WO2015055310A1 - Moteur à combustion interne, en particulier pour véhicule automobile - Google Patents

Moteur à combustion interne, en particulier pour véhicule automobile Download PDF

Info

Publication number
WO2015055310A1
WO2015055310A1 PCT/EP2014/002786 EP2014002786W WO2015055310A1 WO 2015055310 A1 WO2015055310 A1 WO 2015055310A1 EP 2014002786 W EP2014002786 W EP 2014002786W WO 2015055310 A1 WO2015055310 A1 WO 2015055310A1
Authority
WO
WIPO (PCT)
Prior art keywords
cooling
temperature
internal combustion
compressor
combustion engine
Prior art date
Application number
PCT/EP2014/002786
Other languages
German (de)
English (en)
Inventor
Dietmar Schröer
Original Assignee
Daimler Ag
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daimler Ag filed Critical Daimler Ag
Publication of WO2015055310A1 publication Critical patent/WO2015055310A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/12—Intake silencers ; Sound modulation, transmission or amplification
    • F02M35/1288—Intake silencers ; Sound modulation, transmission or amplification combined with or integrated into other devices ; Plurality of air intake silencers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/20—Cooling circuits not specific to a single part of engine or machine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/045—Constructional details of the heat exchangers, e.g. pipes, plates, ribs, insulation, materials, or manufacturing and assembly
    • F02B29/0462—Liquid cooled heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/10—Air intakes; Induction systems
    • F02M35/1015—Air intakes; Induction systems characterised by the engine type
    • F02M35/10157—Supercharged engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/12—Intake silencers ; Sound modulation, transmission or amplification
    • F02M35/1205—Flow throttling or guiding
    • F02M35/1216—Flow throttling or guiding by using a plurality of holes, slits, protrusions, perforations, ribs or the like; Surface structures; Turbulence generators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/12—Intake silencers ; Sound modulation, transmission or amplification
    • F02M35/1255—Intake silencers ; Sound modulation, transmission or amplification using resonance
    • F02M35/1266—Intake silencers ; Sound modulation, transmission or amplification using resonance comprising multiple chambers or compartments
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • Such an internal combustion engine usually comprises at least one cooling circuit through which a cooling medium can flow, in which the combustion chamber housing is arranged.
  • the combustion chamber housing by means of the cooling circuit
  • Cooling device provided for cooling the muffler.
  • the invention is based on the finding that, in particular in highly charged
  • Throttle body can be cooled.
  • the throttle body is designed for example as an electric throttle actuator, which comprises at least one electric motor for moving the throttle valve.
  • Fig. 1 is a schematic longitudinal sectional view of a muffler for a
  • FIG. 2 shows a further schematic longitudinal sectional view of the muffler, the cooling device being provided according to a second embodiment
  • Fig. 3 is a schematic and partially sectioned front view of the
  • Fig. 4 is a schematic view of a cooling circuit for cooling a
  • FIG. 5 shows a schematic view of an internal combustion engine according to a first embodiment, with a combustion chamber housing having at least one combustion chamber, with an intake tract, via which air can be supplied to the combustion chamber, with at least one compressor arranged in the intake tract for compressing the air to be supplied to the combustion chamber, and with at least one cooling circuit through which a cooling medium can flow, in which the combustion chamber housing, which can be cooled by the cooling medium flowing through the cooling circuit, is arranged, wherein at least one component of the intake tract arranged downstream of the compressor is arranged in the cooling circuit for cooling the combustion chamber housing;
  • Fig. 7 is a schematic view of the internal combustion engine according to a third
  • Internal combustion engine 14 is, for example, as reciprocating Internal combustion engine designed and used to drive a motor vehicle, especially a passenger car.
  • the internal combustion engine 14 comprises a combustion chamber housing in the form of a cylinder housing 16, which is also known as
