• 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 an internal combustion engine, in particular a large diesel engine, having at least one individual cylinder (1) with a cylinder housing (3) receiving a cylinder housing (2) and with at least one single cylinder head (4 ), wherein the cylinder liner (3) is surrounded by at least one cooling jacket (5, 6) which is in flow communication with at least one cooling space (14, in the single cylinder head (4).) In order to enable high efficiencies and low exhaust gas values, it is proposed that the Cylinder liner (3) by a first and a second cooling jacket (5, 6) is surrounded, wherein the first cooling jacket (5) from the second cooling jacket (6) within the cylinder housing (2) is fluidly separated.
    公开号:AT513053A1
    申请号:T50248/2012
    申请日:2012-06-26
    公开日:2014-01-15
    发明作者:Gerhard Ing Maier；Rene Koegl
    申请人:Avl List Gmbh；
    IPC主号:
    专利说明:

    1 1 56437
    The invention relates to an internal combustion engine, in particular large diesel engine, with at least a first and a second cooling circuit, with at least one individual cylinder with a cylinder liner female housing, and with at least one single cylinder head, wherein the cylinder liner is surrounded by at least one cooling jacket, which at least one Refrigerator is fluidly connected in the single cylinder head.
    From DE 10 2004 047 452 Al a cooling system of an internal combustion engine having a first cooling circuit of a cylinder head and a second cooling circuit of an engine block is known, which is interconnected. A controllable actuating means for regulating a division of a coolant flow is present between the first and second cooling circuits.
    A similar cooling system with a first cooling circuit for cooling the cylinder head and a second cooling circuit for cooling the cylinder block is known from EP 1 035 306 A2.
    DE 10 2004 024 289 A1 describes a cooling system for a vehicle with a high-temperature circuit and a low-temperature circuit. The high-temperature circuit is provided for cooling the Brennkrafftmaschine, the low-temperature circuit is used to cool a charge air cooler and possibly an oil cooler.
    From DE 10 2011 101 337 Al a circuit arrangement with a low-temperature circuit for cooling ancillaries of an internal combustion engine and a high-temperature circuit for cooling the internal combustion engine and other ancillary units is known.
    Furthermore, it is known to use a separate cooling circuit in large engines for the cooling of valve seat rings.
    Based on the requirement to operate today's large engines with ever better efficiencies and lower emissions, it is necessary to adapt the medium-pressure and Zünddruckpotentiale the internal combustion engine to the improved charging technology (two-stage charging). This means that more heat has to be dissipated in area 2 [102012/50248 of the cylinder liner and the firebox of the cylinder head.
    The object of the invention is to improve the heat dissipation in the area of the fire deck and the cylinder liner for large engines.
    According to the invention this is achieved in that the cylinder liner is surrounded by a first and a second cooling jacket, wherein the first cooling jacket is fluidly separated from the second cooling jacket within the cylinder housing.
    In order to achieve effective cooling of the crown ring of the cylinder liner, it is advantageous if the first cooling jacket with at least a first cooling chamber and the second cooling jacket with at least a second cooling space in the single cylinder head is fluidly connected, wherein preferably the first cooling jacket via at least one, preferably annular, first flow passage within the cylinder housing with at least one bushing surrounding the land section of the cylinder liner, preferably annular, first cooling channel is fluidly connected. The first cooling channel is preferably at least partially, preferably predominantly, disposed between the first cooling jacket and the single cylinder head. This allows excellent cooling of the cylinder in the Feuerstegringbereich, in particular, when the cylinder liner has at least one aushegende from the first Kühikanal radial blind bore, radial through hole or preferably tangential milled.
    The first cooling channel is flow-connected via at least a first Überträttsöffnung between the cylinder housing and single cylinder head with the first cooling chamber in the single cylinder head.
    The first cooling jacket may be partially formed by the cylinder housing surrounding the cylinder housing, partially by the cylinder liner itself, wherein preferably the second cooling jacket is formed by the single cylinder housing. A particularly good cooling of the Feuerstegringbereiches results further when the second cooling jacket surrounds the first cooling channel substantially. 3 3 [10 2012/50248 tPrirtted: 27-06-2Ö12
    In order to optimally cool the area of the fire deck of the individual cylinder head independently of the cylinder housing, it is provided within the scope of the invention that the second cooling jacket is flow-connected to at least one second cooling space in the single cylinder head via at least one preferably annular second overflow opening between cylinder housing and single cylinder head.
