EP3607191A1 - Ensemble moteur turbocompresse a deux conduits d'echappement a reintroduction de gaz brules - Google Patents
Ensemble moteur turbocompresse a deux conduits d'echappement a reintroduction de gaz brulesInfo
- Publication number
- EP3607191A1 EP3607191A1 EP18712994.5A EP18712994A EP3607191A1 EP 3607191 A1 EP3607191 A1 EP 3607191A1 EP 18712994 A EP18712994 A EP 18712994A EP 3607191 A1 EP3607191 A1 EP 3607191A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- exhaust
- engine
- valve
- flow
- duct
- 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.)
- Withdrawn
Links
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
- F02D9/04—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits concerning exhaust conduits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
- F01N13/08—Other arrangements or adaptations of exhaust conduits
- F01N13/10—Other arrangements or adaptations of exhaust conduits of exhaust manifolds
- F01N13/107—More than one exhaust manifold or exhaust collector
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
- F01N3/08—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous
- F01N3/10—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust
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- 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
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
- F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
- F02D13/0242—Variable control of the exhaust valves only
- F02D13/0249—Variable control of the exhaust valves only changing the valve timing only
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
- F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
- F02D13/0257—Independent control of two or more intake or exhaust valves respectively, i.e. one of two intake valves remains closed or is opened partially while the other is fully opened
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- 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
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/01—Internal exhaust gas recirculation, i.e. wherein the residual exhaust gases are trapped in the cylinder or pushed back from the intake or the exhaust manifold into the combustion chamber without the use of additional passages
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- 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
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/02—EGR systems specially adapted for supercharged engines
- F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
- F02M26/05—High pressure loops, i.e. wherein recirculated exhaust gas is taken out from the exhaust system upstream of the turbine and reintroduced into the intake system downstream of the compressor
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- 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
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/40—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with timing means in the recirculation passage, e.g. cyclically operating valves or regenerators; with arrangements involving pressure pulsations
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- 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
- Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
- Y02A50/00—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE in human health protection, e.g. against extreme weather
- Y02A50/20—Air quality improvement or preservation, e.g. vehicle emission control or emission reduction by using catalytic converters
-
- 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
- the present invention relates to an engine assembly comprising an internal combustion engine and a turbocharger for a motor vehicle, this system comprising two exhaust ducts with at least one rapid control valve for at least one of the exhaust ducts not passing through an energy recovery wheel in a turbocharger turbine.
- Such an exhaust system is connected to an output of the turbocharged engine, also called supercharged engine, for exhaust gas exhaust from combustion in the engine, the engine being advantageously but not only a gasoline engine four times.
- Figure 1 substantially takes a turbocharged gasoline engine assembly according to the state of the art closest described in particular in WO-A-2009/105463, with the difference that a fast control valve 13 is shown in Figure 1, this rapid control valve can be driven in accordance with the present invention or be subjected to another control according to the state of the art.
- Such an engine assembly is known under the name VEMB, abbreviation of the English name of "Valve Event Modulated Boost", translated into French by supercharging controlled by motor distribution.
- a thermal combustion engine forming part of the set 1 said supercharging controlled by engine distribution has at least one cylinder, in Figure 1 three cylinders.
- Each engine cylinder is equipped with an intake valve and two exhaust valves. These exhaust valves are selectively associated with a first or a second exit passage in each cylinder and selectively open and close their associated passage.
- each cylinder It is the same for the intake valve associated with an inlet passage in each cylinder.
- the two outlet passages of each cylinder which are closed and opened sequentially by their associated exhaust valve open on a different exhaust manifold 5, 7 each supplying a dedicated exhaust duct 4, 6, the two ducts 4, 6 exhaust does not follow the same course as will be detailed below.
- the first exhaust passage of each cylinder is connected at the first manifold 5 and the second exhaust passage is connected to the second manifold 7.
