space through windows in the outer wall. The flow connection between the upper and lower partial cooling space is formed by the cavity between the outer and the inner wall. The disadvantage here is that the flow in the insert has undesirable turbulence because the flow in the cavity cannot be directed in a targeted manner without additional means.
    The object of the present invention is to provide a cylinder head with improved cooling.
    This object is achieved according to the invention by a cylinder head mentioned at the outset in that the flow connection is formed by at least one recess on the element which is single-walled and that the flow connection to the lower partial cooling space tapers - preferably continuously.
    As a result, it is easily possible to obtain a predeterminable flow and thus also a flow that can be influenced as required for the cylinder head.
    The recess has small dimensions compared to the size of the element, such as bores from the full element.
    It is particularly advantageous if at least one recess in the element is groove-shaped, which is open in the direction of a valve bridge and whose base is essentially aligned with the interior of the element. This allows the critical area between the valves to be cooled.
    In order to intensify this effect, it is advantageous if at least one recess is formed in the element for each valve bridge and if preferably three recesses are formed per valve bridge in the element.
    It is advantageous if the shape of the intermediate deck contributes to the tapering of the flow connection. This is particularly easy if the / 18
    Intermediate deck has a substantially conical recess in which the element is arranged. This can have a positive influence on the flow velocity around the element and advantageously increases.
    In a special embodiment it is provided that at least one channel is provided in the element, which serves for the flow connection between the upper and lower partial cooling space.
    In order to obtain the simplest possible arrangement, it is advantageous if an inlet opening of the channel is at a distance from the intermediate deck that is greater than a distance from a starting point of the recess from the intermediate deck. The same advantage arises from an embodiment in which it is provided that the channel is arranged in a radius of the element which is smaller than a radius at which the base of the recess is arranged in the element. This makes it possible to arrange the channel within the recesses, and not only the element but also the valve bridges can be cooled all around by the recess. Through the channel, which can be designed as a hole, it is possible to specifically cool the interior of the element.
    In order to achieve good cooling, it is advantageous if the channel has a diameter which has a ratio to the diameter of the element which is between 0.02 and 0.2 and preferably between 0.06 and 0.1, in particular approximately 0 , 08, is.
    From the cooling point of view, it is advantageous if, in a special embodiment, it is provided that the element to the intermediate deck has an annular gap which serves for the flow connection between the upper partial cooling space and the lower partial cooling space.
    The cooling via the annular gap can be favorably influenced if the annular gap has a width which has a ratio to the diameter of the element which is less than 0.05 and preferably less than 0.02, in particular less than 0.015.
    The same effect can be achieved if a recess has a width which has a ratio to the diameter of the element which is less than 0.2 and preferably less than 0.1, in particular about 0.06.
    / 18th
    In order to accelerate the flow and thus positively influence and improve the cooling, it is advantageous if the flow connection has an inlet cross section at a first height along the element in the area of the upper partial cooling space and the flow connection at a second height along the element in the area of the lower partial cooling chamber has an outlet cross-section and that the inlet cross-section and the outlet cross-section are in a relationship to one another that is greater than 1 and preferably greater than 1.6 and particularly preferably approximately 1.82.
    The flow is also improved if the element in the area of the flow connection in the intermediate deck has a constriction to a minimum diameter, this minimum diameter to the diameter having a ratio that is between 0.3 and 0.8, in particular between 0.4 and 0 , 6 and most preferably about 0.46.
    The invention is explained in more detail below on the basis of the explanations in the non-limiting figures. Show it:
    Figure 1 shows a detail of a cylinder head according to the invention in a first embodiment in a section along the lines I-I in Fig. 2.
    Figure 2 shows the detail of the cylinder head in a section along the line II-II in Fig. 1.
    3 shows a schematic flow profile of the cylinder head around an element; and
    Fig. 4 is a sketch of the detail analogous to Fig. 1 to 3 of a cylinder head according to the invention in a second embodiment.
    In Fig. 1 an element 1 is shown, which is arranged in a cylinder head of an internal combustion engine, not shown. In the embodiment shown, this element 1 is designed as a sleeve for receiving a spark plug. In an embodiment not shown, the element 1 can be designed to hold another component or can also be the corresponding component itself.