  • Cylinder block is called.
  • the cylinder housing 16 comprises at least one combustion chamber in the form of a cylinder 18.
  • the intake tract 12 serves to supply air to the cylinder 8.
  • At least one compressor 20 of an exhaust gas turbocharger 22 is arranged.
  • the compressor 20 includes a compressor housing 24, in which a recognizable from Fig. 3 compressor wheel 26 is received. As can be seen from FIG. 5, the compressor wheel 26 is rotatable about an axis of rotation 28 relative to the compressor housing 24.
  • the exhaust gas turbocharger 22 also includes a turbine 30 with a turbine housing 32, in which a turbine wheel not visible in the figures is arranged.
  • the intake duct 12 comprises a suction piping 34, which downstream of the
  • Ver Whyrrads 26 arranged and can be flowed through by the compressed air and for guiding the compressed air to the cylinder 18 is used.
  • the intake piping 34 includes, for example, an intake line 36, which is also referred to as charge air line, since the compressed air is also referred to as charge air.
  • the intake piping 34 is fluidly connected to the compressor housing 24 through which the compressed air flows.
  • the muffler 10 is fluidly connected to the Ansaugverrohrung 34 and the
  • Compressor housing 24 is connected and has a recognizable from Fig. 1 channel 38, which is flowed through by the compressed air. In other words, that is
  • an intercooler 84 shown in Figure 7 may be arranged downstream of the muffler 10.
  • the charge air cooler can be flowed through by the compressed air.
  • the air is heated.
  • the air is conveyed by means of the
  • the muffler 10 is in the flow direction of the air, in particular the compressed air, between the intercooler and the
  • Compressor 26 is arranged and thus flows through the compressed and thus heated but not yet cooled charge air.
  • the blading of the compressor wheel and the high rotational speed of its circulation give rise to high-frequency air vibrations at the outlet of the compressor 20. Sound emissions and thus noises can result from these vibrations.
  • Silencer 10 serves to dampen these sound emissions or noise, so that a particularly advantageous noise behavior of the internal combustion engine 14 and thus of the motor vehicle is generally feasible. This includes the
  • Silencer 10 damper chambers 39 which are fluidly connected via openings 41 to the channel 38 and are limited to the outside by outer walls 43, so that the channel 38 flowing through the charge air can not flow to the environment.
  • the different volumes of the damper chambers 39 form with the through holes 41 of the same length and diameter Helmholzresonatoren tuned to different frequencies and so attenuate the Schallemissonen broadband.
  • the inner cooling fins 50 serve to represent a particularly advantageous heat absorption of the wall 42 of the channel 38 flowing through the charge air.
  • the inner cooling fins 50 are arranged on a side facing the channel 38 of the outer walls 43 and, for example, integrally formed with the respective outer walls 43.
  • the outer cooling fins 46 are arranged on a side facing away from the channel 38 of the respective walls 43 and
  • FIG. 2 shows the muffler 10 with the cooling device 40 according to a second embodiment.
  • the cooling device 40 according to the second embodiment has at least one cooling jacket 52, through which a cooling medium can flow, for cooling the muffler 10.
  • the cooling device 40 of the second embodiment is designed as a liquid cooling, the cooling jacket 52 is formed as a water jacket and can be flowed through by a cooling liquid as the cooling medium.
  • the cooling liquid is usually referred to as cooling water and ensures a particularly effective and efficient cooling of the muffler 10.
  • connecting pieces 54 are provided. That in the
  • Cooling jacket 52 introduced cooling medium (cooling liquid) is due to a
  • Coolant is derived from the cooling jacket 52 and passed, for example, to a cooler, by means of which the heated cooling medium is cooled again.
  • the muffler 10 which, for example, designed as a damper insert and
  • Silencer 10 is in intensive heat exchange with the charge air, a particularly good heat transfer from the charge air to the muffler 10 and further to the cooling device 40 and the coolant can be realized by the production of the muffler 10 of a metallic material.