- a motor assembly 1 said supercharging controlled by engine distribution therefore comprises a first duct 4 said exhaust turbine 2 starting from a first exhaust manifold 5 and a second duct 6 said discharge from a second exhaust manifold 7, the exhaust manifolds 5, 7 being each respectively connected to one of two series of first or second exhaust passages provided with their exhaust valves 19, 19a provided for each cylinder.
- the first duct 4 leads to an inlet face of the turbine 2 of the turbocharger being extended by a main expansion passage inside the turbine 2 housing a turbine wheel to recover the kinetic energy content. in the exhaust gas passing through it.
- the second duct 6 bypasses the turbine 2 without entering but joins further downstream of the turbine 2 a third duct 9 outside the turbine 2 and connected to an outlet face of the turbine 2 for exhausting the exhaust gas.
- main flashing passage having been in exchange for energy with the turbine wheel.
- the function of the first duct 4 said exhaust duct turbine is to allow a first flow of exhaust gas through the turbine 2 and its rotary energy recovery member in the form of a wheel to provide the power to the compressor 3.
- the function of the second duct 6, said discharge duct and supplied by a second exhaust manifold 7, different and independent of the first exhaust manifold 5 of the first duct 4, is to allow a second flow of independent exhaust gas and different from the first flow to bypass the turbine 2 and in particular its wheel and thus discharge the turbine 2 of the total flow of exhaust gas by decreasing the flow of exhaust gas therethrough by subtraction of the second stream to the total flow.
- a discharge valve which may be internal or external to the turbine serves to limit the pressure of the exhaust gas on the turbine wheel of the turbocharger by opening a bypass of the exhaust gas so that they no longer pass through the turbine and its wheel.
- a limitation of the speed of the wheel of the turbine is thus obtained, which also limits the rotational speed of the wheel provided in the compressor being integral with the impeller of the turbine, which also limits the compression of the impeller. intake air.
- a relief valve associated with a turbine for regulating the flow of exhaust gas therethrough is no longer necessary with a motor-controlled supercharging engine assembly having two exhaust ducts each starting from a collector respective exhaust.
- FR-A-3032486 substantially reproduces the characteristics of the first state of the art described above.
- This document discloses a turbine provided with a casing surrounding it, the first duct opening into the main relief passage through an inlet face of the casing. This is illustrated in Figure 2.
- the second conduit 6 opening into at least one branch portion 8 internal to the casing 2c bypassing the main expansion passage, the rapid control valve 13 being housed in the housing 2c.
- the main expansion passage and said at least one branch portion 8 are joined to an outlet face of the housing 2c, the exhaust system comprising a third duct 9 outside the turbine 2 being connected to the outlet face of the turbine casing for the discharge of the exhaust gas out of the turbine.
- a motor supercharging engine controlled by engine distribution allows to gain the indicated average pressure and therefore in consumption as soon as it is boosted compared to a standard turbocharged engine. It is the exhaust valve connected to the first turbine exhaust duct that opens first and sends the exhaust puff to the turbine.
- the problem underlying the invention is to be able to recirculate exhaust gases from a two-duct exhaust system powered by two exhaust valves of the same cylinder in a motor.
- a motor assembly said supercharged controlled by engine distribution to two exhaust ducts in a simple and effective manner directly in the exhaust system according to the operating conditions then in force of the motor assembly, this recirculation occurring especially when an exhaust phase during the crossing of the second exhaust valve with the engine intake valve.
- a method of controlling an exhaust of a heat engine assembly of a motor vehicle comprising an exhaust system housing a turbine of a turbocharger, the engine comprising at least one cylinder housing a piston connected to a crankshaft in rotation, a full engine load as a function of the engine speed being determined specifically for the engine, said at least one cylinder having an inlet passage provided with an engine valve; intake and first and second exhaust passages opening into the exhaust system respectively provided with a first and a second exhaust valves taking positions of opening or closing their associated passage at an angle of rotation of the crankshaft, the opening of the second passage being out of phase with the opening of the first passage, the escapement having first and second gas exiting the engine, a first flow per turbine from the first passage through the turbine housing a partial recovery wheel of an energy contained in the gas and a second discharge flow from the second passage joining the first flow downstream of the wheel bypassing it, a common opening time of the inlet valve and the second valve taking place at the end of an exhaust phase,
- the technical effect is to obtain a deactivation of the second flow through the so-called discharge duct bypassing the turbine this at each end of the exhaust phase of one or the engine cylinder forming part of the engine assembly during a crossing of the intake valve and the second exhaust valve.
