• 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 cooling system (4) for an internal combustion engine having at least one cylinder head (1) which is connected via a cylinder head sealing surface (28) to at least one cylinder block (2), with at least one first cooling jacket (5) arranged in the cylinder head (1). which is fluidly connected to at least one coolant inlet (27) and at least one first coolant outlet (19), and at least one second cooling jacket (6) arranged in the cylinder block (2) and having at least one second coolant outlet (20) in the cylinder head (1). is connected, wherein the first and the second cooling jacket (5, 6) via at least one - preferably through an opening (17a) in the cylinder head sealing surface (28) extending - Verbindungsströmungsweg (17) connected to each other and successively flowed through by a liquid coolant, and wherein the coolant flow through the second cooling jacket (6) via at least a first valve (8), preferably ei n thermostatic valve, is controllable, which blocks the coolant flow through the second cooling jacket (6) in a first valve position and releases in at least one second valve position. In order to enable a rapid heating of the coolant with optimum cooling of the internal combustion engine, it is provided that the first cooling jacket (5) can be flowed through in a transverse direction of the internal combustion engine.
    公开号:AT514793A1
    申请号:T50587/2013
    申请日:2013-09-16
    公开日:2015-03-15
    发明作者:Reinhard Biller；Christof Knollmayr；Gernot Fuckar
    申请人:Avl List Gmbh；
    IPC主号:
    专利说明:

    The invention relates to a cooling system for an internal combustion engine having at least one cylinder head connected to at least one cylinder block via at least one cylinder head sealing surface having at least one first cooling jacket disposed in the cylinder head fluidly connected to at least one coolant inlet and at least one first coolant outlet and at least one second cylinder block disposed therein A cooling jacket connected to at least a second coolant outlet, wherein the first and second cooling jackets are interconnected via at least one connecting flow path, preferably through an opening in a cylinder head sealing surface, and sequentially flowed through by a liquid coolant, and wherein the coolant flow through the second cooling jacket is via at least a first valve , Preferably, a thermostatic valve, is controllable, which durc in a first valve position, the coolant flow h blocks the second cooling jacket and releases in at least one second valve position.
    From GB 2 348 485 A there is known an internal combustion engine having a cylinder head and a cylinder block, wherein the cylinder head and the cylinder block each have a cooling jacket. The cooling jacket of the cylinder block is in fluid communication with the cooling jacket of the cylinder head, the coolant entering the cooling jacket of the cylinder head and flowing from the cooling jacket of the cylinder head into the cooling jacket of the cylinder block.
    EP 1 258 609 A2 discloses a similar water-cooled internal combustion engine with a cooling jacket in the cylinder head and a cooling jacket in the cylinder block, wherein in the cold state, the coolant is passed only through the cooling jacket of the cylinder head and in the warm state additionally through the cooling jacket of the cylinder block and a cylinder block downstream radiator. The coolant from the cooling jacket of the cylinder head flows directly into the return line leading to the coolant pump.
    In both GB 2 348 485 A and EP 1 258 609 A2, the coolant inlet and outlet of the cylinder head cooling jacket are located at different ends of the cylinder head, whereby the cooling jacket of the cylinder head is flowed longitudinally. This requires a relatively large cooling jacket cross section in the cylinder head. The necessary relatively large volume of coolant results in the disadvantage of relatively long heating times of the coolant.
    EP 2 562 379 A1 describes a separate coolant circuit for an internal combustion engine, wherein a cylinder head water jacket and an engine block water jacket are provided. The separate coolant circuit includes a pump, a radiator, a control, an exhaust housing, and a heater wherein coolant circulates in the separate coolant. The control element is connected downstream of the cylinder head water jacket and has a thermostat and a proportional valve separated therefrom. Via the control element, the coolant can be supplied either to a radiator or to the engine block water jacket. Both the cylinder head water jacket and the cylinder block water jacket are flowed through longitudinally. This longitudinal flow, as well as a relatively large number of required external lines between the cylinder head water jacket and the cylinder block water jacket have an adverse effect on the coolant volume.
    The object of the invention is to avoid these disadvantages and to improve the cooling and heating behavior.
