• 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 liquid cooling system (K) with a cylinder head (3) having an integrated exhaust collector (7) for an internal combustion engine (2), wherein the cylinder head (3) has at least one first cooling space (5) for cooling to a combustion chamber has adjacent areas and at least a second cooling chamber (6) for cooling the exhaust manifold (7), wherein the first and second cooling chambers (5, 6) are separated from each other by flow through. The cooling management can be improved in a simple manner if at least one oil cooler (14) and / or at least one vehicle heating element (15) is arranged in series with the second cooling space (6) in the cooling circuit (1).
    公开号:AT513175A1
    申请号:T50298/2012
    申请日:2012-07-26
    公开日:2014-02-15
    发明作者:Christof Dipl Ing Knollmayr；Gernot Fuckar；Heinz Petutschnig
    申请人:Avl List Gmbh；
    IPC主号:
    专利说明:

    1 56461
    The invention relates to a liquid cooling system for an internal combustion engine of a vehicle with a cylinder head having an integrated exhaust manifold, wherein the cylinder head has at least a first cooling space for cooling adjacent areas of a combustion chamber and at least a second cooling space for cooling the exhaust manifold, wherein the first and second cooling chambers separated from each other can be flowed through in parallel.
    From US 2005/0087154 Al it is known to carry out the exhaust manifold integrally with the cylinder head. The main cooling space formed by an upper and a lower partial cooling space is thermally connected to the exhaust gas collector.
    EP 0 856 650 A1 shows a cooling system for an outboard motor, wherein the outgoing from the combustion chamber exhaust ports in the cylinder head are U-shaped curved and the flange faces to connect an exhaust manifold in the cylinder head plane. The exhaust manifold is formed integrally with the cylinder housing.
    US 7,051,685 B2 discloses a cylinder head with an integrated exhaust manifold, wherein the exhaust manifold is surrounded by a first and a second cooling space, wherein the two cooling chambers are interconnected by mitgegossene flow connections. The first and the second cooling chamber are arranged one above the other.
    The AT 500 442 Bl describes a cylinder head for an internal combustion engine with liquid cooling with a first central cooling chamber and an integrated exhaust manifold surrounding the second cooling chamber, wherein the coolant flow through the second cooling chamber is separated from the coolant flow through the first cooling chamber adjustable.
    From WO 2011/061 248 Al a cylinder head for an internal combustion engine with liquid cooling and with an integrally formed with the cylinder head liquid-cooled exhaust collector is known, wherein the cylinder head has at least a first and a second, flowed through by a coolant cooling space, and wherein the range of Exhaust manifold is at least partially surrounded by the second refrigerator. The first and the second cooling space are flow-connected to one another via at least one bore. 2
    It is known to arrange the vehicle radiator and the oil cooler parallel to the cooling space of the exhaust manifold. To avoid a disturbance of the cooling, a relatively complex cooling system is required.
    The object of the invention is to improve the cooling management in an internal combustion engine of the aforementioned in the simplest possible way.
    According to the invention, this takes place in that at least one oil cooler and / or at least one vehicle heating element is arranged in series with the second cooling space in the cooling circuit.
    The oil cooler can be arranged in the cooling circuit upstream of the second cooling chamber, and the vehicle heater in the cooling circuit downstream of the second cooling space.
    Particularly advantageous branching to the first refrigerator leading first partial cooling circuit and a second cooling chamber leading second partial cooling circuit downstream of a coolant pump from the common main cooling circuit.
    Upstream of the coolant pump, a first double-acting thermostatic valve may be arranged in the region of a merger of a coming from the Kühlmittekühler main cooling circuit and the Kühlmittekühler immediate auxiliary cooling circuit.
    The first cooling space is preferably connected via a first coolant line to the auxiliary cooling circuit.
    The second cooling space is advantageously connected via a second coolant line to the main cooling circuit and / or the auxiliary cooling circuit, wherein a vehicle heating element is preferably arranged in the second coolant line.
