EP3414438A1 - Dispositif de suralimentation en air d'un moteur à combustion interne - Google Patents
Dispositif de suralimentation en air d'un moteur à combustion interneInfo
- Publication number
- EP3414438A1 EP3414438A1 EP17707383.0A EP17707383A EP3414438A1 EP 3414438 A1 EP3414438 A1 EP 3414438A1 EP 17707383 A EP17707383 A EP 17707383A EP 3414438 A1 EP3414438 A1 EP 3414438A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- air
- cooling circuit
- compressor
- value
- control
- Prior art date
- Legal status (The legal status 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 status listed.)
- Granted
Links
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 14
- 238000001816 cooling Methods 0.000 claims abstract description 82
- 230000004913 activation Effects 0.000 claims description 10
- 238000000034 method Methods 0.000 claims description 10
- 230000009849 deactivation Effects 0.000 claims description 6
- 239000000463 material Substances 0.000 claims description 6
- 238000004804 winding Methods 0.000 claims description 3
- 230000001419 dependent effect Effects 0.000 claims description 2
- 230000001133 acceleration Effects 0.000 description 3
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 239000012528 membrane Substances 0.000 description 3
- 239000007789 gas Substances 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 239000000543 intermediate Substances 0.000 description 2
- 230000002427 irreversible effect Effects 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 239000004677 Nylon Substances 0.000 description 1
- 239000004809 Teflon Substances 0.000 description 1
- 229920006362 Teflon® Polymers 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 230000033228 biological regulation Effects 0.000 description 1
- 239000012809 cooling fluid Substances 0.000 description 1
- 239000000498 cooling water Substances 0.000 description 1
- 230000005672 electromagnetic field Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
- 229920001778 nylon Polymers 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 229920002379 silicone rubber Polymers 0.000 description 1
- 239000004945 silicone rubber Substances 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Classifications
-
- 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
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/005—Cooling of pump drives
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/08—Cooling; Heating; Heat-insulation
- F01D25/12—Cooling
-
- 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
- F01P5/00—Pumping cooling-air or liquid coolants
- F01P5/02—Pumping cooling-air; Arrangements of cooling-air pumps, e.g. fans or blowers
- F01P5/04—Pump-driving arrangements
-
- 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
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/02—Drives of pumps; Varying pump drive gear ratio
- F02B39/08—Non-mechanical drives, e.g. fluid drives having variable gear ratio
- F02B39/10—Non-mechanical drives, e.g. fluid drives having variable gear ratio electric
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
- F04D17/10—Centrifugal pumps for compressing or evacuating
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/58—Cooling; Heating; Diminishing heat transfer
- F04D29/5806—Cooling the drive system
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/58—Cooling; Heating; Diminishing heat transfer
- F04D29/5813—Cooling the control unit
-
- 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
- F01P2060/00—Cooling circuits using auxiliaries
- F01P2060/12—Turbo charger
Definitions
- turbochargers for this purpose, the use of turbochargers is particularly known, in which a compressor is driven by a turbine driven by the speed of the engine exhaust gases.
- the efficiency of a turbocharger is related to the speed of the engine exhaust gas, which implies that the supercharging is not optimal when the engine is running at low speed. This can be troublesome especially when a high power of the engine is required at low speed, because it is not possible to quickly increase the engine torque.
- Such an electric compressor comprises an electric machine formed of a stator and a rotor, installed in a housing, the rotor being secured to a compressor wheel by a shaft passing through the housing.
- the electric compressor is then decoupled from the engine speed and can adapt to the engine's supercharging needs, in particular to produce faster power.
- the motor vehicle when the motor vehicle is sized so that the electric compressor provides the majority of the air intake for the engine supercharging, for example in the absence of a turbocharger, or when the vehicle operates essentially at low speed for example during a city traffic, it may happen that the electric compressor is brought to operate uninterrupted or briefly interrupted, during long periods of time, which can cause significant heating of the electric machine.
- stator circuits of the machine heat by Joule effect, which can cause significant damage and potentially irreversible on this machine.
- a known problem is to find a solution to allow an electric compressor of a motor vehicle to operate over long periods of time, while ensuring that it does not suffer irreversible damage.
- an air supercharging circuit comprises an air inlet which conducts an outside air flow to the compressor inlet.
- the compressed air leaving the compressor is led at the inlet of a heat exchanger, known as the charge air cooler, or under the English name of intercooler, to be cooled, and compressed air cooled is then led to the intake manifold.