    The second cooling dream preferably has at least one annular second cooling passage surrounding a valve seat ring and at least one axial connecting passage adjacent to a central component opening into the combustion chamber, preferably an injector, and radial connecting passages between the second and third cooling passages and leading to the second cooling passages or axial connecting passages radial connection holes in the fire deck of the single cylinder head, wherein preferably the components of the second cooling chamber, at least predominantly in a normal plane to the cylinder axis in the fire deck of the single cylinder head are arranged.
    Furthermore, it can be provided that the axial connection channel is connected in fluid communication with at least one partial cooling space arranged between the first and second cooling chambers in the single cylinder head, which preferably surrounds at least one inlet and / or outlet channel, wherein the partial cooling space is separated from the first cooling water space by an intermediate deck, and wherein the Part cooling chamber via at least a second flow passage in the intermediate deck with the first cooling water space is fluidly connected.
    In order to enable a precisely defined heat dissipation in the region of the central component, it is advantageous if an annular gap is formed between the intermediate deck and the central component, or a sleeve receiving the central component, an annular diaphragm being arranged in the annular gap, wherein preferably the annular aperture is firmly connected to the sleeve. The panel may be formed as a metal or plastic cover.
    The cooling system with the two cooling circuits is thus integrated into the castings of the cylinder housing or the single cylinder head.
    In principle, the two cooling circuits can be operated at the same temperature.
    However, it is particularly advantageous if the two cooling circuits have different temperature levels, wherein the first cooling circuit is designed as a high-temperature circuit and the second cooling circuit as a low-temperature circuit, wherein the low-temperature circuit has a lower temperature level than the high-temperature circuit.
    The high-temperature circuit is formed by the first cooling circuit, which has an inlet temperature in the first coolant jacket of about 85 ° C.
    The coolant flows around the Zyiinderlaufbuchse in the upper region, in order to effect the cooling of the Feuerstegringbereiches and the piston ring portion in the region of the first Kolbenringnut sufficiently, and then flows through the first transfer opening in the first cooling chamber of the single cylinder head.
    The second cooling circuit forms the low-temperature circuit, which is temperature-controlled so that the inlet temperature in the second cooling jacket is approximately at 50 ° to 70 ° C. The coolant flows through the fire deck in the single cylinder head in a normal plane arranged substantially normal to the cylinder axis. The cooling bores and cooling channels are very close to the combustion chamber roof of the building.
    Single cylinder head arranged and also supply the valve seat rings of the intake and exhaust valves with coolant. The flow is directed to the center of the single cylinder head, is deflected in the injector sleeve by means of a diaphragm and then flows through the lower part of the cooling chamber of the single cylinder head in the opposite direction to the connecting holes radially outward. The flows of the first cooling circuit and the second cooling circuit are brought together in a targeted manner in the region of the upper first cooling space and then emerge from the Zyiinderkopf together at the opening to the water collecting line. The coolant of the second cooling circuit can be removed from the first cooling circuit. By arranging at least one mixing valve between the first cooling circuit and the second cooling circuit (before entry into the cooling jackets of the cylinder housing) an admixing of two cooling circuits is made possible. As a result, warm water of the first cooling circuit can be mixed with the second cooling circuit, for example, in cold engine or idling, the mixing valve can be controlled temperature-dependent.
    Characterized in that two separate cooling circuits are provided in the cylinder housing, and by the two separate cooling flow guides in the single cylinder head, 5 5ÖÖ2ÖT ^ 50248 27 ^ 06-2012 (EÖ14
    Areas of the top land, the fire deck and the intake and exhaust ports in the single cylinder head are cooled separately and selectively with the optimum coolant temperature.
    The invention is explained in more detail below with reference to FIGS.
    He show
    1 shows an internal combustion engine according to the invention in a longitudinal section in a first embodiment,
    2 shows this internal combustion engine in a meridian section,
    3 shows an internal combustion engine according to the invention in a second embodiment in a meridian section,
    4 shows this internal combustion engine in a section along the line IV-IV in Fig. 3,
    Fig. 5 "The" Breririkrä- mäschine In a section in accordance with the M ^ -Vln "Fig73runfl".
    Fig. 5, the cooling system of the internal combustion engine according to the invention.
    The internal combustion engine has a plurality of individual cylinders 1, each individual cylinder 1 having a cylinder housing 2 and a cylinder liner 3. The cylinder housing 2 is closed by a single cylinder head 4 upwards.
