• 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 (1) of a liquid - cooled internal combustion engine, wherein the cylinder head (1) has a cooling chamber arrangement (5) which borders on a fire deck (3) and through an intermediate deck (4) arranged substantially parallel to the fire deck (3) a lower side partial cooling space (5a) and an upper partial cooling space (5b) are subdivided, the upper part cooling space (5b) being arranged on a side of the intermediate deck (4) facing away from the fire deck (3) in the direction of a cylinder axis (2) and the upper part cooling space (5b) (5b) and the lower part of the cooling chamber (5a) via at least one, about the cylinder axis (2) extending overflow opening (6) are flow-connected, which is preferably subsequently arranged on a receiving sleeve (7). Object of the present invention is to provide a cylinder head (1), which has an optimal cooling thermally stressed areas. This object is achieved according to the invention in that the overflow opening (6) has at least one annular segment segment (6a) extending around the cylinder axis (2) and one outgoing bulge section (6b) leading away from the cylinder axis (2) in the radial direction.
    公开号:AT518998A4
    申请号:T51113/2016
    申请日:2016-12-07
    公开日:2018-03-15
    发明作者:Andreas Zurk Ing；Martin Klampfer Ing；Ing Gelter Jürgen；Manfred Breitenberger Ing；Dipl Ing Knollmayr Christof
    申请人:Avl List Gmbh；
    IPC主号:
    专利说明:

    SUMMARY
    The invention relates to a cylinder head (1) of a liquid-cooled
    Internal combustion engine, the cylinder head (1) having a cooling space arrangement (5) which borders on a fire deck (3) and through an intermediate deck (4) arranged essentially parallel to the fire deck (3) into a lower partial cooling space (5a) and an upper one on the fire deck side Partial cooling space (5b) is subdivided, the upper partial cooling space (5b) being arranged on a side of the intermediate deck (4) facing away from the fire deck (3) in the direction of a cylinder axis (2) and the upper (5b) and the lower partial cooling space (5a) Are connected to flow via at least one overflow opening (6) extending around the cylinder axis (2), which is preferably arranged next to a receiving sleeve (7). The object of the present invention is to provide a cylinder head (1) which has an optimal cooling of thermally stressed areas. This object is achieved according to the invention in that the overflow opening (6) has at least one ring segment section (6a) which extends in the shape of a ring segment around the cylinder axis (2) and a bulging section (6b) which extends away from the cylinder axis (2) in the radial direction.
    Fig. 3/16
    20863AT
    The invention relates to a cylinder head of a liquid-cooled
    Internal combustion engine, wherein the cylinder head has a cooling space arrangement which borders on a fire deck and is divided by an intermediate deck arranged essentially parallel to the fire deck into a lower partial cooling space on the fire deck side and an upper partial cooling space, the upper partial cooling space on a side facing away from the fire deck in the direction of a cylinder axis of the intermediate deck is arranged and the upper partial cooling space and the lower partial cooling space are fluidly connected via at least one overflow opening which extends around the cylinder axis and which is preferably arranged on a receiving sleeve. The invention also relates to an internal combustion engine with such a cylinder head.
    A cylinder head is known from the applicant's AT 005 939 U1 in which the coolant flows from the upper part of the cooling space through an annular overflow opening between the intermediate deck and a receiving sleeve for a central component into the lower part of the cooling space. From there, the coolant is discharged into the cooling chamber of the crankcase via overflow openings. The valve bridges are flowed through evenly, but without any special directivity, which in certain applications can have disadvantages in terms of the cooling effect. AT 503 182 A2 shows a comparable solution.
    In AT 510 857 Bl an inflow channel is provided between an upper and lower partial cooling space, which has a ring-shaped or ring-segment-shaped inlet opening in a central area. As a result, an adaptation to the local thermal requirements of the subsequent valve bridge passages is sought in order to improve the heat dissipation in the area of the exhaust valve seats and the valve bridges.