    Cooling with coolant is provided in said cylinder head. For this purpose, the cylinder head has an upper partial cooling space O and one of these through / 18
    Intermediate deck Z separate lower sub-refrigerator U. The upper partial cooling space O and the lower partial cooling space U have a flow connection.
    In the embodiment shown, this flow connection is formed by a plurality of recesses 2 and a channel 3 in the element 1 and by an annular gap R around the element 1. The recesses 2 form this flow connection together with a conical recess 4 in the intermediate deck Z, in which the element 1 is arranged.
    The recesses 2 are designed as grooves in the element 1, which start from a starting point A. The starting point A denotes the point at which the run-out of the groove begins, which is curved in the embodiment shown and can be straight in alternative embodiments. The starting point A of the groove is arranged in the upper partial cooling space O and is at a distance e from the intermediate deck Z. The bottom 5 of the groove that forms the recess 2 is bent or kinked.
    In the embodiment shown, the recess 2 is designed as a groove only in the upper region from the upper partial cooling space O to the region in the intermediate deck Z. The recess 2 is formed toward the lower partial cooling space U in such a way that the element 1 has a diameter D which ends in a shoulder 6 at the end of the groove. The flow connection is formed by the recess 2, which has the shape of a further annular gap. The annular gap R also merges into this further annular gap.
    After a short straight section between element 1 and the intermediate deck Z from paragraph 6 in the direction of the lower partial cooling space U, element 1 also tapers conically. The conical surface on element 1 begins at the same height as the conical surface on the intermediate deck Z. The flow cross section through which the coolant flows from the upper partial cooling chamber O into the lower partial cooling chamber U is reduced. During this transition from the straight, cylindrical surface on the element 1 to the conical surface, the element 1 has an angle α, which in the embodiment shown is approximately 40 °. In other versions, a different amount for the angle α is also possible.
    Due to the similar shape of the intermediate deck Z and the conical area on the element 1, the coolant is deflected in this area approximately by the angle α.
    / 18th
    In the area in the lower partial cooling room U, the element 1 has a minimum diameter m. In this area on element 1, the coolant in the embodiment shown is directed into the lower partial cooling space U and is thereby deflected by more than 90 °. The recesses 2 are also continued on the element 1 at the minimum diameter m. (This can be seen in more detail in FIG. 3 and is explained in more detail here.)
    In the embodiment shown, the coolant flows from the upper partial cooling space O along the arrows 8 into the uniform annular gap R, which is arranged around the element 1, and through the recesses 2 and through the channel 3 or the channels 3 into the lower partial cooling space U. Im Channel 3 and in the recesses 2, the flow is deflected at least once in the embodiment shown and the taper of the cross section increases the speed of the coolant accordingly.
    Cooling in which the main flow direction is directed from the upper partial cooling space O to the lower partial cooling space U is referred to as top-down cooling.
    At a first height H1, the flow connection, which forms the sum of channel (s) 3, recesses 2 and annular gap R, has an inlet cross section A1, and at a second height H2, the flow connection has an outlet cross section A2. Outlet cross section A2 and inlet cross section A1 have a ratio A1 / A2 to one another which is 1.8. This accelerates the flow along the height of the element 1.
    Furthermore, the arrangement of the channel 3 and the recesses 2 in the element 1 can be seen in FIG. 1. The channel 3 is arranged essentially as a bore in the direction of the axis of rotation 7 of the element 1 in a radius r1 of the element 1. The base 5 of the recess 2 is arranged essentially in a radius r2 in the element. The radius r1 in which the channel 3 is arranged is smaller than the radius r2 in which the base 5 is arranged in the element 1.
    It can be seen in FIG. 2 that the element 1 has a plurality of recesses 2 for each valve bridge V. The number of recesses 2 can be varied depending on the need for cooling and the size of the element 1.
    / 18th
    In the embodiment shown, three mutually parallel recesses 2 are provided for each valve bridge V. These recesses 2 represent grooves, the bottom 5 of which is directed into the interior of the element 1.