    The cylinder liner 3 is surrounded by a first cooling jacket 5 and a second cooling jacket 6, wherein the first cooling jacket 5 and second cooling jacket 6 belong to different cooling circuits 31, 32 and are separated within the cylinder housing 2, so that the cooling media are supplied separately to the single cylinder head 4. The first cooling jacket 5 starts from a first supply channel 5a of the first cooling circuit 31, the second cooling jacket 6 from a second supply channel 6a of the second cooling circuit 32. The first cooling jacket 5 surrounds the cylinder liner 3 and is connected via an annular first flow passage 7 with an annular first cooling channel 8 and tangential Einfräsungen 9 or radial blind holes or radial through-holes in the cylinder liner 3 for cooling the Feuerstegringbereiches 10 in 6 6 [10 2012 ^ 50248 fPrinted : 27 ^ 0 © -2012
    Flow connection. From the annular first cooling channel 8 is a transition channel 11 goes out, which via a first transfer opening 12 and a substantially parallel to the cylinder axis la formed riser 13 opens into the first cooling chamber 14. The annular first channel region 8 is surrounded by the second cooling jacket 6, which is formed in the cylinder housing 2. The second cooling jacket 6 is flow-connected via a second transfer passage 15 and at least one, for example, annular second transfer opening 16 between the cylinder housing 2 and the single cylinder head 4, as well as radial first connecting bores 17 with annular second cooling channels 18 for cooling the valve seat rings 43. The second cooling channels 18 are connected via radial connecting channels 19 with at least one axial connecting channel 20, which is arranged in the direction of the cylinder axis la adjacent to a sleeve 21 for receiving a central component, for example an injection nozzle. Furthermore, the second cooling jacket 6 is connected via radial second connecting bores 22 with at least one axial connecting channel 20. The second cooling channels 18 and the first and second connection bores 17 and 22 are arranged substantially in a normal plane ε in the fire deek 23 of the single cylinder head 4 and form together with the axial connection channels 20 from the second cooling circuit 32 fed second cooling chamber 24.
    The axial connection channels 20 are connected to a lower part of the cooling chamber 25, which is separated from the overlying first cooling chamber 14 by an intermediate deck 26. The partial cooling space 25 communicates with the first cooling space 14 via a second flow passage 27.
    The axial and radial connecting channels 19, 20 are preferably formed by bores.
    Between the intermediate deck 26 and the sleeve 21, an annular gap 28 is formed, in which an annular aperture 29 is inserted from metal or plastic.
    The panel 29 may be fixed to the sleeve 21, for example, welded or glued.
    FIG. 6 schematically shows the coolant system 30 of the internal combustion engine. The coolant system 30 has a first cooling circuit 31 and a second cooling circuit 32, wherein the first cooling circuit 31 is designed as a high-temperature circuit HT 7 (1Q2Ö12 / 50248 and the second cooling circuit 32 is designed as a low-temperature circuit NT. in the second cooling circuit 32, a second coolant pump 34. The coolant of the first cooling circuit 31 flows from the first coolant pump 33 to a as
    High-temperature charge air cooler formed first intercooler 35 and passes from this into the first cooling jacket 5 of the cylinder housing 2. The coolant of the second cooling circuit 32 is conveyed by the second coolant pump 34 to the designed as Niedertemperaturladeluftkühler second intercooler 36, from which it via the oil cooler 37 the second cooling jacket. 6 is supplied. The coolant flows through the cooling chambers of the cylinder housing 2 and the single cylinder head 4 in the manner described above, with the flows of the two cooling circuits 31, 32 unite in the single cylinder head 4 and leave the single cylinder head 4 via a common coolant manifold 38. Via a thermostatic valve 39, the coolant passes into a central system cooler 40. Downstream of the system cooler 40, the coolant flows are divided into the two partial flows of the first cooling circuit 31 and the second cooling circuit 32.
    The cooling circuit 31 is operated at about 85 ° C (inlet temperature in the first cooling jacket 5), wherein the coolant flows around the cylinder liner 3 in the upper region to cool the Feuerstegringbereich 10 and in the region of the first groove 9 of the piston ring area sufficient. Thereafter, the coolant of the first cooling circuit 31 flows into the single cylinder head 4 in the region of the first transfer opening 12.