    The known arrangements have the disadvantage that only inadequate adaptation of the cooling of regions of the cylinder head which are subject to high thermal stress is possible, which may prove necessary in certain applications. The flow distribution to the various radial cooling channels can only be adjusted via the size of the overflow openings to the cylinder housing. As a result, the radial cooling channels on the inlet side are cooled as well as on the outlet side, but this is disadvantageous in relation to the temperature distribution on the fire deck. By
    2/16 the resulting uneven temperature distribution on the fire deck results in material stresses in the cylinder head. At the same time, the cross-sectional area of the overflow openings can only be expanded to a limited extent for reasons of strength of the cylinder head, so that there may be an undersupply of coolant or disadvantageous pressure conditions. Furthermore, an annular overflow opening does not allow a specific flow around the receiving sleeve in the lower partial cooling space, since the cooling water flows in a vertical direction through the overflow opening onto the fire deck and subsequently into the radial cooling channels.
    The object of the invention is to avoid these disadvantages and to ensure optimal cooling of thermally highly stressed areas of the fire deck and the receiving sleeve.
    This object is achieved according to the invention by a cylinder head mentioned at the outset in that the overflow opening has at least one ring segment section which extends in the form of a circular ring segment around the cylinder axis and a bulging section which extends away from the cylinder axis in the radial direction. In other words, the overflow opening has a first section which extends in the form of a segment of a circle around the cylinder axis and from which a second section extends, which is designed as a radial bulge section which points away from the cylinder axis in the radial direction.
    A circular ring segment in the sense of the invention is a circular ring section which extends over an angular range of less than 360 °.
    Within the scope of the present disclosure, a
    Understand the longitudinal center axis of a cylinder, which runs essentially normal to a fire deck or a cylinder head sealing plane.
    Due to the limited expansion of the ring segment section and
    Bulge section increases the flow velocities in the transition between the partial cooling rooms and this concentrated flow, in particular due to the bulge section, increases the cooling of thermally highly stressed areas on the fire deck and in the area of valve bridges and thus reduces the temperature.
    3/16
    In a variant of the invention, the ring segment section extends over a first angle around the cylinder axis, which is between 20 ° and 180 °, preferably between 30 ° and 90 ° and particularly preferably 40 ° to 50 °. The bulge section extends over a second angle around the cylinder axis, which is between 5 ° and 45 °, preferably between 5 ° and 20 °. The second angle is advantageously smaller than the first angle.
    It is particularly advantageous if the overflow opening is arranged to extend from the receiving sleeve in the direction of an outlet channel, preferably between two outlet valves. As a result, the entire coolant flow in the upper partial cooling space is concentrated on the outlet side and improved cooling of the outlet channel wall and an outlet valve guide is achieved. Furthermore, due to the concentrated flow through the outlet side, the flow through the inlet side is somewhat reduced. This creates a slight temperature rise in the inlet valve bridge, which means that the temperature level on the entire fire deck is very even and the material tensions can be drastically reduced.
    A particularly focused flow with a favorable cooling effect can be achieved if the width of the ring segment section running in the radial direction is less than the width of the bulge section running in the circumferential direction. In other words, the width of the ring segment section is defined as its extension in the radial direction while the width of the bulge section is defined as an extension in the circumferential direction around the cylinder axis.
    The ring segment section has a greater extent in the circumferential direction around the cylinder axis (hereinafter referred to as the length of the ring segment section) than in the radial direction (extent in the radial direction hereinafter referred to as the width of the ring segment section). In contrast, the bulge section has a greater extent in the radial direction (hereinafter referred to as the length of the bulge section) than in the circumferential direction around the cylinder axis (this extent in the circumferential direction is hereinafter referred to as the width of the bulge section). if the overflow opening essentially extends in the circumferential direction around the cylinder axis
    4/16 extends between two connecting lines extending from the cylinder axis to a valve axis of two different valves, preferably between connecting lines from the cylinder axis to the exhaust valve axes of the two exhaust valves. In a variant of the invention, the bulge section extends along a normal to the fire deck between two valve axes, preferably the valve axes of the exhaust valves
    Valve symmetry level. The extension of the
    Bulge section in the radial direction in front of a connecting plane between the two valve axes. This results in a favorable balance between the cooling effect and the strength of the cylinder head.
    It is advantageous if the bulge section extends in the direction leading away from the cylinder axis over a radial cooling channel running through an exhaust valve bridge. As a result, the region of the exhaust valve bridge which is subject to high thermal stress can be cooled particularly effectively.