    According to the invention, it is achieved that the first cooling jacket, preferably also the second cooling jacket, can be flowed through in a transverse direction of the internal combustion engine, preferably at least one collecting chamber extending substantially in the longitudinal direction of the internal combustion engine and / or in the flow path between the first cooling jacket and the first coolant outlet the coolant inlet and the first cooling jacket is arranged a substantially horizontally extending in the longitudinal direction of the engine manifold space.
    In the longitudinal direction of the internal combustion engine, a direction parallel to the crankshaft axis is to be understood here. The transverse direction of the internal combustion engine is understood to mean a direction approximately normal to the crankshaft axis and normal to the cylinder axis.
    By passing through the first cooling jacket in the transverse direction of the internal combustion engine, on the one hand external lines between the first and the second cooling jacket can be omitted and on the other hand the cross section of the first cooling jacket - viewed normal to the crankshaft axis - can be kept small, whereby the coolant volume can be drastically reduced. The second cooling jacket is activated or deactivated as required, wherein the first cooling jacket of the cylinder head is always flowed through by the full amount of coolant. Thus, sufficient heat removal from the thermally highly stressed areas around the exhaust valves in the fire deck can be ensured in each operating range of the internal combustion engine.
    The collecting space for the coolant can be integrated into the cylinder block according to a first embodiment variant of the invention. The collecting space is hydraulically separated from the second cooling jacket within the cylinder block. This variant has the advantage that no constructive measures have to be taken in the cylinder head to accommodate the collecting space, which simplifies the production of the cylinder head.
    In a second embodiment of the invention it is provided that the collecting space is arranged in the cylinder head, wherein preferably the collecting space between the outlet channels and the cylinder head sealing surface is arranged. This arrangement has the advantage that the exhaust ducts, and possibly also an exhaust manifold integrated in the cylinder head, can additionally be cooled by the collecting space integrated in the cylinder head.
    The plenum may extend substantially the entire length of the cylinder head or cylinder block
    In order to allow sufficient heat transfer from thermally critical areas of the cylinder head and rapid warm up after a cold start in any operating range, it is advantageous if the first coolant outlet of the cylinder head is continuously connected to the return line of the cooling system flow and the second coolant exit of the cylinder head via the first valve switchable with a return line of the cylinder head Cooling system is connected.
    It may be provided that a mixing chamber of the first valve has a first and a second valve inlet and a valve outlet and the first coolant outlet of the cylinder head with the first valve inlet, the second coolant outlet with the second valve inlet and the valve outlet with a return line of the cooling system is fluidly connected, preferably by the first valve only the flow connection between the second valve inlet and the valve outlet is switchable.
    The return line may comprise a long return train having at least one radiator and a short return train bypassing the radiator, wherein the flow of coolant through the short or long return train through at least one second valve, preferably a thermostatic valve, may be controlled. Via the second valve, the coolant can be fed back either directly or via a cooler of the coolant pump.
    In all embodiments of the invention, the first cooling jacket flows through the entire coolant flow. Downstream of the first cooling jacket, the first valve is arranged, which in a first position completely blocks the outflow of the coolant from the second cooling jacket of the cylinder block. Thus, all of the coolant is fed directly to the return line of the cooling system. When the first valve moves to the second position, a partial flow of the coolant is directed into the second cooling jacket of the cylinder block. After passing through the second cooling jacket, the coolant is returned to the cylinder head via an overpass passage where it is supplied via the first valve to the coolant system.
    In a further embodiment of the invention it can be provided that the coolant pump is driven by a camshaft preferably arranged in the cylinder head. This measure has the advantage that the coolant volume between the coolant pump and the first cooling jacket can be reduced to a minimum, which has an advantageous effect on the heating time of the coolant.
    A particularly low coolant volume and thus very short heating times can be achieved if the coolant inlet, the first coolant outlet and the second coolant outlet are arranged in the cylinder head.
    The invention will be explained in more detail below with reference to FIGS.
    Show it:
    Fig. 1, the cooling jackets of a cooling system according to the invention in a first
    Variant in an oblique view,
    1a shows the second cooling jacket in a plan view of the cylinder head density plane,
    Fig. 2, the cooling jackets in a further oblique view
    3 shows the cooling system according to the invention in a schematic representation in a first embodiment,
    4 shows the cooling system from FIG. 3 in a first switching position, FIG.
    Fig. 5, the coolant flow in the first switching position in one
    Cross section through the cooling jackets,
    6 shows the cooling system from FIG. 3 in a second switching position, FIG.