  • a metallic material is particularly advantageous aluminum or an aluminum alloy.
  • Embodiment the inner cooling fins 50 creating a particularly good Heat transfer from the charge air received in the damper chambers 39 to the cooling fins 50 and further to the outer walls 43 can take place. From the outer walls 43 then a very good heat dissipation to the cooling liquid can take place, which flows through the cooling jacket 52 and - as can be seen from Fig. 2 - the outer walls 43 flows around the outer peripheral side and contacted or touched. In other words, the outer walls 43 are facing away from the channel 38
  • cooling fins 50 are arranged between the cooling jacket 52 and the channel 38 of the muffler 10 through which the charge air can flow.
  • FIG. 3 shows the cooling device 40, wherein the muffler 10 is integrated in the compressor housing 24.
  • the compressor housing 24 has at least one channel in the form of a spiral channel 56.
  • the spiral channel 56 can be traversed by the compressed air and serves to discharge the compressed air from the compressor wheel 26.
  • the channel 38 of the muffler 10 is fluidly connected to the spiral channel 56.
  • the channel 38 forms the continuation of the spiral channel 56. Further, the muffler 10 forms a connection piece 58, with which, for example, the suction line 36 can be connected so that the charge air through the spiral channel 56 and the channel 38 and flows from the Channel 38 can flow into the suction line 36.
  • the compressor housing 24 also has an integrated water cooling. In other words, runs within at least one wall of the compressor housing 24, at least one cooling channel, which is flowed through by a cooling medium, in particular cooling liquid.
  • the cooling channel of the compressor housing 24 thus forms a further cooling jacket, in particular a water jacket, which can be flowed through by cooling medium for cooling the compressor housing 24 or the compressor 20.
  • Silencer 10 and the further cooling jacket for cooling the compressor housing 24 are arranged in a common cooling circuit and thus can be flowed through by the same cooling liquid.
  • the cooling jacket 52 of the cooling device 40 for cooling the muffler 10 and the further cooling jacket for cooling the compressor housing 24 fluidly connected or with each other are connectable, so that the muffler 10 and the compressor housing 24 are to be cooled by means of the same coolant.
  • the further cooling jacket of the compressor housing 24 is formed as a water jacket, whereby an effective and efficient cooling of the compressor 20 can be realized.
  • the further water jacket of the compressor housing 24 surrounds, for example, the spiral channel 56 at least partially, in particular at least predominantly, and is led up to the cooling jacket 52 of the muffler 10.
  • a fully water-cooled compressor silencer housing can be created, with only one inlet and one outlet nozzle in the form of the connecting piece 54 for the
  • the connecting piece 54 can be used to both the cooling jacket 52 of the muffler 10 and the cooling jacket of the
  • Compressor housing 24 to supply the cooling liquid or dissipate the cooling liquid from both the cooling jacket 52 and the other cooling jacket of the compressor housing 24.
  • the internal combustion engine 14 has a
  • This cooling circuit 60 is, for example, a high-temperature cooling circuit in which the cylinder housing 16 or at least one water jacket of the cylinder housing 16 is arranged.
  • the cooling circuit 60 is flowed through by a cooling medium, in particular a cooling liquid.
  • a cooling medium in particular a cooling liquid.
  • the water jacket of the cylinder housing 16 can also be flowed through by this cooling liquid.
  • the cylinder housing 16 can be cooled by means of the cooling liquid 60 flowing through the cooling circuit 60 (high-temperature cooling circuit).
  • the internal combustion engine 14 also has a further cooling circuit in the form of a low-temperature cooling circuit.
  • the high temperature refrigeration cycle and the low temperature refrigeration cycle are
  • a respective cooling medium in particular a respective cooling liquid.
  • High-temperature cooling circuit and the low-temperature cooling circuit differ from each other in that the cooling liquid of the high-temperature cooling circuit is cooled to a higher temperature than the cooling liquid of the low-temperature cooling circuit.