    Furthermore, it can be provided that at least one third cooling space arranged in the cylinder block is connected via at least one transfer passage to the first cooling space in the cylinder head. Preferably, the third cooling space is connected via a third coolant line to the main cooling circuit, wherein the connection with the main cooling circuit is arranged upstream of the coolant radiator. A 3
    Embodiment variant of the invention provides that in the third coolant line, a single-acting thermostatic valve is arranged.
    In another embodiment of the invention, it is provided that the third cooling space is connected via a fourth coolant line to the auxiliary cooling circuit and / or the first coolant line. In the fourth coolant line while a single-acting thermostatic valve is arranged. Alternatively, it is also possible to arrange a second double-acting thermostatic valve in the region of a crossing point of the first coolant line, the fourth coolant line and the secondary cooling circuit.
    The described embodiments allow a simple cooling management, wherein the flow of the oil cooler and the vehicle heater has no adverse effects.
    The invention will be explained in more detail below with reference to FIG.
    1 to 3 show a liquid cooling system according to the invention for an internal combustion engine in a first embodiment, FIGS. 4 to 7 show a liquid cooling system according to the invention for an internal combustion engine in a second embodiment, FIGS. 8 to 11 show a liquid cooling system according to the invention an internal combustion engine in a third embodiment and FIGS. 12 to 16 a liquid cooling system according to the invention for an internal combustion engine in a fourth embodiment variant.
    In the figures, deactivated parts of the liquid cooling system K are each shown in dashed lines. Functionally identical parts are provided in the embodiment variants with the same reference numerals.
    The figures each show a liquid cooling system K with a cooling circuit 1 for a vehicle with an internal combustion engine 2 with a cylinder head 3 and a cylinder block 4, wherein in the cylinder head 3 at least a first cooling chamber 5 for cooling adjacent to the combustion chamber thermally critical areas and at least one second cooling chamber 6 are arranged for cooling the integrated in the cylinder head 3 exhaust manifold 7. Furthermore, at least a third cooling chamber 8 is provided in the cylinder block 4 for cooling the cylinder 9. 4
    The engine-side region of the cooling system K is denoted by KM, the vehicle-side region of the cooling system by KF.
    The first and second cooling chambers 5, 6 are flowed through in the cooling circuit 1 hydraulically parallel from the coolant, wherein a first part of the cooling circuit 10 to the first cooling chamber 5 and a second partial cooling circuit 11 leads to the second cooling chamber 6. The first and second partial cooling circuits 10, 11 branch downstream of a coolant pump 12 from a common main branch 13 of the liquid cooling system K.
    In the second partial cooling circuit 11, an oil cooler 14 is arranged upstream of the second cooling space 6 and a vehicle heating element 15 is arranged downstream of the second cooling space. The vehicle heater 15 can be deactivated via a bypass valve, not shown.
    Upstream of the coolant pump 12, a first double-acting thermostatic valve 20 is disposed in the region of a merger 16 of a main cooling circuit 18 coming from the coolant cooler 17 and a secondary cooling circuit 19 bypassing the coolant center 17.
    In the first three exemplary embodiments, the first and the third cooling chambers 5, 8 are connected to one another via at least one transfer channel 21.
    The second cooling chamber 6 is connected via a second coolant line 23 to the main cooling circuit 18 and / or the auxiliary cooling circuit 19, wherein the vehicle radiator 15 is arranged in the second coolant line 23. The third cooling chamber 8 is connected via a third coolant line 24 to the main cooling circuit 18, wherein the connection 25 is arranged with the main cooling circuit 18 upstream of the coolant radiator 17.