    Fig. 7, the coolant flow in the second switching position in one
    Cross section through the cooling jackets,
    8 shows the cooling system from FIG. 3 in a third switching position, FIG.
    Fig. 9, the coolant flow in the third switching position in one
    Cross section through the cooling jackets,
    10 shows an inventive cooling system in a second embodiment variant in an oblique view,
    10a the second cooling jacket in a plan view of the cylinder head density plane,
    11 shows the cooling system according to the invention in a schematic representation in a second embodiment variant,
    12, the cooling system of FIG. 11 in a first switching position,
    Fig. 13, the coolant flow in the first switching position in one
    Cross section through the cooling jackets,
    14 shows the cooling system from FIG. 11 in a second switching position, FIG.
    Fig. 15, the coolant flow in the second switching position in one
    Cross section through the cooling jackets,
    FIG. 16 shows the cooling system from FIG. 11 in a third switching position, FIG.
    17 shows the coolant flow of the third switching position in a cross section through the cooling jackets, and
    Fig. 18, the cooling system of Fig. 11 in a side view.
    Functionally identical features are provided in the embodiments with the same reference characters.
    In FIGS. 4, 6, 8 and 12, 14, 16, non-flow elements of the cooling system 4 are not shown for clarity.
    The internal combustion engine comprises a cylinder head 1 and a cylinder block 2 for each of a plurality of cylinders 3, and a cooling system 4 with a liquid cooling medium. In the cylinder head 1, a first cooling jacket 5 is arranged, which serves for cooling thermally critical areas in the cylinder head 1. The cylinder block 2 has a second cooling jacket 6 which is fluidly connected to the first cooling jacket 5. The cooling jacket 5 is fluidly connected to a coolant inlet 27 and a first coolant outlet 19 of the cylinder head 1.
    Besides the first cooling jacket 5 and the second cooling jacket 6, the cooling system 4 further comprises a coolant pump 7, a first valve 8 formed as a thermostatic valve, a second valve 9 formed as a thermostatic valve, a radiator 10, an interior heater 11, an expansion tank 12, and an oil cooler 13 as shown in FIG Figs. 3 and 11 is shown. Furthermore, the cooling system has a collecting space 14a or 14b extending in the longitudinal direction of the cylinder block 2 and the cylinder head 1, respectively, which is arranged either in the cylinder block 2 (FIGS. 1 to 9) or in the cylinder head 1 (FIGS. 10 to 17).
    The components coolant pump 7, first thermostatic valve 8 and second valve 9 can be combined in a pump / thermostat module. The coolant pump 7 is advantageously arranged in or on the cylinder head 1 and is driven by an overhead camshaft, which is indicated by the camshaft axis 15 in FIG.
    From the coolant pump 7, the coolant is passed to the first cooling jacket 5 via a distributor chamber 16 extending in the longitudinal direction of the internal combustion engine inside the cylinder head 1. The distribution space 16 is disposed on the exhaust side E of the cylinder head 1 in the embodiments. The inlet side is indicated by reference I. From the distribution space 16, the coolant flows in the transverse direction of the cylinder head 1 through the first cooling jacket 5, whereby regions subjected to high thermal stress around the outlet valves etc. are cooled. The first cooling jacket 5 is in fluid communication with the second cooling jacket 6 via openings 17a in the cylinder head sealing surface 28 and in the cylinder head gasket (not shown). The first cooling jacket 5 is further connected to the collecting space 14a or 14b via collecting channels 18, wherein at least one collecting channel 18 per cylinder 3 is provided. The collecting space 14a, 14b is connected to a first outlet 19 arranged in the cylinder head 1. Furthermore, the second cooling jacket 6 of the cylinder block 2 is flow-connected via a riser 21 to a second outlet 20 in the cylinder head 1.
    In the embodiment variant shown in FIGS. 1 to 9, the cylinder head gasket has openings 18a, through which the coolant passes through the collection channels 18 into the collecting space 14a. Furthermore, the cylinder head gasket in the region of an end face of the internal combustion engine has an over-access opening 18b, via which the coolant passes from the collecting space 14a in the cylinder block 2 into an outlet channel 22 in the cylinder head 1 to the first outlet 19. The openings 17a, 18a and the transfer opening 18b are clearly shown in FIG. la to take.