    The second cooling circuit 32 is temperature-controlled so that the inlet temperature in the second cooling jacket 6 is in the range between 50 to 70 ° C. The coolant of the second cooling circuit 32 flows through the fire deck 23 of the single cylinder head 4 substantially in a normal plane ε to the cylinder axis la. The second cooling channels 18 and distributor bores 17 and 22 are arranged in the region of a normal plane ε on the cylinder axis la near the combustion chamber roof of the single cylinder head 4 and cool the valve seat rings 43 of the inlet and outlet valves. The flow is directed radially in the direction of the center of the single cylinder head 4, is deflected in the region of the sleeve 21 by means of the diaphragm 29 and flows through the lower part of the cooling chamber 25 in opposite directions to the distribution holes 17 and 22. The flows of the first and 8 8 [10 2012/50248 27-06-2012 IE014 second cooling circuit 31, 32 are specifically brought together in the region of the upper first cooling chamber 14 and then exit together from the single cylinder head 4 through the manifold 38. The second cooling circuit 32 can branch off from the low-temperature cooling circuit NT before it enters the second coolant jacket 6. By arranging the mixing valve 41 between the first and second cooling circuits 31, 32, admixing of both cooling circuits 31, 32 is made possible. For example, with a cold engine or idling, hot water from the high-temperature circuit HT may be mixed into the low-temperature circuit NT. The mixing valve 41 and the control valve 42 can be controlled depending on temperature.
    权利要求:
    Claims (29)
    [1]
    27-06-2012

    : 10 2012/50248 9 PATENT CLAIMS 1. Internal combustion engine, in particular large diesel engine, with at least a first and a second cooling circuit (31, 32), with at least one individual cylinder (1) with a cylinder housing (3) receiving the cylinder housing (2), and with at least one individual cylinder head (4), the cylinder liner (3) being surrounded by at least one cooling jacket (5, 6) which is fluidly connected to at least one cooling space (14) in the single cylinder head (4), characterized in that the cylinder liner (3) is surrounded by a first and a second cooling jacket (5, 6), wherein the first cooling jacket (5) from the second cooling jacket (6) within the cylinder housing (2) is fluidly separated.
    [2]
    2. Internal combustion engine according to claim 1, characterized in that the first cooling jacket (5) with at least a first cooling chamber (14) and the second cooling jacket (6) with at least one second cooling chamber (24) in the single cylinder head (4) is fluidly connected.
    [3]
    3. Internal combustion engine according to claim 1 or 2, characterized in that the first cooling jacket (5) via at least one, preferably annular, first flow passage (7) within the cylinder housing (2) with at least one area of the land (10) of the Zyiinderlaufbuchse (3 ), preferably annular, first cooling channel (8) is fluidly connected.
    [4]
    4. Internal combustion engine according to claim 3, characterized in that the first cooling channel (8) at least partially, preferably predominantly, between the first cooling jacket (5) and the single cylinder head (4) is arranged.
    [5]
    5. Internal combustion engine according to one of claims 3 or 4, characterized in that the Zyiinderlaufbuchse (3) at least one of the first cooling channel (8) outgoing radial blind hole through hole or preferably tangential - milled recess (9).
    [6]
    6. Internal combustion engine according to one of claims 3 to 5, characterized in that the first cooling channel (8) via at least one first iPrinted: 27-06- ^ 012 [E015 | 10 2012/50248 10 transfer opening (12) between the cylinder housing (2) and single cylinder head (4) is fluidly connected to the first cooling space (14) in the single cylinder head (4).
    [7]
    7. Internal combustion engine according to one of claims 1 to 6, characterized in that the first cooling jacket (5) is partially formed by the cylinder housing (2) and partially by the cylinder liner (3).
    [8]
    8. Internal combustion engine according to one of claims 1 to 7, characterized in that the second cooling jacket (6) through the cylinder housing (2) is formed.
    [9]
    9. Internal combustion engine according to one of claims 3 to 8, characterized in that the second cooling jacket (6) surrounds the first cooling channel (8) substantially.
    [10]
    10. Internal combustion engine according to one of claims 1 to 9, characterized in that the second cooling jacket (6) via at least one preferably annular second overflow opening (16) between the cylinder housing (2) and single cylinder head (4) with at least one second cooling chamber (24) in Single cylinder head (4) is fluidly connected.
    [11]
    11. Internal combustion engine according to one of claims 2 to 10, characterized in that the second cooling space (24) has at least one valve seat ring (43) surrounding an annular second cooling channel (18).
    [12]
    12. Internal combustion engine according to one of claims 2 to 11, characterized in that the second cooling chamber (24) has at least one preferably parallel to the cylinder axis (la) formed axial connecting channel (20), wherein preferably the axial connecting channel (20) adjacent to a in the combustion chamber of the single cylinder (1) opening out central component, preferably an injector, or to a receiving this sleeve (21) is formed.
    [13]
    13. Internal combustion engine according to claim 12, characterized in that the axial connecting channel (20) via at least one radial connecting channel (19) with at least one second cooling channel (18) is fluidly connected.