- This makes it possible to improve the response of the engine in stabilized and transient conditions, in particular under transient conditions at full load and at low speed or at a relatively low partial load corresponding to an effective mean pressure of less than 10 6 Pascals. Gases of the second stream are reintroduced into the combustion chamber.
- the second exhaust valve opens during an exhaust phase, it can be obtained by a rapid control valve disposed on the second duct of the exhaust system or, where appropriate, on an extension of the exhaust system. second conduit in the turbine, that the second flow be interrupted at least partially in the exhaust system and a part of the flow returns to the combustion chamber of the cylinder or cylinders.
- it is carried out a closing of the second flow downstream of the second valve during the common opening period followed by reopening after an end of the common opening time, at least a portion of the second flow returning in said at least one cylinder by the second passage associated with the second valve.
- it is carried out an introduction of a portion of the first exhaust stream in the second flow downstream of the first and second valves during the common opening time, the second flow being closed downstream of the reintroduction of a portion of the first stream, at least a portion of the second stream and the portion of the first stream returning to said at least one cylinder through the second passage associated with the second valve.
- it is to create a connection between the first and second exhaust valves gas leak or equivalent of a gas leak to the second flow, which maximizes the capacity recirculating burnt gases by recovering a puff of gas from the first stream of the cylinder according to the ignition order, while the second exhaust valve is still open in the crossing phase with the intake valve.
- the second flow downstream of the second valve is closed during the common opening period or, for partial load of the engine under an effective mean pressure of less than 10 6 Pascals, it is carried out the introduction of a portion of the first exhaust stream in the second flow downstream of the first and second valves during the common opening time , the second flow being closed downstream of the introduction.
- the first of these configurations it is necessary to recirculate less flue gases than in the second.
- the recirculated gas stream from the second stream is enriched with a portion of gas from the first exhaust stream.
- the invention also relates to an engine assembly comprising a heat engine, an exhaust system with a turbine of a turbocharger for the implementation of such a method, the exhaust system being connected to the engine comprising the at least one cylinder having an inlet passage provided with an intake valve and first and second outlet passages for exhaust gas discharge from combustion in the engine respectively provided with first and second valves of exhaust opening the associated passage and shutter sequentially, the system comprising a first exhaust duct by the turbine leaving the first valve and a second discharge duct from the second valve, the turbine being provided in its interior with a main relaxation passage in which is housed a turbine wheel and the first conduit opening into the main passage of relaxation, the second conduit conto urnning the wheel of the turbine, characterized in that the exhaust system comprises means for forced increase of a pressure in the second conduit controlled by a control unit having means for detecting a common opening of the valve intake and the second valve and means for estimating or measuring an effective mean pressure, a partial load of the engine and an engine speed.
- the major problem that the present invention has solved is the consumption penalty in partial loads under 10 6 Pascals (10 bar) of effective average pressure associated with a supercharged engine by engine distribution.
- the present invention makes it possible to maximize the gains on test cycles as well as in normal use by overcoming the penalty at low loads as well as total loads at low speeds.
- the present invention allows in particular to give the potential for carbon dioxide at relatively low partial load where such a supercharged engine loses carbon dioxide in comparison with a standard engine.
- a motor supercharged by engine distribution provided with the improvement proposed by the present invention can really win over the entire engine field and maximize the consumption gain.
- the second duct comprises a rapid control valve interrupting the flow of exhaust gas in the second duct during a common opening of the intake valve and the second exhaust valve, the rapid control valve. being controlled by the control unit comprising means for actuating the fast control valve during this opening according to the effective mean pressure, the engine speed and the partial load being estimated or measured by the estimation means.