    In contrast, in the embodiment shown in Figs. 10 to 17, with a collecting space 14b integrated in the cylinder head 1, the openings 18a and the transfer opening 18b in the cylinder head gasket may be omitted. The collecting space 14b is arranged below, ie on the side facing the cylinder block 2, the exhaust ducts 29 or an exhaust manifold 30 integrated in the cylinder head 1 (see FIG. 18). The exhaust ducts are thus limited on the one hand by the distribution chamber 16 upwards and the collection chamber 14b down, whereby a particularly high heat removal from the region of the outlet channels is made possible (see Fig. 10).
    In both embodiments, first coolant outlet 19 and second coolant outlet 20 are provided with first and second valve inlets 8a, 8b of the first
    Valve 8, wherein from the valve outlet 8c of the first valve 8, a return line 25 via a short return line 23 and a long return line 24 leads back to the coolant pump 7. In the long return line 24, the radiator 10 is arranged to cool the coolant. The path through the short return line 23 and the long return line 24 is controlled by the second valve 9. The flow direction of the coolant is indicated by arrows. For both embodiments, the following applies: The entire coolant flows through the first cooling jacket 5 of the cylinder head 1, through which the first valve 8 flows, depending on the temperature of the coolant, the second cooling jacket 6 in the cylinder block 2 by a part of the coolant entering the first cooling jacket 5. Via the second valve 9, the coolant either via the radiator 10 or directly - bypassing the radiator 10 - returned to the coolant pump 7.
    The coolant flows are indicated by arrows.
    First embodiment variant (FIGS. 1 to 9)
    In the first switching position of the cooling system 4 shown in Fig. 4, the first valve 8 and the second valve 9 are in a first valve position, wherein the first switching positions are associated with the cold condition of the coolant. The coolant is conveyed by the coolant pump 7 into the first cooling jacket 5 of the cylinder head 1. In the first valve position of the first valve 8, the first coolant outlet 19 is connected to the valve outlet 8c of the first thermostatic valve 8, but the second coolant outlet 20 is separated from the valve outlet 8c of the first valve 8. Due to the blocked outflow from the second cooling jacket 6, the coolant can not flow from the first cooling jacket 5 into the second cooling jacket 6, as a result of which only the first cooling jacket 5 in the cylinder head 1 is flowed through by the coolant. The entire coolant passes from the first cooling jacket 5 via the collecting channels 18 into the collecting space 14a arranged in the cylinder block 2 and flows from the collecting space 14a via the transfer opening 18b and the discharge channel 22 to the first coolant outlet 19 of the cylinder head 1 and further to the first valve inlet 8a of the first valve 8. The second Valve 9 is in the first valve position shown in Fig. 4, whereby the coolant drain from the radiator 10 is closed. Thus, the coolant from the first valve 8 passes directly back to the coolant pump 7. FIG. 5 shows the flow between the distributor chamber 16 and the collecting space 14a for this first switching position of the cooling system 4.
    Fig. 6 shows the cooling system 4 with a warm engine, wherein the first valve 8 in the second valve position and the second valve 9 is still in the first valve position. The second valve position of the first valve 8 is associated with warm or hot coolant temperatures. In the second valve position of the first valve 8, both the first valve inlet 8a and the second valve inlet 8b of the first valve 8 are fluidly connected to the valve outlet 8c. Thereby the outflow from the second valve outlet 20 and thus from the second cooling jacket 6 of the cylinder block 2 is released. The coolant now flows both via the collecting channels 18 into the collecting space 14a, and via the connecting flow paths 17 and the openings 17a of the cylinder head sealing surface 28 and the cylinder head gasket in the cooling jacket 6 in the second cylinder block 2. From the second cooling jacket 6 the coolant passes via the branch channel 21 to the second Outlet 20 of the cylinder head 1. Within the first valve 8 takes place in a mixing chamber 26 of the first valve 8, the merging of the flowing through the first cooling jacket 5 and the second cooling jacket 6 sub-flow. Via the second valve 9 located in the first valve position, the coolant is returned directly to the coolant pump 7. FIG. 7 shows the flow between distributor chamber 16 and second cooling jacket 6 or collecting chamber 14a for this second switching position of the cooling system 4.