- a heat exchanger known as the charge air cooler, or under the English name of intercooler
- the air circuit also comprises a first air supply duct opening at one end at the outlet of the heat exchanger and at another end inside the casing of the electric machine.
- the air circuit also comprises a second conduit opening at one end inside the housing of the electric machine and at the other end in the vicinity of the air inlet of the compressor.
- an air-boosting device of an internal combustion engine comprising an air inlet, an electric compressor driven by a suitable control device, for compressing the air coming from the air inlet and an exchanger thermal device for cooling compressed air from the compressor, the cooled compressed air flowing to an intake manifold of the internal combustion engine, said supercharging device comprising a cooling circuit of the electric compressor and / or the control device , the cooling circuit comprising an air supply duct to the electric compressor and / or the control device, extending between the outlet of the heat exchanger and the electric compressor and / or the control device, so as to ability to capture cooled compressed air, the recirculation circuit further comprising an air recirculation duct extending between the electric compressor and / or the control device and the vicinity of the inlet of the intake manifold.
- the pressure gradient at the ends of the cooling circuit, for circulating the air in the cooling circuit is a function of the acceleration of the air as it flows between the outlet of the heat exchanger and the inlet of the intake manifold.
- the cooling circuit allows the circulation of a cooled compressed air flow to cool the electric compressor, even when the operating speed of the engine is low.
- Such a device has the advantage of slaving the flow rate in the cooling circuit to the control current of the compressor, which defines the speed of rotation of the compressor wheel. Indeed, the higher the current, the higher the pressure at the outlet of the heat exchanger will be high and therefore the higher the air flow in the cooling circuit will be important. Also, such The device performs an implicit servocontrol of the air flow in the cooling circuit, which makes it possible to reduce the cost of integration and development since it does not necessarily require external servocontrol.
- the electric compressor comprises an electric machine installed in a housing and the cooling circuit comprises at least a portion of the interior of the housing.
- the components of the electrical machine in particular the power electronics components installed in the housing, the stator and the rotor of the electric machine, can be cooled simply and efficiently.
- control device comprises a housing in which at least one power electronics is arranged, the cooling circuit comprising at least a part of the inside of the housing.
- the recirculation duct opens in the vicinity of the inlet of the intake manifold so as to form a junction orthogonal to the direction of the cooled compressed air flow in the vicinity of said junction.
- the cooling device further comprises means for controlling the amount of cooled compressed air allowed to circulate in said cooling circuit.
- means for controlling the amount of air circulating in the cooling circuit independently of the passive circulation conditions, such as the pressure gradient at the ends of the cooling circuit.
- said control means comprises a solenoid valve.
- the solenoid valve is disposed in the cooling circuit in the vicinity of the outlet of the heat exchanger.
- the electric compressor comprises means for generating a forced air flow through the cooling circuit, said means for generating a forced air flow being, for example, fins disposed on the rotor, said fins being able to material from the rotor according to a particular winding of the latter.
- the invention also relates to a method for controlling a supercharging device as described above, comprising steps of:
- control of the control means according to said determined opening value so as to control the amount of cooled compressed air allowed to circulate in said cooling circuit.
- control method further comprises steps of:
- closure of the control means can be effectively controlled to maximize the availability of air for supercharging the internal combustion engine.
- control method comprises a step of determining a pressure gradient value associated with the cooling circuit, for example as a function of the pressure difference between the vicinity of the outlet of the heat exchanger and the pressure at the pressure. junction in the vicinity of the entrance of the intake manifold, the control of the means of control being furthermore a function of a closure command determined so that, when the determined pressure gradient value is lower than a predetermined threshold value, the control means at least partially prevents the circulation of cooled compressed air in the cooling circuit.
- a pressure gradient value associated with the cooling circuit for example as a function of the pressure difference between the vicinity of the outlet of the heat exchanger and the pressure at the pressure. junction in the vicinity of the entrance of the intake manifold, the control of the means of control being furthermore a function of a closure command determined so that, when the determined pressure gradient value is lower than a predetermined threshold value, the control means at least partially prevents the circulation of cooled compressed air in the cooling circuit.
- the invention relates to a supercharging assembly comprising a supercharging device as described above and a controller adapted to implement the control method.
- the control member may for example be an onboard computer, a microprocessor, or for example the control unit of the electric compressor.
- the invention further relates to a motor vehicle comprising a supercharging device as described above.
- FIG. 1 is a schematic representation of a supercharging device according to one embodiment of the invention.