    For good cooling, it is also advantageous if the overflow opening is flow-connected in the lower partial cooling space via a distribution ring arranged in the lower partial cooling space around the receiving sleeve with cooling channels leading radially away from the distribution ring. This allows the receiving sleeve in the lower
    Part of the cooling compartment can be flowed around in a targeted manner.
    The object of the invention is also achieved by an internal combustion engine with a cylinder head according to one of the variants described above.
    The invention is described below on the basis of a non-restrictive one
    Embodiment, which is shown in the figures, explained in more detail. In it shows
    1 shows a schematic representation of a cylinder head according to the invention in a section along the line I-I in Fig. 2;
    FIG. 2 shows the cylinder head from FIG. 1 in a section in the region of an upper partial cooling space along the line II-II in FIG. 1; and
    3 shows the cylinder head from FIG. 1 in a section in the region of a lower partial cooling space along the line III-III in FIG. 1.
    5/16
    1 shows, in a section of an internal combustion engine 100, a liquid-cooled cylinder head 1 with at least one cylinder, not shown, which is arranged along a cylinder axis 2. The cylinder head 1 has a fire deck 3 in the direction of a combustion chamber of the cylinder. An intermediate deck 4 divides a cooling space arrangement 5 into a lower partial cooling space 5a near the fire deck 3 and an upper partial cooling space 5b adjoining in the direction of the cylinder axis 2.
    The intermediate deck 4 has at least one overflow opening 6 for the flow connection between the upper partial cooling space 5b and the lower partial cooling space 5a, which is formed between the intermediate deck 4 and a receiving sleeve 7. The receiving sleeve 7 serves, for example, to receive a fuel injection device or a spark plug and is arranged essentially concentrically with the cylinder axis 2. 2, the overflow opening 6, starting from the cylinder axis 2, connects to the receiving sleeve 7 in the radial direction and, according to the invention, has an annular segment section 6a, which extends at least partially around the cylinder axis 2 or the receiving sleeve 7, with an additional one running in the radial direction
    Bulge section 6b. When implemented as a top-down cooling, that is, when the coolant flows from the upper 5b into the lower partial cooling space 5a, a favorable distribution of the coolant and cooling, in particular of the thermally highly stressed areas, can be achieved.
    The ring segment section 6a has the shape of a circular ring segment and extends in the circumferential direction over a first angle α about the cylinder axis 2 or the receiving sleeve 7. The first angle α is between 20 ° and 180 °, an angle of approximately 65 in the exemplary embodiment shown ° is realized. The substantially radially extending bulge section 6b extends in the circumferential direction over a second angle β, which is between 5 ° and 45 °, with approximately 16 ° being implemented in the exemplary embodiment shown.
    The second angle β is preferably small compared to the first angle α. This allows the coolant to be directed specifically to the areas of the valve axes that are particularly thermally highly stressed on the outlet side.
    In addition to the angular ranges mentioned in the circumferential direction about the cylinder axis 2, the extensions in the radial direction are also starting
    6/16 of the cylinder axis 2, to be taken into account: The ring segment section 6a has a larger extent in the circumferential direction in all design variants than in the radial direction. The extent in the radial direction is the width of the ring segment section 6a. The bulge section 6b can be designed differently depending on the design variant: the width of the
    Bulge section 6b, that is to say its extent in the circumferential direction around the cylinder axis 2, can either be smaller, the same size or larger than the extent of the bulge section 6b in the radial direction (starting from the cylinder axis 2). In the exemplary embodiment shown in FIGS. 2 and 3, the width of the bulge section 6b is essentially equal to the length, that is to say to extend in the radial direction. A favorable coolant distribution when flowing through the overflow opening 6 can be achieved if - as implemented in the exemplary embodiment shown - the width of the ring segment section 6a running in the radial direction is smaller than the width of the bulge section 6b running around the cylinder axis 2 in the circumferential direction.