    If the temperature of the internal combustion engine and thus the temperature of the coolant continue to increase, the second valve 9 switches to the second valve position, as shown in FIG. 8. In this second valve position, the drain from the radiator 10 is released to the coolant pump 7, whereby the coolant flows through the long return line 24 and the radiator 10. The flow through the first and the second cooling jacket 5, 6, takes place analogously to FIGS. 6 and 7, as shown in FIG. 9 is shown.
    Second Embodiment (FIGS. 10 to 17)
    This embodiment differs from the first embodiment shown in FIGS. 1 to 9 in that the collecting space 14b is now arranged not in the cylinder block 2 but in the cylinder head 1. This has the advantage that the coolant volume can be further reduced and the cylinder block 2 can be made simpler. As can be seen in Fig. 10a, substantially fewer openings 17a in the cylinder head sealing surface 28 are required.
    Figures 12 and 13 show a first shift position of the cooling system 4 for the second embodiment, with the first valve 8 and the second valve 9 each in the first valve position, with the first valve positions associated with the cold engine and the cold coolant, respectively. The coolant flows from the coolant pump 7 into the distributor chamber 16 and further into the first cooling jacket 5 of the cylinder head 1, which it flows through in the transverse direction. Thereafter, the coolant passes through collecting channels 18 in the also arranged in the cylinder head 1 collecting space 14b. Since the flow connection between the second valve inlet 8b and the valve outlet 8c is blocked by the first valve 8, the outflow from the second cooling jacket 6 of the cylinder block 2 is prevented and thus an overflow of the coolant from the first cooling jacket 5 into the second cooling jacket 6 is prevented. The entire coolant of the first cooling jacket 5 passes from the collecting space 14b to the first coolant outlet 19 of the cylinder head 1, which is connected to the first valve inlet 8 of the first valve 8. Since the flow communication between the first valve inlet 8a and the valve outlet 8c is opened within the first valve 8 and the outflow from the radiator 10 is blocked by the first valve position of the second valve 9, the coolant flowing out of the first cooling jacket 5 flows through the short return line 23 back to the coolant pump 7.
    As soon as the coolant has exceeded a first switching temperature for the first thermostatic valve 8, the first valve 8 is switched to the second valve position, as shown in FIG. 14. In this position, both the flow connection between the first valve inlet 8a and the valve outlet 8c of the first valve 8, as well as the flow connection between the second valve inlet 8b and the valve outlet 8c are released. As a result, part of the coolant flows from the first cooling jacket 5 of the cylinder head 1 via the connecting flow paths 17 into the second cooling jacket 6 and from there via the riser 21 to the second coolant outlet 20 of the cylinder head 1. After merging the coolant partial streams originating from the first cooling jacket 5 and the second cooling jacket 6 in the mixing chamber 26 of the first valve 8, the coolant is returned via the short return line 23 to the coolant pump 7. FIG. 15 shows the flow between distributor space 16 and second cooling jacket 6 or collecting space 14b for this second switching position of the cooling system 4.
    If the internal combustion engine and thus the coolant are further heated, the second valve 9 also switches from a second switching temperature into the second valve position, which is shown in FIG. 16. As a result, the short return line 23 is blocked and the drain from the radiator 10 to the coolant pump 7 is released. The coolant leaving the first valve 8 now flows through the long return line 24 through the radiator 10 and, after passing through the second valve 9, passes to the coolant pump 7. The flow through the first cooling jacket 5 and the second cooling jacket 6 shown in FIG. 17 is analogous to FIGS. 14 and 15.
    The second embodiment variant with the collecting space 14b arranged in the cylinder head 1 between at least one outlet channel 29 and the cylinder head sealing surface 28 of the cylinder head 1 has the advantage that the coolant volume of the cooling system 4 can be made very small, and on the other hand a particularly high heat removal from the region of the outlet channels 29 possible is, in particular, when the exhaust manifold 30 is integrated into the cylinder head 1, as shown in FIG. 18 can be seen. This, in turn, has a particularly beneficial effect on the heating time of the coolant during a cold start of the internal combustion engine.