- the turbine is provided with a casing surrounding it, the second duct opening into at least one internal bypass portion to the casing bypassing the main expansion passage, the rapid control valve being housed in the casing or the housing.
- second conduit comprises a branch portion of the turbine, the rapid control valve being carried by this branch section.
- the fast control valve is a three-way valve and the second conduit has a stitching on the first conduit, with a first closed position of the second conduit kept sealed with respect to a gas flow from the first conduit by quenching of the quilting, a second position of a communication of the first duct in the second duct and passage of a partial flow of exhaust gas from the first duct to the second duct by opening the quilting, the second duct being closed downstream of the communication between first and second ducts, and a third open position of the second duct kept sealed with respect to a gas flow from the first duct, the quilting being closed.
- the first passage is connected to a first exhaust manifold while the second output passage is connected to a second exhaust manifold, the first conduit from the first manifold and the second conduit from the second manifold, the exhaust system comprising a leakage channel from the first manifold to the second manifold, the control unit having actuating means opening or closing a valve in the leakage channel according to the effective mean pressure, the partial load and the engine speed estimated or measured by the estimating means.
- FIG. 1 is a diagrammatic representation of a turbocharged motor-controlled supercharging engine assembly comprising an exhaust system with two exhaust ducts, the second duct being outside a turbine and having a fast control valve according to a first embodiment of the present invention providing means for forced pressure increase in the second conduit during the crossing time of the intake valve and the second exhaust valve called discharge for a return of a part of the second flow in said at least one cylinder for full load conditions under engine speed below 3000 rpm or engine partial load under an effective mean pressure of less than 10 6 Pascals,
- FIG. 2 is a schematic representation of a second motor assembly comprising an exhaust system with two exhaust ducts according to another embodiment according to the present invention, the turbine being traversed by the two ducts and the second duct; having a fast control valve according to the first embodiment of the present invention,
- FIGS. 3, 4 and 5 show pressure curves as a function of a crankshaft angle for a turbocharged assembly respectively to an exhaust duct, a set with two exhaust ducts and a set with two exhaust ducts with means for forcing pressure increase in the second conduit during the crossing time of the intake valve and the second exhaust valve called discharge, the latter figure being in accordance with the present invention
- FIGS. 6a, 6b and 6c illustrate various positions of closing and opening of a three-way valve as a means of forcing pressure increase in the second conduit during the crossing time of the intake valve and the second exhaust valve called discharge, this three-way valve equipping a motor-controlled supercharging engine assembly according to the present invention
- FIG. 7 shows a curve of full load with a given engine torque as a function of the engine speed in a motor assembly according to the present invention and equipped with the three-way valve shown in FIGS. 6a, 6b and 6c.
- the words downstream and upstream are to be taken in the direction of the flow of exhaust gas out of the engine, an element in the exhaust system downstream of the engine being further from the engine than another element upstream of the element.
- the engine assembly includes the engine as well as its auxiliaries for the intake of air into the engine and for the exhaust of gases out of the engine, a turbocharger also forming part of the engine assembly, the turbine being included in the exhaust system of the engine assembly. Referring to Figures 1 and 2, it will be described characteristics that are customary for a turbocharged engine and more specifically for a supercharging engine controlled by engine distribution but which are not essential for the implementation of the present invention.
- the turbine 2 drives the compressor 3 by being secured to it by an axis, the compressor 3 being traversed by fresh air for supplying air to the engine, air compressor 3 compresses .
- the air which is then called charge air is supplied by the air supply line to a charge air cooler 25 to cool the air leaving the compressor 3.
- a butterfly valve 26 regulating the air flow in the engine air intake manifold forming the air inlet of the engine.
- EGR line a recirculation line of the exhaust gas to the engine air intake
- EGR line such a line being referenced 1 1 in Figure 1.
- An EGR line 1 1 has a stitching 12 on an element of one of the two exhaust pipes, for example the second exhaust manifold 7 or through the turbine 2, to withdraw a portion of the exhaust gas.