- FIG. 2 is a schematic representation of a method for controlling a supercharging device according to the embodiment of FIG. 1.
- an air supercharging device 1 of an internal combustion engine 2 comprises an air inlet 5 and a compressor 6.
- the supercharging device 1 and the engine 2 are installed in a motor vehicle.
- the invention is not limited solely to motor vehicles, and relates to any supercharging device installation 1 for an internal combustion engine 2.
- the compressor 6 receives the air coming from the air inlet 5 after passing through an air filter 7.
- the air filter 7 makes it possible to filter the solid particles that can be conveyed by the air and that could be damage the compressor 6.
- the air entering through the air inlet 5 generally comes from outside the assembly in which the supercharging device 1 and the engine 2 are installed, for example from the outside of a motor vehicle. This air is therefore generally at atmospheric pressure and at ambient temperature.
- the compressor 6 is here an electric compressor 6 which comprises an electric machine 8 installed in a housing 1 1 and formed of a stator 10 and a rotor 9.
- the compressor 6, may be a turbocharger assisted by an electric machine, the electric machine then replacing the turbine of the turbocharger to drive the compression wheel, when the engine runs at low speed.
- the implementation of this alternative is then simply adaptable to cool the electric machine.
- the rotor 9 is installed in the stator 10 so as to be rotated by the electromagnetic field produced by the stator 10.
- a shaft 12 is secured to a first end of the rotor 9, and passes through the housing 1 1 so as to be secured at another end to a compressor wheel 13.
- the rotor 9 rotates the shaft 12 which in turn drives the compressor wheel 13.
- the compressor 6 is controlled by an onboard control unit 20.
- the on-board control unit 20 receives a power demand value from the engine 2, for example as a function of the force produced by the user of the motor vehicle on the accelerator pedal 21, or the position that the user gives to said accelerator pedal 21.
- the on-board control unit 20 calculates the necessary torque to quickly obtain the requested power.
- the onboard control unit actuates the compressor 6 so that it provides the engine 2 a sufficient rate of supercharged air to increase the torque produced
- the compressed air which has been heated during its compression, is led to a heat exchanger 14, here a charge air cooler 14, also known as the English intercooler, for cooling the compressed air .
- the cooled compressed air exiting the heat exchanger 14 flows to the intake manifold 3 of the engine 2 so that it can be injected into the cylinders of the engine 2.
- the supercharging device 1 also comprises a cooling circuit 41, 42 of the compressor 6.
- the cooling circuit 41, 42 is formed of an air supply duct 41 and an air recirculation duct 42.
- the cooling circuit 41, 42 therefore constitutes a parallel circuit 41, 42 to the main supercharging circuit 44 described above.
- the ducts of the cooling circuit 41, 42 may be fixed to the main circuit 44 by threading, by press fitting on rigid or straight ducts, for example provided with bulges, or else locked by collars.
- the ducts of the cooling circuit 41, 42 may be made of any suitable material, for example silicone rubber, fabricated, for example with wire mesh, Teflon, nylon.
- each duct of the cooling circuit can be made from at least one material or a combinatorial of materials that is able to thermally isolate the flow of cooled air circulating in the ducts of the environment. high temperature that is the engine compartment. This is to maintain a constant airflow temperature for cooling the compressor.
- the air supply duct 41 is adapted to supply fresh air capable of cooling the electric machine of the compressor 6.
- the air supply duct 41 extends between the outlet 47 of the heat exchanger 14 and the compressor 6.
- the air intake duct 41 enters the casing 1 1 of the electrical machine 8 so as to put the air opening in the casing January 1 in contact in particular with the stator 10, the rotor 9, but also the housing where are the power electronics components of the controller that manage the power introduced into the stator or rotor according to the design technology of the electric machine, to cool them by heat exchange.
- control device comprising the power electronics is remote from the electrical machine, for example according to an arrangement of the power devices in a dedicated housing and separated from the housing 1 1, the circuit of cooling 41,
- An air recirculation duct 42 is installed, which extends between the interior of the casing 1 1 of the electrical machine 8 and the vicinity of the inlet 45 of the intake manifold 3.
- the recirculation duct 42 opens at a junction point 48, in the main circuit 44, orthogonal to the direction of the flow of air flowing in the main circuit 44 at the junction point 48 with the recirculation duct 42.
- This junction point 48 will be chosen so that the air circulating in the main circuit 44 at this junction point 48 has a substantially maximum speed.
- junction point 48 will be chosen so that it is as far as possible from the outlet 47 of the heat exchanger 14, and therefore as close as possible to the intake manifold 3.