    In order to achieve the best possible balance between the pressure loss when flowing through the overflow opening 6 and the cooling effect in the region of the areas subjected to high thermal stress, such as the receiving sleeve 7 and valve bridges, the dimensioning of the overflow opening 6 is selected as follows: two connecting lines A extending from the cylinder axis 2 to one valve axis 8a, 8b each from two different valves are arranged. Basically, these can be the exhaust valve axles 8a and the intake valve axles 8b, or a connection line A to an exhaust valve axis 8a and an intake valve axis 8b, but in the exemplary embodiment shown in FIG. 2, the connection lines A are between the cylinder axis 2 and the exhaust valve axes 8a arranged. This is advantageous because the highest thermal loads occur during operation on the outlet side. The connecting line A connects as a valve axis 8a, 8b to the cylinder axis 2. At the same time, the bulge section 6b extends along a valve symmetry plane Z running between two valve axes 8a, 8b - in the exemplary embodiment shown between the exhaust valve axes 8a - normal to the fire deck 3. The valve symmetry plane Z runs normal to the fire deck 3 or to the cylinder head sealing plane and parallel to the valve axes 8a, 8b through the cylinder axis 2. The extension of the ends in the radial direction
    7/16
    Overflow opening 6, in particular the bulge section 6b, in front of a
    Connection line between the two assigned to the valve symmetry plane Z.
    Valve axes 8a, 8b - in the exemplary embodiment shown, these are the
    Exhaust valve axles 8a.
    The figures use arrows P to show the flow of a coolant in a cylinder head 1 according to the invention. According to arrows P in FIG. 1, the coolant comes from a pressure source, not shown, for example a coolant pump, through a coolant inlet into the upper partial cooling chamber 5b, flows through the Overflow opening 6 in the vertical direction in the lower partial cooling space 5a, where it strikes the fire deck 3 and cools it.
    As shown in FIG. 3, the coolant in the lower partial cooling space 5a is divided via a distribution ring 10 into, for example, four radial cooling channels 9a, 9b, 9c, 9d and flows further through openings 11a, 11b, 11c, lld into a crankcase. Of course, fewer radial cooling channels and fewer openings can also be provided.
    A targeted flow around and thus cooling of the receiving sleeve 7 is made possible via the distribution ring 10. The radial cooling channels 9a, 9b, 9c, 9d are arranged in particular in the region of valve bridges - due to the design of the overflow opening 6 with ring segment section 6a and bulge section 6b, the coolant flow is directed and in particular the outlet valve bridge 90, i.e. the first radial cooling channel 9a between the outlet channels 8, efficiently cooled. As can be seen from FIG. 2 in conjunction with FIG. 3, the bulge section 6b runs in the direction leading radially away from the cylinder axis 2 over the first radial cooling channel 9a running through an exhaust valve bridge 90. The positioning “above is to be understood here in a direction leading away from the fire deck 3 along the cylinder axis 2. The first radial cooling duct 9a is part of the lower partial cooling space 5a and the bulge section 6b is carried out in the area of the intermediate deck 4. On the one hand, a larger amount of water is supplied to this first cooling duct 9a, on the other hand, the outlet valve bridge 90 is additionally cooled in the area of the intermediate deck 4.
    8/16
    This steering effect is reinforced by the positioning of the openings 11a,
    11b, 11c, lld, through which the coolant from the cylinder head 1 into the
    Crankcase expires.
    The geometry shown in the exemplary embodiment in the figures and positioning of the overflow opening 6 on the outlet side result in concentrated cooling of the outlet side both in the upper partial cooling chamber 5b and in the lower partial cooling chamber 5a. This results in optimal cooling of the outlet channel 8 or the outlet channels, of outlet valve guides 7a, 7b (see FIG. 2) and subsequently of the fire deck 3 in the region which is subject to high thermal stress
    Exhaust valve bridge 90 reached. This results in a homogeneous
    Temperature level on the entire fire deck 3 and thus lower material stresses occur in the cylinder head 1. The valve bridge or exhaust valve bridge 90 is understood to mean the accumulation of material between the gas exchange valves (not shown) or the exhaust valves. The exhaust valve bridge 90 is very thermally stressed.
    In addition to the variant shown in the exemplary embodiment in the figures, other variants are also possible where, for example, the bulge section 6b is arranged in the region of the inlet valve bridge or the inlet-outlet valve bridge or that further ring segment sections are provided which are each connected or partially connected to bulge sections.