    In the interior of the element 1, the channel 3 can also be seen as an extension between two recesses 2. These two recesses 2, which are arranged at 90 ° to one another, have a smaller depth t inside the element 1. A width w of the recesses 2 is essentially the same for all recesses 2. The channel 3 has a diameter d.
    A flow profile in and around the element 1 is shown schematically in FIG. 3. It can be seen that the flow velocities increase in the direction of the lower partial cooling space U. Furthermore, it can be seen in the lower region that after a region in which the recesses 2 on the element 1 disappear downwards, depth t increases again towards a combustion chamber. This makes it possible to conduct the flow better.
    4 shows a second embodiment of the cylinder head according to the invention. The main features are the same and only the differences from the first version are discussed below.
    In this second embodiment, the element points to two valve bridges V, which are arranged next to one another, each with five recesses 2, which have different depths t. In relation to these two groups of recesses 2, only four recesses 2 are arranged on element 1 and three channels 3 are provided in between. As can be seen in this illustration, a cooling channel is also provided in the valve bridges V each.
    权利要求:
    Claims (13)
    [1]
    P A T E N T A N S P R Ü C H E
    1. Cylinder head for an internal combustion engine with at least one upper partial cooling chamber (O) and one lower partial cooling chamber (U), which are separated from one another by an intermediate deck (Z), with an element (1) extending into a combustion chamber that forms the intermediate deck (Z) penetrates, wherein in the area of the element (1) at least one flow connection is formed between the two partial cooling chambers (O, U) to allow the coolant to flow from the upper partial cooling chamber (O) to the lower partial cooling chamber (U), characterized in that the Flow connection is formed by at least one recess (2) on the element (1), which is single-walled and that the flow connection to the lower partial cooling chamber (U) tapers - preferably continuously.
    [2]
    2. Cylinder head according to claim 1, characterized in that at least one recess (2) in the element (1) is groove-shaped, which is open in the direction of a valve bridge (V) and with its base (5) essentially inside the element ( 1) is aligned.
    [3]
    3. Cylinder head according to claim 1 or 2, characterized in that for each valve bridge (V) at least one recess (2) is formed open in the element (1) and that preferably three recesses (2) per valve bridge (V) in the element ( 1) are trained.
    [4]
    4. Cylinder head according to one of claims 1 to 3, characterized in that the intermediate deck (Z) has a substantially conical recess (4) in which the element (1) is arranged.
    [5]
    5. Cylinder head according to one of claims 1 to 4, characterized in that in the element (1) at least one channel (3) is provided, which serves for the flow connection between the upper partial cooling space (O) and lower partial cooling space (U).
    [6]
    6. Cylinder head according to claim 5, characterized in that an inlet opening of the channel (3) has a distance (a) from the intermediate deck (Z) which is greater than a distance (e) from a starting point (A) of the recess (2) from False deck (Z).
    9/18
    [7]
    7. Cylinder head according to claim 5 or 6, characterized in that the channel (3) is arranged in a radius (r1) of the element (1) which is smaller than a radius (r2) at which the base (5) of the Recess (2) is arranged in the element (1).
    [8]
    8. Cylinder head according to claim 5, 6 or 7, characterized in that the channel (3) has a diameter (d) which has a ratio (d / D) to the diameter (D) of the element (1) which is between 0, 02 and 0.2 and is preferably between 0.06 and 0.1, in particular about 0.08.
    [9]
    9. Cylinder head according to one of claims 1 to 8, characterized in that the element (1) to the intermediate deck (Z) has an annular gap (R) which serves for the flow connection between the upper part cooling chamber (O) and the lower part cooling chamber (U).
    [10]
    10. Cylinder head according to claim 9, characterized in that the annular gap (R) has a width (B) which has a ratio (B / D) to the diameter (D) of the element (1) which is less than 0.05 and is preferably less than 0.02, in particular less than 0.015.
    [11]
    11. Cylinder head according to one of claims 1 to 10, characterized in that a recess (1) has a width (w) which has a ratio (w / D) to the diameter (D) of the element (1) which is smaller is less than 0.2 and is preferably less than 0.1, in particular about 0.06.