  • the high-temperature refrigeration cycle is operated at a first temperature of the cooling liquid of the high-temperature refrigeration cycle, wherein the low-temperature refrigeration cycle at a second temperature of the Cooling liquid of the low-temperature cooling circuit is operated and wherein the first temperature is higher than the second temperature.
  • the cooling jacket 52 and optionally the further cooling jacket of the compressor housing 24 are arranged in the low-temperature cooling circuit, so that the cooling liquid of the low-temperature cooling circuit is used to cool the muffler 10 and possibly the compressor housing 24.
  • the low-temperature cooling circuit is designated 62.
  • the low-temperature cooling circuit 62 comprises a pump 64, by means of which the cooling liquid of the low-temperature cooling circuit 62 is required.
  • the direction in which the cooling liquid of the low-temperature cooling circuit 62 flows through it is illustrated in FIG. 4 by directional arrows.
  • the low-temperature cooling circuit 62 also includes a radiator 68, which is referred to as a recooler. In the low-temperature cooling circuit 62 is also a
  • Bearing housing 66 of the exhaust gas turbocharger 22 is arranged.
  • the compressor wheel 26 and the turbine wheel are rotatably mounted on the bearing housing 66 about the rotation axis 28 relative to the bearing housing 66 via the shaft. It also has, for example, the
  • Low-temperature cooling circuit 62 initially promoted to the bearing housing 66, which is cooled by means of the cooling liquid. From the bearing housing 66 and its
  • Water jacket flows the coolant to the cooling jacket 52 of the muffler 10 and the other cooling jacket of the compressor housing 24 and then to a in the intake manifold 12 downstream of the compressor 20 and downstream of the muffler 10 arranged throttle body 70th
  • the throttle body 70 is flowed through by the cooling liquid of the low-temperature cooling circuit 62.
  • the throttle body 70 is thus another component of the intake tract 12, which is cooled by means of the coolant.
  • the low temperature refrigeration cycle 62 may also be that shown in FIG. 4
  • intercooler which can be cooled by means of the cooling liquid of the low-temperature cooling circuit 62.
  • the intercooler is designed as an air-water cooler, so that the charge air can be cooled particularly effectively and efficiently. It can thus be seen from FIG. 4 that components arranged in the intake tract 12 between the charge air cooler and the compressor wheel 26, for example the muffler 10 and the throttle body 70, can be cooled by means of the cooling liquid of the low-temperature cooling circuit 62. As a result, these components can be protected against thermal damage. In addition, it is possible to cool the compressed and thereby heated air along the charge air path before reaching the charge air cooler, since the charge air, the components mentioned
  • Throttle body 70 is, for example, an electrical
  • a throttle valve actuator comprising a throttle and an electric motor for moving the throttle.
  • the cooling fins 46 and / or 50 of FIG. 1 can also be aligned for the best possible cooling effect so that they optimally pass through or occur when there is a flow through an engine compartment in which the internal combustion engine 14 is arranged.
  • the integration of the muffler 10 in the compressor housing 24 according to FIG. 3 has the advantage that the intake tract 12 can be designed particularly space-saving, since the muffler 10 and the compressor housing 24 may be integrally formed with each other and surrounded by only a common water jacket.
  • the charge air cooler is preferably arranged in the low-temperature cooling circuit 62 downstream of the radiator 68 and upstream of the bearing housing 66. This means that the cooled by the radiator 68 cooling water from the radiator 68 first the
  • Charge air cooler flows through, in order to allow the supercharged air to cool down.
  • Compressor housing 24 and the bearing housing 66 to cool.
  • the order of the components through which the cooling liquid of the low-temperature cooling circuit 62 flows and / or the components arranged in the low-temperature cooling circuit 62 are arbitrary or variable.
  • the pump 64 is, for example, an electrically operated pump and can be at least almost arbitrarily integrated into the low-temperature cooling circuit 62 and ensures the circulation of the cooling liquid (cooling water). In partial load operation of