    The invention thus permits an increase in the flow velocities in the transition between the partial cooling rooms 5a, 5b and, through this concentrated flow, in particular due to the bulge section 6b, the cooling of thermally highly stressed areas on the fire deck 3 and in the area of valve bridges - especially the outlet valve bridge 90 - increased and thus the temperature reduced. This prevents thermal stresses and consequent damage to the cylinder heads.
    9/16
    权利要求:
    Claims (14)
    [1]
    PATENT CLAIMS
    1. Cylinder head (1) of a liquid-cooled internal combustion engine, the cylinder head (1) having a cold room arrangement (5) which borders on a fire deck (3) and through an intermediate deck (4) arranged essentially parallel to the fire deck (3) into a fire deck-side lower partial cooling space (5a) and an upper partial cooling space (5b), the upper partial cooling space (5b) being arranged on a side of the intermediate deck (4) facing away from the fire deck (3) in the direction of a cylinder axis (2) and the upper partial cooling space ( 5b) and the lower partial cooling chamber (5a) are connected to flow via at least one overflow opening (6) extending around the cylinder axis (2), which is preferably arranged next to a receiving sleeve (7), characterized in that the overflow opening (6) at least an annular segment segment (6a) extending in the shape of an annular segment around the cylinder axis (2) and one extending therefrom in the radial direction from the cylinder has the bulge portion (6b) pointing the way (2).
    [2]
    2. Cylinder head (1) according to claim 1, characterized in that the ring segment section (6a) extends over a first angle (α) around the cylinder axis (2), which is between 20 ° and 180 °, preferably between 30 ° and 90 ° and particularly preferably 40 ° to 50 °.
    [3]
    3. Cylinder head (1) according to claim 1 or 2, characterized in that the bulge section (6b) extends over a second angle (β) around the cylinder axis (2), which is between 5 ° and 45 °, preferably between 5 ° and 20 °.
    [4]
    4. Cylinder head (1) according to one of claims 1 to 3, characterized in that the bulge portion (6b) extends over a second angle (β) around the cylinder axis (2), which is smaller than the first angle (α).
    [5]
    5. Cylinder head (1) according to any one of claims 1 to 4, characterized in that the radial direction running in the [direction extending from the cylinder axis (2)]
    10/16
    Ring segment section (6a) is less than the circumferential width of the bulge section (6b).
    [6]
    6. Cylinder head (1) according to one of claims 1 to 5, characterized in that the overflow opening (6) in the circumferential direction around the cylinder axis (2) essentially between two of the cylinder axis (2) to one valve axis (8a, 8b) ) extending from two different valve connecting lines (A), preferably between the connecting lines (A) from the cylinder axis (2) to the exhaust valve axes (8a) of the two exhaust valves.
    [7]
    7. Cylinder head (1) according to one of claims 1 to 6, characterized in that the bulge portion (6b) along one between two valve axes (8a, 8b), preferably the exhaust valve axes (8a) of the exhaust valves, normal to the fire deck (3) extending valve symmetry plane (Z) extends.
    [8]
    8. Cylinder head (1) according to one of claims 1 to 7, characterized in that the bulge section (6b) in the direction leading away from the cylinder axis (2) over a radial cooling channel (9a; 9b) extending through a valve bridge, in particular an exhaust valve bridge (90) ; 9c; 9d) runs.
    [9]
    9. Cylinder head (1) according to one of claims 1 to 8, characterized in that the overflow opening (6) via a in the lower cooling compartment (5a) around the receiving sleeve (7) arranged distribution ring (10) with radially leading away from the distribution ring (10) Cooling channels (9a, 9b, 9c, 9d) in the lower part of the cooling chamber (5a) is flow-connected.