    In the first embodiment variant shown in FIGS. 1 to 3, only a single thermostat, specifically the first double-acting thermostatic valve 20, is provided. Fig. 1 shows the first double-acting thermostatic valve 20 in an intermediate position in which both the main cooling circuit 18, and the auxiliary cooling circuit 19 is connected to the coolant pump 12 having the main strand 13. Fig. 2 shows the situation at operating-warming internal combustion engine 2, wherein the auxiliary cooling circuit 19 is deactivated and the entire amount of coolant is passed through the main cooling circuit 18. 5
    Fig. 3 shows the liquid cooling system K in the cold state, wherein the main cooling circuit 18 is deactivated and the total amount of coolant - bypassing the coolant radiator 17 - is passed through the auxiliary cooling circuit 19.
    FIGS. 4 to 7 show a second embodiment variant with various circuit options, in which, in addition to the first double-acting thermostatic valve 20, a single-acting thermostatic valve 26 is also provided in the third coolant line 24. Furthermore, the first cooling space 5 is connected to the auxiliary cooling circuit 19 via a first coolant line 22.
    In Fig. 4 is the first double-acting thermostatic valve 20 - analogous to FIG. 1 - in a middle position, the single-acting thermostatic valve 26 is open. Thus, coolant can flow unhindered both in the main cooling circuit 18, and in the auxiliary cooling circuit 19, as well as in the third coolant line 24. In contrast to the first embodiment, the coolant can flow directly into the auxiliary cooling circuit 19 via the first coolant line 22.
    Fig. 5 shows the situation with cold engine 2, wherein by the first double-acting thermostatic valve 20 of the main cooling circuit 18 is closed. The entire coolant is passed through the auxiliary cooling circuit 19, wherein the coolant can again flow directly into the auxiliary cooling circuit 19 via the first coolant line 22.
    In FIG. 6, the internal combustion engine 2 is in the low operating temperature range, wherein the secondary cooling circuit 19 is closed via the first double-acting thermostatic valve 20 and the main cooling circuit 18 is opened. By closing the single-acting thermostatic valve 26, the cooling in the cylinder block 4 is deactivated. The coolant thus flows through the first cooling chamber 5 into the first coolant line 22 and passes via the free part 19a of the auxiliary cooling circuit 19 in the main cooling circuit 18 upstream of the coolant radiator 17. In parallel, the coolant flows through the second partial cooling circuit 11 through oil cooler 14, second working space. 6 and vehicle heater 15 and passes - after union with the coolant from the first partial cooling circuit 10 - also in the coolant cooler 17th
    Fig. 7 differs from Fig. 6 in that the single-acting thermostatic valve 26 is now open, whereby the cooling of the cylinder block 4 - is activated in the warm-to-hot temperature range of the internal combustion engine 2. The coolant passes from the cylinder head 3 via the transfer channels 21 in the third working space 8 and leaves the cylinder block 4 via the third coolant line 24 in the direction of the main cooling circuit 18 to deliver the heat absorbed in the coolant cooler 17.
    FIGS. 8 to 11 show a third variant with various circuit options, in which the third cooling chamber 8 is connected to the auxiliary cooling circuit 19 via a fourth coolant line 27 and to the first cooling chamber 5 via the first coolant line 22. In addition to the first double-acting thermostatic valve 20, a single-acting thermostatic valve 28 is still provided in the third coolant line 24. In this embodiment, no further transfer channels 21 between the first and third cooling chamber 5, 8 are provided - the function of the transfer channels 21 is taken over by the first and fourth coolant line 22, 27.
    In Fig. 8, the first double-acting thermostatic valve 20 is - analogous to Fig. 1 and Fig. 4 - in a middle position, the single-acting thermostatic valve 28 is open. Thus, coolant in both the main cooling circuit 18, and in the auxiliary cooling circuit 19, and in the third and fourth coolant line 24, 27 flow freely. In contrast to the first embodiment, the coolant can flow via the first coolant line 22 directly into the secondary cooling circuit 19 and flow from the secondary cooling circuit 19 via the fourth coolant line 27 into the third cooling chamber 8.