  • the low-temperature cooling circuit 62 can also be shut down.
  • the silencer 10 for example according to FIG. 3 -is integrated into the compressor housing 24 of the compressor 20.
  • the muffler 10 is now the muffler 10 or be
  • Cooling jacket 52 not in the low-temperature cooling circuit 62 but in the
  • Cooling circuit 60 High-temperature cooling circuit (cooling circuit 60) arranged.
  • Coolant by means of which also the cylinder housing 16 is cooled, also used for cooling the muffler 10. Also the further cooling jacket of the
  • Compressor housing 24 is disposed in the high-temperature cooling circuit, so that the compressor housing 24 by means of the high-temperature cooling circuit
  • the compressor housing 24 is thus a component of the intake tract 12, which is arranged in the high-temperature cooling circuit.
  • the throttle body 70 is also arranged as a further component of the intake tract 12 in the high-temperature cooling circuit, so that it too can be cooled by means of the cooling liquid flowing through the high-temperature cooling circuit.
  • the high-temperature refrigeration cycle includes a pump 72, by means of which the
  • Coolant can be promoted through the high-temperature cooling circuit.
  • the high-temperature refrigeration cycle includes a cooler 74, which is also referred to as a recooler.
  • the bearing housing 66 is disposed in the high-temperature cooling circuit and can be cooled by means of the cooling liquid flowing through the high-temperature cooling circuit.
  • the cooling liquid flowing through the high-temperature cooling circuit is heated as a result of corresponding heat transfers, whereby the corresponding components are cooled.
  • the cooler 74 serves to cool the heated coolant again.
  • the high-temperature cooling circuit comprises at least one valve element in the form of a thermostat 76, by means of which the supply of the cooling jacket 52 and thus of the Silencer 10, the other cooling jacket and thus the compressor housing 24 and the throttle body 70 with the cooling liquid of the high-temperature cooling circuit is adjustable. It is provided that the supply of these components (muffler 10, compressor housing 24 and throttle body 70) with the cooling liquid of the high-temperature cooling circuit by means of the thermostat 76 in response to a temperature of at least one of the components, in particular in response to a temperature difference between the at least a component and the coolant, is adjustable.
  • the arranged in the high-temperature cooling circuit thermostat 76 prevents the
  • thermostat 76 is, for example, coupled or connected in a heat-conducting manner with the named components. Has at least one of the components, i. the compressor housing 24 and / or the
  • Silencer 10 and / or the throttle body 70 to a temperature which is greater than the temperature of the cooling liquid of the high-temperature cooling circuit, so heat transfer from the opposite of the cooling liquid warmer component can be done to the cooling liquid of the high-temperature cooling circuit.
  • the thermostat 76 releases the flow of the components with the cooling liquid, so that the components can be cooled by means of the cooling liquid of the high-temperature cooling circuit.
  • the cooling liquid of the high-temperature cooling circuit flows through said components and / or through a bypass line 78 of the high-temperature cooling circuit, wherein in the bypass line 78 a throttle 80 of the high-temperature cooling circuit
  • the cooling liquid is taken, for example, the cylinder block (cylinder housing 6) at a location with a relatively high pressure level and at a location with respect to lower pressure level, for example, close to the exit of a
  • Cylinder head of the internal combustion engine 14 fed again.
  • these can be removed and circulated coolant circulated parallel to the cooling liquid in the internal combustion engine 14 and in the cylinder housing 16, wherein the cooling liquid flows in the internal combustion engine 14, in particular in the cylinder housing 16, via a cylinder head gasket and cooling channels in the cylinder head.
  • the thermostat 76 with at least one temperature-critical component, in particular a housing of the muffler 10, heat is conductively connected. This allows the thermostat 76 the flow of