    [12]
    12. Cylinder head according to one of claims 1 to 11, characterized in that the flow connection at a first height (H1) along the element (1) in the region of the upper partial cooling chamber (O) has an inlet cross-section (A1) and the flow connection in a second Height (H2) along the element (1) in the area of the lower partial cooling space (U) has an outlet cross-section (A2) and that the inlet cross-section (A1) and the outlet cross-section (A2) are in a ratio (A1 / A2) to one another that is greater is as 1, and is preferably over 1.6 and particularly preferably about 1.82.
    [13]
    13. Cylinder head according to one of claims 1 to 12, characterized in that the element (1) in the region of the flow connection in the
    10/18
    The intermediate deck (Z) has a constriction to a minimum diameter (m), this minimum diameter (m) to the diameter (D) having a ratio (m / D) which is between 0.3 and 0.8, in particular between 0.4 and 0.6, particularly preferably about 0.46.
    类似技术:
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    CH615980A5|1980-02-29|
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    DE712655C|1941-10-23|Pre-chamber for internal combustion engines with a cross-section that changes in the direction of the fuel jet
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    DE407577C|1924-12-29|Internal combustion engine with combustion chamber
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    同族专利:
    公开号 | 公开日
    WO2020051607A1|2020-03-19|
    JP2022500588A|2022-01-04|
    DE112019004577A5|2021-08-19|
    AT521514B1|2020-02-15|
    US20220065191A1|2022-03-03|
    CN112689706A|2021-04-20|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    GB2009846A|1977-12-08|1979-06-20|Sulzer Ag|A system for cooling a cylinder head for a four-stroke diesel engine|
    DE102005031243A1|2004-07-08|2006-02-02|Avl List Gmbh|Cylinder head for internal combustion engine has flow connection between upper and lower cooling chambers formed in cooling insert encompassing component at least in region of partition between cooling chambers|
    JP2009264255A|2008-04-25|2009-11-12|Daihatsu Diesel Mfg Co Ltd|Cooling device of fuel injection valve|
    EP2372135A1|2008-12-26|2011-10-05|Mitsubishi Heavy Industries, Ltd.|Gas engine|
    WO2012101014A1|2011-01-27|2012-08-02|Avl List Gmbh|Liquid-cooled internal combustion engine|AT522929A1|2019-11-29|2021-03-15|Avl List Gmbh|LIQUID-COOLED CYLINDER HEAD FOR A COMBUSTION ENGINE|
    WO2022027076A1|2020-08-07|2022-02-10|Innio Jenbacher Gmbh & Co Og|Flow guiding device, cylinder head assembly, and internal combustion engine|FR2835883B1|2002-02-12|2004-04-09|Renault|CYLINDER HEAD FOR INTERNAL COMBUSTION ENGINE|
    AT6654U1|2002-10-31|2004-01-26|Avl List Gmbh|CYLINDER HEAD FOR A LIQUID-COOLED MULTI-CYLINDER INTERNAL COMBUSTION ENGINE|
    AT503182B1|2007-04-05|2008-10-15|Avl List Gmbh|LIQUID-COOLED INTERNAL COMBUSTION ENGINE|
    CN201599103U|2010-01-29|2010-10-06|东风汽车有限公司|Cylinder cover for oil intake and return of oil injector|
    AT518998B1|2016-12-07|2018-03-15|Avl List Gmbh|CYLINDER HEAD|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50789/2018A|AT521514B1|2018-09-14|2018-09-14|cylinder head|ATA50789/2018A| AT521514B1|2018-09-14|2018-09-14|cylinder head|
    PCT/AT2019/060290| WO2020051607A1|2018-09-14|2019-09-09|Cylinder head|
    DE112019004577.6T| DE112019004577A5|2018-09-14|2019-09-09|Cylinder head|
    JP2021513825A| JP2022500588A|2018-09-14|2019-09-09|cylinder head|
    US17/275,925| US20220065191A1|2018-09-14|2019-09-09|Cylinder head|
    CN201980060020.9A| CN112689706A|2018-09-14|2019-09-09|Cylinder head|
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