- the line EGR 1 1 comprises a cooler 23 of the exhaust gas passing through this line January 1, these gases then being very hot.
- the line RGE 1 1 opens on the intake of air upstream of the compressor 3 it feeds.
- a valve 24 called RGE valve equips the line RGE 1 1, advantageously downstream of the cooler 23 RGE in the flow direction of the recirculation gas to open or close the flow of gas to the inlet.
- the recirculation of the exhaust gas to the air intake of the engine improves the thermodynamic efficiency of the engine due to the reduction of heat transfer through the reintroduction. of gas recirculated through line EGR 1 1 in the intake manifold. Such recirculation may also allow a decrease in the enrichment related to the exhaust temperature and a decrease in pump losses when the engine is associated with a turbocharger.
- FIGs 3, 4 and 5 while referring to Figures 1 and 2 for missing references to these figures, show pressure curves in P bars (bars) depending on a crank angle ANGLE VIL respectively for a turbocharged assembly to an exhaust duct, a dual exhaust duct assembly with a motor-controlled supercharging engine and a dual exhaust duct assembly with means for forced pressure increase in the second duct during the crossing time of the intake valve and the second exhaust valve called discharge, the latter Figure 5 being representative of the pressures obtained by a turbocharged assembly according to the present invention.
- valve lift S2 of the second exhaust valve 19a is out of phase with the valve lift S1 of the first exhaust valve 19.
- first and second output passages are respectively open and when the first and second exhaust valves 19, 19a are closed, the first and second output passages are respectively closed.
- the exhaust has two gas exhaust flows at the output of the engine, a first flow called exhaust from the first passage of said at least one cylinder passing through the turbine 2 by a partial recovery wheel of a contained energy in the exhaust gas inside the turbine 2 and a second flow called discharge from the second outlet passage of said at least one cylinder joining the first flow downstream of the wheel bypassing it, either by passing to the outside of the turbine as shown in Figure 1 or passing inside the turbine as shown in Figure 2.
- FIG. 3 there is a crossing C soup between an intake valve whose lift is referenced SA and the single exhaust valve whose lift is referenced S1.
- the crossing C of the intake valve is made with the second exhaust valve 19a whose lift is referenced S2.
- FIG. 3 at the intersection C of intake and exhaust valve, there exists a difference in crossing pressure ⁇ which is greater than the difference in crossing pressure ⁇ of FIG. intake valve and the second exhaust valve 19a.
- the intake valve is opened and since the exhaust pressure PS1 is much greater than the intake pressure PA, this causes the reintroduction of burnt gases into the combustion chamber of the combustion chamber. cylinder.
- the reintroduction of burnt gases into the cylinder makes it possible to manage a portion of the engine load by the amount of flue gas reintroduced into the combustion chamber of the cylinder and not by the throttle valve to reduce pumping losses and limit transfers. in the chamber by a dilution effect.
- the present invention relates to a method for controlling an exhaust of a thermal engine assembly 1 of a motor vehicle, the engine being a supercharging engine controlled by engine distribution.
- Such an engine comprises an exhaust system housing a turbine 2 of a turbocharger, the engine comprising at least one cylinder housing a piston connected to a crankshaft in rotation.
- the effective mean pressure is the ratio between the work provided by the engine during a cycle and the displacement of the engine and calculates the engine load.
- the PME is proportional to the engine torque and therefore depends on the operating point of the engine that can be defined by the engine speed and load.
- the cylinder or each cylinder has an inlet passage provided with an intake valve and first and second exit passages opening into the system.
- exhaust respectively provided with a first and a second exhaust valves 19, 19a taking positions of opening or closing of their associated passage at an angle of rotation of the crankshaft, the opening of the second passage being out of phase compared to the opening of the first passage.
- the exhaust has first and second flows of gas at the engine outlet, a first flow per turbine from the first passage through the turbine 2 housing a partial recovery wheel of an energy contained in the gases. and a second discharge stream from the second passage joining the first flow downstream of the wheel bypassing it.