- the recirculation duct 42 firstly makes it possible to reintroduce the air used to cool the electrical machine 8 upstream of the intake manifold 3, which makes it possible to preserve the overall air flow at the inlet of the collector. admission 3.
- the casing January 1 forming from a general point of view, a substantially airtight envelope, the pressure gradient between the vicinity of the inlet manifold 45 inlet 3 and the outlet 47 of the heat exchanger 14 makes it possible to obtain a depression that circulates the air in the cooling circuit 41, 42 from the outlet 47 of the heat exchanger 14 to the vicinity of the inlet inlet manifold inlet 45 so that creating a flow of air cooling the interior of the casing 1 1 of the electric machine 8.
- the accelerated air in the vicinity of the inlet of the intake manifold 3 has a lower pressure than the slower air in the vicinity of the outlet 47 of the heat exchanger 14, such as so that the air can be sucked into the cooling circuit 41, 42 parallel.
- the acceleration of the air can be produced by the particular shape of the intake manifold 3 or the main circuit 44, however if the air is not naturally accelerated in the main circuit portion 44 between the outlet 47 of the heat exchanger 14 and the vicinity of inlet 45 of intake manifold 3, a venturi device may be installed between heat exchanger 14 and inlet of intake manifold 3, in main circuit 44, so forcing the acceleration of the air, and creating a pressure gradient favorable to the circulation of air in the cooling circuit 41, 42.
- the supercharging device comprises, at the level of the electric compressor 6, means for generating a forced air flow through the cooling circuit 41, 42.
- said means for generating a forced air flow may be fins disposed at the periphery of the rotor. According to an alternative embodiment of these fins, they may be of rotor material according to a particular winding of the latter.
- the rotation of the rotor causes the wings to move, which forces the air to circulate in the ducts of the cooling circuit 41, 42.
- 41, 42 comprises a control means 60 of the air flow.
- the control means 60 is here a solenoid valve 60 installed in the vicinity of the end of the air supply duct 41 opening out in the vicinity of the outlet 47 of the heat exchanger 14.
- control means 60 may comprise a membrane or a needle, installed in the cooling circuit 41, 42 in the vicinity of the electrical machine 8, and sealingly closing the cooling circuit 41, 42.
- the needle or the membrane is mechanically connected to a spring bearing on the air intake circuit 41, the expansion of which increases the length, so that it exerts a force that moves the membrane or the needle, thus clear a passageway to said fluid.
- the dimensioning of the spring is made so that the circuit is open when the temperature of the electric compressor 6 having led to the expansion of the spring, corresponds to a threshold T1 for triggering the cooling.
- the solenoid valve 60 can be controlled by an independent control member 20 or directly by the on-board control unit 20 controlling the compressor 6.
- the solenoid valve 60 is adapted to move from an open position in which the air is free to pass into the cooling circuit 41, 42 to a closed position preventing the passage of air in the cooling circuit 41, 42.
- the solenoid valve 60 is further adapted to take several positions intermediates modulating the allowable air flow in the cooling circuit 41, 42.
- the solenoid valve can be positioned in a closed position. In this way no pressure drop is produced at the main circuit 44 air supercharging, and the operation of the motor 2 is, in this respect, optimal.
- a method of controlling the solenoid valve 60, implemented by the control member 20, comprises a first step in which 100 is received for each instant t a value representative of the temperature Tce of the electric machine 8 of the compressor 6, to which will be referred, for more legibility, as being the Tce temperature of the electric machine 8.
- the temperature Tce of the electrical machine 8 may be provided by a temperature sensor installed in the housing 1 1 of the machine 8.
- the temperature Tce of the electrical machine 8 can be obtained by a calculation means, for example a microprocessor, adapted to calculate, as a function of the engine speed, the compressor operation and any other suitable parameter, an estimated value and / or predictive for the following instants, the Tce temperature of the electric machine 8.
- a calculation means for example a microprocessor, adapted to calculate, as a function of the engine speed, the compressor operation and any other suitable parameter, an estimated value and / or predictive for the following instants, the Tce temperature of the electric machine 8.
- a calculation means for example a microprocessor, can implement a heat dissipation model adapted to predict heating of the electric machine, in order to anticipate the regulation of the opening of the solenoid valve 60, for optimize the temperature control Tce in the housing 1 1 of the electrical machine 8
- the temperature Tce of the electrical machine 8 is then compared with an upper limit temperature T1, called the activation temperature T1, for example an activation temperature T1 between 60 ° C. and 150 ° C.