  • the bypass line 78 also provides a closed thermostat 76, i. If the thermostat 76 prevents the flow of the components through coolant, a flow through the bearing housing 66 safely.
  • the throttle 80 ensures when the thermostat 76 is open a sufficient pressure drop for the flow through the components (compressor housing 24, muffler 10 and throttle body 70) with coolant.
  • the thermostat 76 has a three-way function.
  • the coolant of the high-temperature cooling circuit is passed either through the components to be cooled (compressor housing 24, muffler 10, throttle body 70) or by the bypass line 78.
  • the cooling liquid is conducted past them either through the components to be cooled or via the bypass line 78.
  • throttle 80 can be omitted.
  • the thermostat 76 is replaced by a valve element in the form of a switching valve 82.
  • the switching valve 82 takes over the task of the thermostat 76, wherein the switching valve 82 is driven electronically.
  • a controlled variable or control variable for driving or regulating the switching valve 82 is either the at least one
  • Temperature of the at least one component to be cooled of the charge air path used can be Alternatively or additionally, a temperature model can be used. By means of such a virtual model, at least one temperature of at least one of the components is calculated by means of a computing device. When the calculated temperature exceeds the temperature of the cooling liquid, the switching valve 82 releases the flow of the cooling liquid, so that the at least one component can be cooled by means of the cooling liquid of the high-temperature cooling circuit.
  • the charge air cooler designated by 84 is provided as additional component to be cooled by means of the cooling liquid of the high-temperature cooling circuit, which is arranged downstream of the throttle body 70.
  • the charge air cooler 84 can be flowed through by the compressed air (charge air) and, in particular when required, by the cooling fluid of the high-temperature cooling circuit, so that the charge air cooler 84 is designed as an air-water cooler.
  • the charge air cooler 84 it is possible to cool the charge air via the intercooler 84 by means of the cooling liquid of the high temperature refrigeration cycle.
  • the intercooler 84 has a high-temperature part 86 and a
  • the high-temperature part 86 is to be cooled by means of the cooling liquid of the high-temperature cooling circuit.
  • the low-temperature part 88 is to be cooled with the low-temperature cooling circuit 62, which can be seen in detail in FIG.
  • the high-temperature part 86 is arranged in the high-temperature cooling circuit, wherein the low-temperature part 88 is arranged in the low-temperature cooling circuit 62.
  • the internal combustion engine 14 also includes a temperature sensor 90, by means of which a temperature of a component of the charge air path is detected.
  • this component is the throttle body 70, which, however, is only optionally provided in the internal combustion engine 14 according to FIGS. 4 to 7.
  • the electrically operable switching valve 82 is effected in response to the temperature detected by the temperature sensor 90 that the cooling liquid of the high-temperature cooling circuit either through the components of the charge air path, i. through the compressor housing 24, the muffler 10, the throttle body 70 and the high-temperature part 86 or through the
  • Bypass line 78 flows past these components. As a result, a need-based cooling of the said components of the charge air route can be realized. If the temperature model is used in the form of a computer model to calculate at least one temperature of at least one component of the charge air path and operated the switching valve 82 in dependence on this temperature, the temperature model is used in the form of a computer model to calculate at least one temperature of at least one component of the charge air path and operated the switching valve 82 in dependence on this temperature, the
  • Temperature sensor 90 also omitted.
  • the order in which the components of the charge air path or the components of the internal combustion engine 14 are at all traversed by the cooling liquid can also be varied. Likewise, components to be cooled can be omitted and / or other components to be cooled can be provided.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Exhaust Silencers (AREA)