    11 fib ^ Ö12 / 50Sl48
    [14]
    14. Internal combustion engine according to one of claims 2 to 13, characterized in that the second cooling space (24) has at least one radial connecting bore (17, 22) in the fire deck (23) of the single cylinder head (4), wherein preferably at least one connecting bore (17, 22) in the second cooling channel (18) or the axial connecting channel (20) opens.
    [15]
    15. Internal combustion engine according to one of claims 2 to 14, characterized in that at least one element from the group connecting bore (17, 22), radial connecting channel (19) and second cooling channel (18) in a normal plane (ε) on the cylinder axis (la ) is arranged in the fire deck (23) of the single cylinder head (4).
    [16]
    16. Internal combustion engine according to one of claims 2 to 15, characterized in that the axial connecting channel (20) with at least one between the first and second cooling chamber (14, 24) arranged part cooling space (25) in the single cylinder head (4) is fluidly connected, which preferably at least surrounds an inlet and / or outlet channel.
    [17]
    17. Internal combustion engine according to claim 16, characterized in that the partial cooling space (25) is separated from the first cooling space (14) by an intermediate deck (26).
    [18]
    18. Internal combustion engine according to claim 16 or 17, characterized in that the partial cooling space (25) via at least one second flow passage (27) in the intermediate deck (26) with the first cooling chamber (14) is fluidly connected.
    [19]
    19. Internal combustion engine according to one of claims 16 to 18, characterized in that between the intermediate deck (26) and central component, or a central component receiving sleeve (21), an annular gap (28) is formed, preferably in the annular gap (28 ) An annular aperture (29) is arranged.
    [20]
    20. Internal combustion engine according to claim 19, characterized in that the annular aperture (29) is fixedly connected to the sleeve (21). ΙΡΗΪ®Ww & W 2 feÖ15 [102012/50248 12
    [21]
    21. Internal combustion engine according to claim 19 or 20, characterized in that the diaphragm (29) is formed by a metal or plastic ring.
    [22]
    22. Internal combustion engine according to one of claims 1 to 21, characterized in that - preferably the input side - the first cooling jacket (5) with the first cooling circuit (31) and the second cooling jacket (6) with the second cooling circuit (32) is connected.
    [23]
    23. Internal combustion engine according to one of claims 1 to 22, characterized in that the first cooling circuit (31) as a high-temperature circuit (HT) and the second cooling circuit (32) is designed as a low-temperature circuit (NT).
    [24]
    24. Internal combustion engine according to one of claims 1 to 23, characterized in that in the first cooling circuit (31) a first coolant pump (33) and a first charge air cooler (35) is arranged, wherein the low temperature circuit (NT a lower temperature level than the high temperature circuit (HT ) having.
    [25]
    25. Internal combustion engine according to one of claims 1 to 24, characterized in that in the second cooling circuit (32) a second coolant pump (34) and a second charge air cooler (36), preferably also an oil cooler (37) is arranged.
    [26]
    26. Internal combustion engine according to one of claims 1 to 25, characterized in that the first and the second cooling circuit (31, 32) before entering the first or second cooling jacket (5, 6) of the cylinder housing (2) via at least one bypass or mixing valve (41, 42) are connectable to each other.
    [27]
    27. Internal combustion engine according to one of claims l to 26, characterized in that the media of the first and second cooling circuits (31, 32) within the single cylinder head (4) are brought together.
    [28]
    28. Internal combustion engine according to one of claims 1 to 27, characterized in that first and second cooling circuit (31, 32) branch off downstream of a central cooler (40) from a common cooling circuit. iPrinted: 27-06-2012 (E0i5 [10 2012/50248 13
    [29]
    29. Internal combustion engine according to one of claims 1 to 28, characterized in that the first and second cooling circuit (31, 32) have the same temperature level before entry into the first and second cooling jacket (5, 6). 2012 06 25 Fu / Ec
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50248/2012A|AT513053B1|2012-06-26|2012-06-26|Internal combustion engine, in particular large diesel engine|ATA50248/2012A| AT513053B1|2012-06-26|2012-06-26|Internal combustion engine, in particular large diesel engine|
    PCT/EP2013/062804| WO2014001181A1|2012-06-26|2013-06-19|Internal combustion engine, in particular large diesel engine|
    US14/410,721| US9874133B2|2012-06-26|2013-06-19|Internal combustion engine, in particular large diesel engine|
    DE112013003196.5T| DE112013003196A5|2012-06-26|2013-06-19|Internal combustion engine, in particular large diesel engine|
    JP2015518984A| JP2015521716A|2012-06-26|2013-06-19|Internal combustion engines, especially large diesel engines|
    JP2018122331A| JP2018145971A|2012-06-26|2018-06-27|Internal combustion engine, in particular large diesel engine|
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