    [10]
    10. Internal combustion engine (100) with a cylinder head (1) according to one of claims 1 to 9.
    2016 12 07
    Wr
    [11]
    11/16
    [12]
    12/16
    / Κ Ό ~ $
    Q.
    lld
    14/16
    20863ATv2p
    Record number: A 51113/2016 (new) PATENT CLAIMS
    1. Cylinder head (1) of a liquid-cooled internal combustion engine, the cylinder head (1) having a cold room arrangement (5) which borders on a fire deck (3) and through an intermediate deck (4) arranged essentially parallel to the fire deck (3) into a fire deck-side lower partial cooling space (5a) and an upper partial cooling space (5b), the upper partial cooling space (5b) being arranged on a side of the intermediate deck (4) facing away from the fire deck (3) in the direction of a cylinder axis (2) and the upper partial cooling space ( 5b) and the lower partial cooling chamber (5a) are connected to flow via at least one overflow opening (6) extending around the cylinder axis (2), which is preferably arranged next to a receiving sleeve (7), characterized in that the overflow opening (6) at least an annular segment segment (6a) extending in the shape of an annular segment around the cylinder axis (2) and one extending therefrom in the radial direction from the cylinder has the bulge section (6b) which points the way (2), the ring segment section (6a) being arranged entirely within two diameters and these diameters at least affecting the ring segment section (6a).
    2. Cylinder head (1) according to claim 1, characterized in that the ring segment section (6a) extends over a first angle (α) around the cylinder axis (2), which is between 20 ° and 180 °, preferably between 30 ° and 90 ° and particularly preferably 40 ° to 50 °.
    3. Cylinder head (1) according to claim 1 or 2, characterized in that the bulge section (6b) extends over a second angle (β) around the cylinder axis (2), which is between 5 ° and 45 °, preferably between 5 ° and 20 °.
    4. Cylinder head (1) according to one of claims 1 to 3, characterized in that the bulge portion (6b) extends over a second angle (β) around the cylinder axis (2), which is smaller than the first angle (α).
    [13]
    15/16 [LAST CLAIMS]
    5. Cylinder head (1) according to any one of claims 1 to 4, characterized in that the radial direction of the radial segment of the ring segment section (6a) is smaller than the circumferential width of the bulge section (6b).
    6. Cylinder head (1) according to one of claims 1 to 5, characterized in that the overflow opening (6) in the circumferential direction around the cylinder axis (2) essentially between two of the cylinder axis (2) to one valve axis (8a, 8b ) extending from two different valve connecting lines (A), preferably between the connecting lines (A) from the cylinder axis (2) to the exhaust valve axes (8a) of the two exhaust valves.
    7. Cylinder head (1) according to one of claims 1 to 6, characterized in that the bulge section (6b) along one between two valve axes (8a, 8b), preferably the exhaust valve axes (8a) of the exhaust valves, normal to the fire deck (3) extending valve symmetry plane (Z) extends.
    8. Cylinder head (1) according to one of claims 1 to 7, characterized in that the bulge section (6b) in the direction leading away from the cylinder axis (2) over a radial cooling channel (9a; 9b) running through a valve bridge, in particular an exhaust valve bridge (90) ; 9c; 9d) runs.
    9. Cylinder head (1) according to one of claims 1 to 8, characterized in that the overflow opening (6) via a in the lower cooling compartment (5a) around the receiving sleeve (7) arranged distribution ring (10) with radially leading away from the distribution ring (10) Cooling channels (9a, 9b, 9c, 9d) in the lower part of the cooling chamber (5a) is flow-connected.