Abstract

L'invention concerne un moteur à combustion interne (14), destiné en particulier à un véhicule automobile, comprenant un système d'aspiration (12), permettant d'amener de l'air à au moins une chambre de combustion (18) du moteur à combustion interne, au moins un compresseur (20) équipé d'une roue de compresseur (26), disposé dans le système d'aspiration (12) et servant à comprimer l'air à amener à la chambre de combustion (18) et au moins un silencieux (10) disposé dans le système d'aspiration (12) en aval de la roue de compresseur (26), un moyen de refroidissement (40) servant à refroidir le silencieux (10).
PCT/EP2014/002786 2013-10-17 2014-10-16 Moteur à combustion interne, en particulier pour véhicule automobile WO2015055310A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201310017276 DE102013017276A1 (de) 2013-10-17 2013-10-17 Verbrennungskraftmaschine, insbesondere für einen Kraftwagen
DE102013017276.4 2013-10-17

Publications (1)

Publication Number Publication Date
WO2015055310A1 true WO2015055310A1 (fr) 2015-04-23

Family

ID=51842472

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2014/002786 WO2015055310A1 (fr) 2013-10-17 2014-10-16 Moteur à combustion interne, en particulier pour véhicule automobile

Country Status (2)

Country Link
DE (1) DE102013017276A1 (fr)
WO (1) WO2015055310A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107850091A (zh) * 2016-02-22 2018-03-27 三菱重工业株式会社 噪音降低构造和增压装置
CN108869004A (zh) * 2017-05-15 2018-11-23 通用汽车环球科技运作有限责任公司 用于调节通过车辆的增压空气冷却器的冷却剂流量的系统和方法
US10403256B2 (en) * 2014-10-31 2019-09-03 Umfotec Gmbh Resonator with ring-shaped chamber between an inner tube and an outer wall and with a dividing rib extending from the inner tube toward the outer wall

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017126125A1 (de) * 2017-11-08 2019-05-09 Dietrich Denker Vorrichtung zur Absenkung von Luft- und Körperschall
DE102021102717A1 (de) 2020-02-05 2021-08-05 Bayerische Motoren Werke Aktiengesellschaft Brennkraftmaschine mit einem Verdichter

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3531353A1 (de) 1985-09-03 1987-03-12 Audi Ag Ladeluftkuehler fuer aufgeladene brennkraftmaschine
DE19504223A1 (de) * 1995-02-09 1996-08-14 Volkswagen Ag Schalldämpfer für den Ansaugkanal einer Brennkraftmaschine
WO2005111390A1 (fr) * 2004-05-11 2005-11-24 Modine Manufacturing Company Echangeur thermique integre et module de silencieux
DE102005039459A1 (de) * 2005-08-20 2007-02-22 Daimlerchrysler Ag Brennkraftmaschine mit einem Abgasturbolader
FR2921123A1 (fr) * 2007-09-17 2009-03-20 Mark Iv Systemes Moteurs Soc P Circuit de refroidissement des gaz d'alimentation propulses par un turbocompresseur
DE102009027539A1 (de) 2009-07-08 2011-01-20 Ford Global Technologies, LLC, Dearborn Brennkraftmaschine mit Ladeluftkühler
DE102009028632A1 (de) 2009-08-19 2011-03-03 Ford Global Technologies, LLC, Dearborn Flüssigkeitsgekühlte Brennkraftmaschine mit flüssigkeitsgekühlter Turbine
FR2951782A1 (fr) * 2009-10-28 2011-04-29 Peugeot Citroen Automobiles Sa Refroidisseur d'air de suralimentation

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1113119B (de) * 1959-07-01 1961-08-24 Leistritz Hans Karl Schalldaempfer fuer stroemende und vorzugsweise auch heisse Gase
DE3633405A1 (de) * 1986-10-01 1988-04-14 Man Nutzfahrzeuge Gmbh Verfahren zum betreiben einer abgas-truboaufgeladenen, niedrigverdichtenden mehrzylinder-dieselbrennkraftmaschine
DE4219249C2 (de) * 1992-06-12 1994-03-31 Kuehnle Kopp Kausch Ag Radialverdichter, insbesondere eines Turboladers
JP2002115608A (ja) * 2001-08-29 2002-04-19 Yanmar Diesel Engine Co Ltd 内燃機関の吸気部構造
EP1445454A1 (fr) * 2003-02-07 2004-08-11 Renault s.a.s. Commande de la température pour un système d'admission d'un moteur
FR2955622B1 (fr) * 2010-01-27 2012-07-13 Peugeot Citroen Automobiles Sa Architecture de groupe motopropulseur diesel suralimente