- the second flow passing through the second duct 6 passes outside the turbine 2 while in FIG. 2 the second flow by a bypass circuit 8 which bypasses the wheel of the turbine 2 while being inside the turbine 2.
- the present invention proposes to perform a forced increase in pressure of the second flow during the common opening time for a return of a portion of the second flow in said at least one cylinder in at least two cases .
- the first case is obtained for full load conditions under an engine speed below 3000 revolutions per minute referenced A in Figure 7.
- the second case is obtained for partial load conditions of the engine under a effective average pressure of less than 10 6 pascals, which is referenced B in Figure 7.
- burnt gases are then reintroduced into the combustion chamber of the cylinder or each cylinder in greater quantity than for a motor-controlled supercharging engine assembly of the state of the art.
- FIG. 5 a difference in crossing pressure ⁇ which is greater than the difference in crossover pressure ⁇ of FIG. 4.
- the present invention therefore makes it possible to increase the pressure in the second duct 6 of FIG. during the crossover phase of valves C soup, which increases the reintroduction of burnt gases into the combustion chamber of the or each cylinder of the engine and reduces the pumping losses introduced by the management of the load by the throttle valve as well as the heat transfers in the combustion chamber of the cylinder or each cylinder.
- the second flow downstream of the second valve 19a may be closed for the duration of the common opening followed by reopening after an end of the duration. common opening. After this closure, at least a portion of the second flow can no longer flow into the rest of the exhaust line downstream of the second valve 19a and can return to the at least one cylinder through the second passage associated with the second valve 19a as burned gases reintroduced into the combustion chamber of the cylinder or each cylinder.
- it may be performed an introduction of a portion of the first exhaust stream in the second stream downstream of the first and second valves 19, 19a during the period of time. common opening, the second stream being closed downstream of the introduction of a portion of the first stream.
- At least a portion of the second flow and the portion of the first flow can then return to said at least one cylinder by the second passage associated with the second valve 19a.
- This embodiment introduces more flue gas into the combustion chamber than in the first mode and therefore adapts to a case of operation of the specific engine requiring more reintroduced flue gas.
- FIG. 7 shows a full load curve with a motor torque C (Nm) Newton-meter given according to the engine speed N (rpm) in revolutions per minute in a motor assembly according to the present invention.
- zone C is a total or partial charging zone in which a modification of the fluxes with respect to the fluxes obtained according to the state of the art is not necessary.
- the operation of the motor-controlled supercharging engine according to the present invention is the same in this zone as that of a motor of the state of the art.
- a motor assembly 1 comprising a supercharging engine controlled by engine distribution and an exhaust system with a turbine 2 of a turbocharger.
- the exhaust system is connected to the output of an engine comprising at least one cylinder having an inlet passage provided with an intake valve and first and second outlet passages for exhaust gas discharge from combustion in the engine respectively provided with first and second exhaust valves 19, 19a opening the associated passage and closing sequentially, the outlet passages opening into the exhaust system.
- the system comprises a first exhaust pipe 4 by the turbine 2 starting from the first valve 19 and a second discharge pipe 6 starting from the second valve 19a, the turbine 2 being provided in its interior with a main passage detent in which is housed a turbine wheel and the first conduit 4 opening into the main passage of relaxation.
- the second duct 6 bypasses the wheel of the turbine 2, this being extended by a bypass duct 8 inside the turbine 2, as can be seen in FIG. 2 or bypassing the turbine 2 from the outside, as it is visible in Figure 1.
- the exhaust system comprises means for forced increase of a pressure in the second duct 6 controlled by a control unit.
- the control unit has means for detecting a common opening of the intake valve and the second valve, means for estimating or measuring an effective mean pressure, a partial load of the heat engine and a motor speed. This control unit can be the control unit of the engine.
- the second flow is closed downstream of the second valve 19a during the common opening time and then reopened by a rapid control valve 13.