    FIG. 9 shows the situation with cold internal combustion engine 2: the main cooling circuit 18 is closed by the first double-acting thermostatic valve 20 - the entire coolant is passed through the secondary cooling circuit 19, wherein the coolant can again flow directly into the auxiliary cooling circuit 19 via the first coolant line 22 , The single-acting thermostatic valve 28 is closed and thus prevents the flow in the first cooling chamber eighth
    In Fig. 10 is the internal combustion engine 2 -analog to Fig. 6 - in the lower operating temperature range, being closed via the first double-acting thermostatic valve 20 of the secondary cooling circuit 19 and the main cooling circuit 18 is opened.
    By closing the single-acting thermostatic valve 28, the cooling in the cylinder block 4 is deactivated. The coolant thus flows through the first cooling chamber 7 5 in the first coolant line 22 and passes through the free part 19 a of the auxiliary cooling circuit 19 in the main cooling circuit 18 upstream of the coolant radiator 17. In parallel, the coolant flows through the second subcool 11 through oil cooler 14, second working space 6 and vehicle heater 15 and passes - after union with the coolant from the first partial cooling circuit 10 - also in the coolant radiator 17th
    In Fig. Ll, the single-acting thermostatic valve 28 is now open, whereby the cooling of the cylinder block 4 - in the warm to hot temperature range of the internal combustion engine 2 - is activated. The coolant passes from the first cooling chamber 5 of the cylinder head 3 via the first and fourth coolant line 22, 27 in the third working chamber 8 of the cylinder block 4 and leaves the cylinder block 4 via the third coolant line 24 in the direction of the main cooling circuit 18 upstream of the coolant radiator 17th
    FIGS. 12 to 16 show a fourth embodiment variant of the liquid cooling system K with different circuit options. Similar to the third embodiment, the third cooling chamber 8 is connected via a fourth coolant line 27 to the subcooling circuit 19 and via the first coolant line 22 to the first cooling chamber 5. Instead of the single-acting thermostatic valve 28 is now in addition to the first double-acting thermostatic valve 20, a second double-acting thermostatic valve 29 at the intersection 30 of the first and fourth coolant line 22, 27 provided with the auxiliary cooling circuit 19. Again, no further transfer channels 21 between the first and third cooling chamber 5, 8 are provided - the function of the transfer channels 21 is taken over by the first and fourth coolant line 22, 27.
    In Fig. 12, both double-acting thermostatic valve 20, 29 are in central positions. Thus, coolant in both the main cooling circuit 18, and in the auxiliary cooling circuit 19, as well as in the third and fourth coolant line 24, 27 flow freely. The coolant can flow via the first coolant line 22 directly into the secondary cooling circuit 19 or into the fourth coolant line 27 and flow from the auxiliary cooling circuit 19 via the fourth coolant line 27 into the third cooling chamber 8. δ
    Fig. 13 shows the situation with cold engine 2: By the first double-acting thermostatic valve 20, the main cooling circuit 18 is closed - the entire coolant is passed through the auxiliary cooling circuit 19. Furthermore, the first and the fourth coolant line 22, 27 are closed by the second double-acting thermostatic valve 29, so that the first cooling chamber 5 and the third cooling chamber 8 is not flowed through. The coolant circulates through the second coolant line 11, the oil cooler 14, the second working space 7, the vehicle heater 15 and the auxiliary cooling circuit 19 only in the small circuit.
    If the operating temperature of the internal combustion engine 2 increases, the first coolant line 22 is first opened via the second double-acting thermostatic valve 29, as shown in FIG. 14. As a result, the first cooling space 5 in the cylinder head 3 is now also flowed through, with the coolant leaving the first cooling space 5 through the first coolant line 22 and flowing back to the coolant center pump 12 via the auxiliary cooling circuit 19.