    10. Internal combustion engine (100) with a cylinder head (1) according to one of claims 1 to 9.
    11/03/2017
    WR
    [14]
    16/16 [LAST CLAIMS]
    类似技术:
    公开号 | 公开日 | 专利标题
    EP3333398B1|2020-02-12|Cylinder head
    DE10350394B4|2014-10-30|Cylinder head for a liquid-cooled multi-cylinder internal combustion engine
    DE10331918B4|2014-08-07|Cylinder head for a liquid-cooled multi-cylinder internal combustion engine
    DE1476804A1|1970-03-26|Turbine blade with aerofoil profile
    AT510857B1|2012-07-15|LIQUID-COOLED INTERNAL COMBUSTION ENGINE
    EP1733132B1|2011-11-02|Water-cooled cylinder head for a multi-cylinder internal combustion engine
    EP3379063A1|2018-09-26|Liquid-cooled combustion engine
    EP1799987A1|2007-06-27|Piston for a combustion engine, and combustion engine
    AT506468A2|2009-09-15|Cylinder head for internal combustion engine of vehicle, has inlet side and outlet side with outlet channel per cylinder, where coolant jacket is arranged in cylinder head
    EP2737188B1|2017-01-11|Cylinder head with liquid-type cooling
    DE3127122A1|1983-01-20|"PISTON COMBUSTION ENGINE WITH LIQUID-COOLED VALVE SEAT FOR THE EXHAUST VALVE"
    DE102014100841A1|2014-07-31|Cylinder head for internal combustion engine, has inlet and outlet that are separated using separating region that is provided with throttle point for defined short-circuit flow between inlet and outlet
    EP1917493B1|2015-08-19|Heat exchanger, particularly an oil cooler for an internal combustion engine
    EP2788583B1|2016-03-02|Turbine vane with a throttling element
    EP0819837A1|1998-01-21|Cooling circuit of an internal combustion engine
    WO2014180873A1|2014-11-13|Cylinder head for an internal combustion engine
    AT516742B1|2016-08-15|INTERNAL COMBUSTION ENGINE WITH A LIQUID COOLED CYLINDER BLOCK
    DE102010036392B4|2021-10-07|Liquid-cooled cylinder head for an internal combustion engine
    DE102012112904A1|2013-07-25|Internal combustion engine with a cylinder head
    DE102016216360A1|2018-03-01|Cylinder head for an internal combustion engine
    DE102016110993A1|2016-12-22|Cylinder head with features for limiting exhaust manifold shrinkage
    DE102004011656A1|2005-11-24|Water-cooled cylinder head for an internal combustion engine
    AT519991B1|2019-07-15|Cylinder head with valve seat ring cooling
    AT522271B1|2021-02-15|COMBUSTION ENGINE WITH AT LEAST ONE CYLINDER
    DE102010007877A1|2011-08-18|Exhaust manifold for an internal combustion engine
    同族专利:
    公开号 | 公开日
    EP3333398B1|2020-02-12|
    KR20180065940A|2018-06-18|
    EP3333398A1|2018-06-13|
    AT518998B1|2018-03-15|
    CN108167085A|2018-06-15|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US4889080A|1987-05-26|1989-12-26|Kabushiki Kaisha Komatsu Seisakusho|Cylinder head for an internal combustion engine|
    JPH0674041A|1992-08-24|1994-03-15|Daihatsu Motor Co Ltd|Structure of cylinder head for four-valve type internal combustion engine|
    AT5939U1|2002-01-25|2003-01-27|Avl List Gmbh|CYLINDER HEAD|
    AT6654U1|2002-10-31|2004-01-26|Avl List Gmbh|CYLINDER HEAD FOR A LIQUID-COOLED MULTI-CYLINDER INTERNAL COMBUSTION ENGINE|
    AT503182A2|2007-04-05|2007-08-15|Avl List Gmbh|LIQUID-COOLED INTERNAL COMBUSTION ENGINE|
    AT508830A1|2010-07-08|2011-04-15|Avl List Gmbh|CYLINDER HEAD FOR A LIQUID-COOLED INTERNAL COMBUSTION ENGINE|
    AT510857A4|2011-01-27|2012-07-15|Avl List Gmbh|LIQUID-COOLED INTERNAL COMBUSTION ENGINE|
    JP2866259B2|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|
    US10001078B2|2014-09-22|2018-06-19|Deere & Company|Engine cooling system|
    CN106150746A|2016-08-30|2016-11-23|潍柴动力股份有限公司|A kind of cylinder and cylinder head thereof|AT521514B1|2018-09-14|2020-02-15|Avl List Gmbh|cylinder head|
    US11181032B2|2018-09-18|2021-11-23|Deere & Company|Cylinder head with improved valve bridge cooling|
    AT523950A1|2020-06-18|2022-01-15|Avl List Gmbh|Cylinder head for an internal combustion engine|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA51113/2016A|AT518998B1|2016-12-07|2016-12-07|CYLINDER HEAD|ATA51113/2016A| AT518998B1|2016-12-07|2016-12-07|CYLINDER HEAD|
    EP17202118.0A| EP3333398B1|2016-12-07|2017-11-16|Cylinder head|
    CN201711276745.0A| CN108167085A|2016-12-07|2017-12-06|Cylinder head|
    KR1020170167419A| KR20180065940A|2016-12-07|2017-12-07|Cylinder head|
    [返回顶部]