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3531353A1 (de) 1985-09-03 1987-03-12 Audi Ag Ladeluftkuehler fuer aufgeladene brennkraftmaschine
DE19504223A1 (de) * 1995-02-09 1996-08-14 Volkswagen Ag Schalldämpfer für den Ansaugkanal einer Brennkraftmaschine
WO2005111390A1 (fr) * 2004-05-11 2005-11-24 Modine Manufacturing Company Echangeur thermique integre et module de silencieux
DE102005039459A1 (de) * 2005-08-20 2007-02-22 Daimlerchrysler Ag Brennkraftmaschine mit einem Abgasturbolader
FR2921123A1 (fr) * 2007-09-17 2009-03-20 Mark Iv Systemes Moteurs Soc P Circuit de refroidissement des gaz d'alimentation propulses par un turbocompresseur
DE102009027539A1 (de) 2009-07-08 2011-01-20 Ford Global Technologies, LLC, Dearborn Brennkraftmaschine mit Ladeluftkühler
DE102009028632A1 (de) 2009-08-19 2011-03-03 Ford Global Technologies, LLC, Dearborn Flüssigkeitsgekühlte Brennkraftmaschine mit flüssigkeitsgekühlter Turbine
FR2951782A1 (fr) * 2009-10-28 2011-04-29 Peugeot Citroen Automobiles Sa Refroidisseur d'air de suralimentation

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10403256B2 (en) * 2014-10-31 2019-09-03 Umfotec Gmbh Resonator with ring-shaped chamber between an inner tube and an outer wall and with a dividing rib extending from the inner tube toward the outer wall
CN107850091A (zh) * 2016-02-22 2018-03-27 三菱重工业株式会社 噪音降低构造和增压装置
CN108869004A (zh) * 2017-05-15 2018-11-23 通用汽车环球科技运作有限责任公司 用于调节通过车辆的增压空气冷却器的冷却剂流量的系统和方法
CN108869004B (zh) * 2017-05-15 2021-03-02 通用汽车环球科技运作有限责任公司 用于调节通过车辆的增压空气冷却器的冷却剂流量的系统和方法

Also Published As

Publication number Publication date
DE102013017276A1 (de) 2015-04-23

Similar Documents

Publication Publication Date Title
DE102010038055A1 (de) Brennkraftmaschine mit Flüssigkeitskühlung
DE102011104446B4 (de) Kühlvorrichtung für einen Turbolader eines Motors für ein Fahrzeug
DE102013202834A1 (de) Einlasssystem mit einem integrierten Ladeluftkühler
WO2015055310A1 (fr) Moteur à combustion interne, en particulier pour véhicule automobile
DE102011105041B4 (de) Schmiervorrichtung für einen Turbolader eines Motors für ein Fahrzeug
DE102007053126B4 (de) Brennkraftmaschine mit gekühlter Abgasrückführung sowie Abgaskrümmer
DE102014219252A1 (de) Brennkraftmaschine
DE112007001140T5 (de) Fahrzeug-Kühlungssystem mit gelenkten Strömen
DE102011104450A1 (de) Turboladevorrichtung für einen Fahrzeugmotor
DE102011053176A1 (de) Verfahren und Vorrichtung zur Leckagedetektion eines Fahrzeug-Schmiersystems
DE102007050259A1 (de) Aufgeladene Brennkraftmaschine mit integriertem Abgaskrümmer und Flüssigkeitskühlung
WO2014033053A1 (fr) Tubulure d'admission pour moteur à combustion interne
DE102008025953A1 (de) Motorsystem mit dafür vorgesehenem Wärmemanagementsystem
DE102018130212A1 (de) Verdichtergehäuse
DE102010033125A1 (de) Wärmetauschereinrichtung
DE102008029455A1 (de) Wärmeübertrager
DE102017208034B4 (de) Flüssigkeitsgekühlte Brennkraftmaschine mit Entlüftung
DE202013103704U1 (de) Zylinderkopf mit einer Axialturbine
WO2008058737A1 (fr) Dispositif de recyclage des gaz d'échappement
DE102014114649B4 (de) Luftrohrleitung und Kühlsystem für ein Fahrzeug
DE102013218164B4 (de) Ladeluftkühler
DE102005036045B4 (de) Kühlvorrichtung für Verbrennungskraftmaschinen
DE102014218782A1 (de) Aufgeladene Brennkraftmaschine mit flüssigkeitsgekühlter Turbine und Lagergehäuse
DE102013216112A1 (de) Zylinderkopf mit einer Axialturbine
DE202014104463U1 (de) Flüssigkeitsgekühlte Turbine mit Lagergehäuse

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 14790509

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 14790509

Country of ref document: EP

Kind code of ref document: A1