- the heat exchanger 14 may be a water / air type exchanger, in that the cooling water circuit is a cooling circuit said to be at a low temperature, the water temperature not exceeding 60 ° C. preferably at 50.degree. C., compared with a so-called high temperature cooling circuit, such as the cooling circuit of the engine, the cooling fluid of which approaches a temperature of between 90.degree. C. and 120.degree.
- the heat exchanger 14 may be of the air / air type, disposed on the front of the vehicle to draw the frigories of air to cool the compressed air.
- the temperature value of the electrical machine 8 is compared with a deactivation value T2, for example a temperature value of between 40 ° C. and 80 ° C. vs.
- the deactivation value T2 is lower than the activation value T1 so as to ensure sufficient cooling of the electrical machine 8.
- each activation temperature value T1 defining an intermediate opening position different from the solenoid valve 60, so that each activation value T1 allows a flow rate corresponding to a different fraction of the maximum possible flow in the circuit 41, 42 when the solenoid valve 60 is in the fully open position. Also, the higher the activation temperature value T1, the greater the opening of the solenoid valve 60 is important.
- the pressure gradient at the ends of the cooling circuit 41, 42 is calculated, for example as a function of the measured or estimated pressure values, in the vicinity of the outlet 47 of the heat exchanger 14, of the pressure at the junction 48 in the vicinity of the inlet 45 inlet of the intake manifold 3, and the length of the main circuit 44.
- the calculated gradient has a value between of the order of 10 and 300 mbar, it controls a partial closure of the control means 60, here the solenoid valve, to create a pressure drop, so that by Venturi effect, the air flow in the main circuit 44 in the vicinity of inlet 45 of intake manifold 3 produces a suction of air in the cooling circuit 41, 42.
- the control means 60 here the solenoid valve
- the air supercharging device of an internal combustion engine may also include a conventional compressor in addition to the electric compressor 6, each preferably operating at different points of load of the engine to internal combustion 2.
- the air supply duct cooled the electric compressor 6 is preferably a stitching made close to the exchanger 14, or even according to one embodiment, directly included in the outlet manifold of the exchanger 14 which then comprises a main air outlet 47 and a secondary outlet through which the cooling air can pass in the direction of the electric compressor 6 or the control device to be cooled.
- the means of controlling the air flow rate including the valve 60 can be directly integrated in the exchanger 14, for example by molding an outlet manifold.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Supercharger (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR1650972A FR3047515B1 (fr) | 2016-02-08 | 2016-02-08 | Dispositif de suralimentation en air d'un moteur a combustion interne. |
PCT/FR2017/050266 WO2017137687A1 (fr) | 2016-02-08 | 2017-02-06 | Dispositif de suralimentation en air d'un moteur à combustion interne |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3414438A1 true EP3414438A1 (fr) | 2018-12-19 |
EP3414438B1 EP3414438B1 (fr) | 2019-12-04 |
Family
ID=55486973
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP17707383.0A Active EP3414438B1 (fr) | 2016-02-08 | 2017-02-06 | Dispositif de suralimentation en air d'un moteur à combustion interne |
Country Status (8)
Country | Link |
---|---|
US (1) | US10480400B2 (fr) |
EP (1) | EP3414438B1 (fr) |
JP (1) | JP6882308B2 (fr) |
KR (1) | KR102102343B1 (fr) |
CN (1) | CN108699962B (fr) |
FR (1) | FR3047515B1 (fr) |
RU (1) | RU2698374C1 (fr) |
WO (1) | WO2017137687A1 (fr) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN107806382A (zh) * | 2017-10-10 | 2018-03-16 | 安徽江淮汽车集团股份有限公司 | 一种新型进气*** |