    If the temperature of the internal combustion engine 2 continues to rise, the secondary cooling circuit 19 leading to the coolant pump 12 is blocked between the intersection point 30 and the junction 16 by the second double-acting thermostatic valve 29, as shown in FIG. The first working chamber 5 through the first Kühlmitteistrang 22 leaving coolant now flows through the free portion 19a of the auxiliary cooling circuit 19 in the main cooling circuit 18 upstream of the coolant radiator 17th
    The first double-acting thermostatic valve 20 now blocks the auxiliary cooling circuit 19 and opens the main cooling circuit 18. The second double-acting thermostatic valve 29 is now in its intermediate position, in which the first and the fourth coolant line 22, 27 are opened, whereby coolant from the first coolant line 22 in both the free part 19 a of the auxiliary cooling circuit 19, as well as in the fourth coolant line 27 can flow. Thus, the first and third working spaces 5, 8 are flowed through. The coolant passes from the first cooling chamber 5 of the cylinder head 3 via the first and fourth coolant line 22, 27 in the third working chamber 8 of the cylinder block 4 and leaves the cylinder block 4 via the third 9 coolant line 24 in the direction of the main cooling circuit 18 upstream of the coolant radiator 17th
    Regardless of the positions of the thermostatic valves 20, 26 28 and 29, the oil cooler 14, the second working space 6 for cooling the exhaust manifold 7 and the vehicle heater 15 are always flowed through.
    权利要求:
    Claims (13)
    [1]
    1. A liquid cooling system (K) having a cylinder head (3) for an internal combustion engine (2) of a vehicle having an integrated exhaust collector (7), the cylinder head (3) having at least one first cooling space (5) for cooling to one Combustion chamber adjacent areas and at least a second cooling chamber (6) for cooling the exhaust manifold (7), wherein the first and second cooling chambers (5, 6) separated from each other in parallel, characterized in that at least one oil cooler (14) and / or at least one vehicle heating element (15) is arranged in series with the second cooling space (6) in the cooling circuit (1).
    [2]
    2. Liquid cooling system (K) according to claim 1, characterized in that a first cooling chamber (5) leading first partial cooling circuit (10) and a second cooling chamber (6) leading second partial cooling circuit (11) preferably downstream of a coolant pump (12) of branch off a common main line (13).
    [3]
    3. Liquid cooling system (K) according to claim 2, characterized in that the oil cooler (14) in the second partial cooling circuit (11) upstream of the second cooling chamber (6) is arranged.
    [4]
    4. Liquid cooling system (K) according to claim 2 or 3, characterized in that the vehicle heating element (15) in the second partial cooling circuit (11) downstream of the second cooling chamber (6) is arranged.
    [5]
    5. Liquid cooling system (K) according to one of claims 1 to 4, characterized in that upstream of the coolant pump (12) in the region of a merger (16) of a coolant from the coolant (17) coming main cooling circuit (18) and a coolant radiator (17) bypassing secondary cooling circuit (19) a first double-acting thermostatic valve (20) is arranged.
    [6]
    6. Liquid cooling system (K) according to one of claims 1 to 5, characterized in that the first cooling chamber (5) via a first coolant line (22) to the auxiliary cooling circuit (19) is connected. 11
    [7]
    7. Liquid cooling system (K) according to one of claims 1 to 6, characterized in that the second cooling space (6) via a second coolant line (23) to the main cooling circuit (18) and / or the auxiliary cooling circuit (19) is connected, preferably in the second coolant line (23) of the vehicle heater (15) is arranged.
    [8]
    8. Liquid cooling system (K) according to one of claims 1 to 7, characterized in that at least one in the cylinder block (4) arranged third cooling chamber (8) via at least one passage (21) with the first cooling chamber (5) in the cylinder head (3) connected is.
    [9]
    9. Liquid cooling system (K) according to claim 8, characterized in that the third cooling chamber (8) via a third coolant line (24) to the main cooling circuit (18) is connected, wherein the connection (25) with the main cooling circuit (18) upstream of the Coolant cooler (17) is arranged.
    [10]
    10. Liquid cooling system (K) according to claim 9, characterized in that in the third coolant line (24) a single-acting thermostatic valve (26) is arranged.
    [11]
    11. Liquid cooling system (K) according to one of claims 1 to 10, characterized in that the third cooling chamber (8) via a fourth coolant line (27) with the auxiliary cooling circuit (19) and / or the first coolant line (22) is connected.