    权利要求:
    Claims (10)
    [1]
    A cooling system (4) for an internal combustion engine having at least one cylinder head (1) connected to at least one cylinder block (2) via a cylinder head sealing surface (28), comprising at least one first cooling jacket (5) disposed in the cylinder head (1) at least one coolant inlet (27) and at least one first coolant outlet (19) and at least one in the cylinder block (2) arranged second cooling jacket (6) which is connected to at least a second coolant outlet (20), wherein the first and the second cooling jacket ( 5, 6) via at least one - preferably through an opening (17a) in the cylinder head sealing surface (28) extending - Verbindungsströmungsweg (17) connected to each other and flowed through by a liquid coolant, and wherein the coolant flow through the second cooling jacket (6) via at least one first valve (8), preferably a thermostatic valve, is controllable, which in a first valve position blocks the coolant flow through the second cooling jacket (6) and releases in at least one second valve position, characterized in that the first cooling jacket (5), preferably also the second cooling jacket (6), can flow in a transverse direction of the internal combustion engine, preferably in the flow path between the first cooling jacket (5) and the first coolant outlet (19) extending at least substantially in the longitudinal direction of the internal combustion engine collecting space (14a, 14b) and / or in the flow path between the coolant inlet (27) and the first cooling jacket (5) substantially in the longitudinal direction Internal combustion engine extending Verteilerraum (16) is arranged.
    [2]
    2. Cooling system (4) according to claim 1, characterized in that the collecting space (14a) is arranged in the cylinder block (2).
    [3]
    Cooling system (4) according to claim 1, characterized in that the collecting space (14b) is arranged in the cylinder head (1).
    [4]
    A cooling system (4) according to claim 3, characterized in that the collecting space (14b) is interposed between at least one exhaust passage (29) and / or exhaust manifold (30) integrated with the cylinder head (1) and the cylinder head sealing surface (28) of the cylinder head (1 ) is arranged.
    [5]
    5. Cooling system (4) according to one of claims 1 to 4, characterized in that the first Kühlmitte laustritt (19) of the cylinder head (1) is constantly fluidly connected to at least one return line (25) of the cooling system (4).
    [6]
    6. Cooling system (4) according to one of claims 1 to 5, characterized in that the second coolant outlet (20) of the cylinder head (1) via the first valve (8) is switchably connected to a return line (25) of the cooling system (4).
    [7]
    7. cooling system (4) according to one of claims 1 to 6, characterized in that a mixing chamber (26) of the first valve (8) has a first and a second valve inlet (8a, 8b), and a valve outlet (8c) and the first coolant outlet (19) of the cylinder head (1) to the first valve inlet (8a), the second coolant outlet (20) to the second valve inlet (8b) and the valve outlet (8c) with at least one return line (25) of the cooling system (4) is fluidly connected, preferably by the first valve (8) only the flow connection between the second valve inlet (8b) and the valve outlet (8c) is switchable.
    [8]
    8. Cooling system (4) according to one of claims 5 to 7, characterized in that the return line (25) has a long return line (24) with at least one radiator (10) and a radiator (10) bypassing short return line (23), wherein the flow of coolant through the short or long return train (23, 24) is controllable by at least one second valve (9), preferably a thermostatic valve.
    [9]
    9. Cooling system (4) according to one of claims 1 to 8, characterized in that the coolant pump (7) by a preferably in the cylinder head (1) arranged camshaft is driven.
    [10]
    10. Cooling system (4) according to one of claims 1 to 9, characterized in that at least one coolant inlet (27) and / or at least one first coolant outlet (19) and / or at least one second coolant outlet (20) are arranged in the cylinder head (1).
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    同族专利:
    公开号 | 公开日
    AT514793B1|2015-06-15|
    DE112014004232A5|2016-06-09|
    US20160230639A1|2016-08-11|
    CN105723078B|2019-04-12|
    US10858980B2|2020-12-08|
    WO2015036584A1|2015-03-19|
    CN105723078A|2016-06-29|
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50587/2013A|AT514793B1|2013-09-16|2013-09-16|Cooling system for an internal combustion engine|ATA50587/2013A| AT514793B1|2013-09-16|2013-09-16|Cooling system for an internal combustion engine|
    US15/022,128| US10858980B2|2013-09-16|2014-09-15|Cooling system for an internal combustion engine|
    DE112014004232.3T| DE112014004232A5|2013-09-16|2014-09-15|Cooling system for an internal combustion engine|
    PCT/EP2014/069576| WO2015036584A1|2013-09-16|2014-09-15|Cooling system for an internal combustion engine|
    CN201480061633.1A| CN105723078B|2013-09-16|2014-09-15|Cooling system for internal combustion engine|
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