CN114750611A (zh) * | 2022-06-10 | 2022-07-15 | 吉泰车辆技术(苏州)有限公司 | 利用降低发电机空气压力来提高效率的增程器及方法 |
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US3741677A (en) * | 1971-10-12 | 1973-06-26 | Barodyne Inc | Flow control apparatus for a centrifugal compressor |
AT408785B (de) * | 1995-11-30 | 2002-03-25 | Blank Otto Ing | Aufladeeinrichtung für die ladeluft einer verbrennungskraftmaschine |
DE19845375A1 (de) * | 1998-10-02 | 2000-04-06 | Asea Brown Boveri | Verfahren und Vorrichtung zur indirekten Kühlung der Strömung in zwischen Rotoren und Statoren von Turbomaschinen ausgebildeten Radialspalten |
DE10040508A1 (de) * | 2000-08-18 | 2002-02-28 | Daimler Chrysler Ag | Luftkühlung an einem Turboladerlagergehäuse |
RU2193673C2 (ru) * | 2001-02-15 | 2002-11-27 | Открытое акционерное общество "Специальное конструкторское бюро турбонагнетателей" | Система управляемого турбонаддува |
US6609375B2 (en) * | 2001-09-14 | 2003-08-26 | Honeywell International Inc. | Air cooling system for electric assisted turbocharger |
DE10156704A1 (de) * | 2001-11-13 | 2003-05-22 | Iav Gmbh | Verfahren und Vorrichtung zum Betreiben eines Abgasturboladers für Verbrennungskraftmaschinen mit elektrisch unterstütztem Antrieb |
JP3843932B2 (ja) * | 2002-03-26 | 2006-11-08 | トヨタ自動車株式会社 | ターボチャージャ |
JP2003298268A (ja) * | 2002-03-29 | 2003-10-17 | Denso Corp | 電子制御装置の筐体構造及び電子制御装置の冷却構造 |
US6668553B1 (en) * | 2002-09-13 | 2003-12-30 | Honeywell International Inc. | Ejector-based cooling system for turbochargers |
US7302804B2 (en) * | 2003-06-24 | 2007-12-04 | Honeywell International, Inc. | Cabin air compressor cooling system |
DE10343758B4 (de) * | 2003-09-22 | 2015-02-19 | Robert Bosch Gmbh | Verfahren zur Begrenzung des Druckanstieges in einem Hochdruck-Kraftstoffsystem nach Abstellen eines Verbrennungsmotors |
JP4367184B2 (ja) * | 2003-10-03 | 2009-11-18 | トヨタ自動車株式会社 | ターボチャージャ |
US7056103B2 (en) * | 2004-03-05 | 2006-06-06 | Honeywell International, Inc. | Method and apparatus for cooling turbomachinery components |
JP4539487B2 (ja) * | 2005-08-05 | 2010-09-08 | 株式会社Ihi | 電動機付過給機 |
US7448212B2 (en) * | 2006-02-27 | 2008-11-11 | International Engine Intellectual Property Company, Llc | Engine bleed air passage and method |
US8439019B1 (en) * | 2009-02-25 | 2013-05-14 | Accessible Technologies, Inc. | Compressed air delivery system with integrated cooling of a continuous variable transmission |
US8544453B2 (en) * | 2009-09-25 | 2013-10-01 | James E. Bell | Supercharger cooling |
JP5174073B2 (ja) * | 2010-03-18 | 2013-04-03 | 三菱重工業株式会社 | 電動過給装置 |
FR3022946B1 (fr) * | 2014-06-26 | 2019-06-28 | Valeo Systemes De Controle Moteur | Systeme moteur avec circuit de recirculation des gaz brules |
-
2016
- 2016-02-08 FR FR1650972A patent/FR3047515B1/fr not_active Expired - Fee Related
-
2017
- 2017-02-06 JP JP2018541335A patent/JP6882308B2/ja active Active
- 2017-02-06 RU RU2018132014A patent/RU2698374C1/ru active
- 2017-02-06 KR KR1020187026073A patent/KR102102343B1/ko active IP Right Grant
- 2017-02-06 WO PCT/FR2017/050266 patent/WO2017137687A1/fr active Application Filing
- 2017-02-06 US US16/066,436 patent/US10480400B2/en active Active
- 2017-02-06 CN CN201780012632.1A patent/CN108699962B/zh active Active
- 2017-02-06 EP EP17707383.0A patent/EP3414438B1/fr active Active
Also Published As
Publication number | Publication date |
---|---|
KR20180107248A (ko) | 2018-10-01 |
RU2698374C1 (ru) | 2019-08-26 |
CN108699962A (zh) | 2018-10-23 |
FR3047515A1 (fr) | 2017-08-11 |
EP3414438B1 (fr) | 2019-12-04 |
FR3047515B1 (fr) | 2018-02-02 |
CN108699962B (zh) | 2021-01-08 |
JP2019512059A (ja) | 2019-05-09 |
KR102102343B1 (ko) | 2020-04-20 |
WO2017137687A1 (fr) | 2017-08-17 |
US20190153934A1 (en) | 2019-05-23 |
JP6882308B2 (ja) | 2021-06-02 |
US10480400B2 (en) | 2019-11-19 |
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