    [12]
    12. Liquid cooling system (K) according to claim 11, characterized in that in the fourth coolant line (27) a single-acting thermostatic valve (28) is arranged.
    [13]
    13. Liquid cooling system (K) according to claim 11, characterized in that in the region of a crossing point (30) of the first coolant line (22), the fourth coolant line (24) and the secondary cooling circuit (19), a second double-acting thermostatic valve (30) is arranged , 2012 07 26 Fu · * ** »··· ······································· * * ♦ * · · · "• * '♦" * ·· "* · Μ



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    FOLLOW-UP • «« * • · «* • · • *« ·· < * ·



    REPLACED «· • · * ·« ·



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    FOLLOWING »·« * »« * «· • · · * * C fvtf * *» * * • ················· ·· tt ··





    Fig. 12

    | POSSIBLE * 4 m «• ί * * * * * * * * f * * * * t * * * * · · * * * * * * *« # «· i ·» «i «· · · * * # * # T *« ··· * ·



    POSSIBLE REVIEW ································································································································································································································· · · 4 44 44 4 444 «4 44

    SUBSEQUENT
    类似技术:
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    同族专利:
    公开号 | 公开日
    CN104685180A|2015-06-03|
    AT513175B1|2014-10-15|
    CN104685180B|2018-07-10|
    WO2014016177A1|2014-01-30|
    US20150211399A1|2015-07-30|
    DE112013003684A5|2015-04-30|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
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    EP0856650A1|1997-02-03|1998-08-05|Honda Giken Kogyo Kabushiki Kaisha|Engine cooling system for outboard motor|
    US20050087154A1|2003-10-27|2005-04-28|Hayman Alan W.|Cylinder head with integrated exhaust manifold|
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    AT500442B1|2005-07-19|2008-06-15|Avl List Gmbh|CYLINDER HEAD FOR AN INTERNAL COMBUSTION ENGINE|
    GB2429763A|2005-09-02|2007-03-07|Ford Global Tech Llc|Cooling system comprising heat exchangers for motor vehicle cold start operation|
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    EP1900919B1|2006-09-13|2011-03-02|Ford Global Technologies, LLC|Coolant circuit|
    DE102010001803A1|2010-02-11|2011-08-11|Behr GmbH & Co. KG, 70469|Circuit arrangement for motor vehicle, has protecting unit for dethrottling coolant flow rate that passes through exhaust manifold|
    DE102010002082B4|2010-02-18|2013-09-19|Ford Global Technologies, Llc|Separately cooled exhaust manifold to maintain a no-flow strategy of the cylinder block coolant jacket|
    JP5526982B2|2010-04-27|2014-06-18|株式会社デンソー|Internal combustion engine cooling device|
    AT510741B1|2010-11-18|2014-11-15|Avl List Gmbh|POWER GENERATION UNIT|WO2018217634A1|2017-05-23|2018-11-29|Cummins Inc.|Engine cooling system and method for a spark ignited engine|
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50298/2012A|AT513175B1|2012-07-26|2012-07-26|Liquid cooling system for an internal combustion engine of a vehicle|ATA50298/2012A| AT513175B1|2012-07-26|2012-07-26|Liquid cooling system for an internal combustion engine of a vehicle|
    US14/417,264| US20150211399A1|2012-07-26|2013-07-17|Liquid cooling system for an internal combustion engine of a vehicle|
    CN201380050061.2A| CN104685180B|2012-07-26|2013-07-17|For the liquid-cooling system of vehicle internal combustion engine|
    DE201311003684| DE112013003684A5|2012-07-26|2013-07-17|Liquid cooling system for an internal combustion engine of a vehicle|
    PCT/EP2013/065080| WO2014016177A1|2012-07-26|2013-07-17|Liquid cooling system for an internal combustion engine of a vehicle|
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