- the rapid control valve 13 can be controlled by the control unit comprising means for actuating the fast control valve during this opening according to the effective mean pressure, the partial load and the engine speed estimated by the estimating means.
- the rapid control valve 13 can interrupt the flow of exhaust gas in the second conduit 6 during a common opening of the intake valve and the second exhaust valve 19a.
- FIGS. 1 and 2 Two non-limiting positions of this rapid control valve 13 are shown respectively in FIGS. 1 and 2.
- the rapid control valve 13 can be disposed outside the turbine 2, the second duct bypassing the turbine 2. is shown in Figure 1.
- the fast control valve 13 can be disposed in the turbine 2. This is shown in FIG.
- the turbine 2 may be provided with a casing 2c surrounding it, the second duct 6 opening into at least one branch portion 8 internal to the casing 2c bypassing the main relief passage.
- the fast control valve 13 can be housed in the casing 2c, which is shown in FIG. 2 where the second duct 6 bypasses the turbine 2 by including a bypass section of the turbine 2, the fast control valve 13 being worn. by this shunt section, which is shown in Figure 1.
- this valve 13 rapid control can be a three-way valve but this is not limiting.
- the different control modes can be realized with two 2-way valves, both in the exhaust manifold, one in the manifold and one in the turbine housing, or both in the turbine housing.
- the three-way valve, referenced 13 in Figures 1 and 2 but not referenced 13 in Figures 6a to 6c with only specific positions referenced 13a, 13b and 13c is located downstream of a turbine 2 on the second conduit 6 which is then outside the turbine 2.
- the three-way valve can be located elsewhere than outside and near the turbine 2, for example inside the turbine 2, the bypass portion 8 connected to the second conduit bypassing the wheel of the turbine 2, or in a second manifold 7 associated with the second conduit 6, or downstream of the second manifold 7 and upstream of the third conduit 9.
- the internal arrows in conduits 4 and 6 indicate the flow of the gas flows in these FIGS. 6a to 6c.
- the second duct 6 may have a stitching on the first duct 4, with a first closed position of the second duct 6 kept sealed with respect to a flow of gas from the first duct 4 by closing the quilting, this flow of gas from the first conduit 4 entering the second conduit 6.
- FIG. 6a This configuration can be used for zone A shown in FIG. 7 with total load or average load above 10 6 Pascals and relatively low engine speed, for example below 3000 rpm.
- a torque increase referenced Z1 obtained by the closing and thus the deactivation of the second exhaust flow flowing in the second duct 6 is shown in this FIG. 7.
- the reference 13b indicates that the control valve is closed for the second duct 6.
- FIG. 6b shows a second position of a communication of the first duct 4 in the second duct 6 and passage of a partial flow of exhaust gas from the first duct 4 to the second duct 6 by opening of the quilting.
- the second duct 6 is closed downstream of the communication between first and second ducts 4, 6, which is referenced 13b in this figure and a leak is open from the first duct 4 to the second duct, which is referenced 13a to this figure .
- This configuration can be used for Zone B shown in Figure 7 with low partial load below 10 6 Pascals for a wide range of engine speeds ranging from low to high.
- Figure 6c shows a third opening position of the second duct 6, which is referenced 13c, simultaneously maintained sealed with respect to a gas flow from the first duct 4, the quilting being closed.
- This configuration can be used for the zone C shown in FIG. 7 with average partial load above 10 6 Pascals and a wide range of engine speeds ranging from low to high, for example being above 3000 revolutions per minute.
- the first passage may be connected to a first exhaust manifold while the second output passage may be connected to a second manifold.
- the exhaust system may comprise a leakage channel from the first manifold 6 to the second manifold 7.
- the control unit may comprise actuating means opening or closing a valve in the leakage channel according to the effective mean pressure, the partial load and the engine speed estimated or measured by the estimation means.
- the valve can be controlled between different open or closed positions or be operable between a closed or open position.
- Another embodiment of the present invention is to size a connection between the first conduit 4 and the second conduit 6, this connection being passive and permanently existing.
- This connection can be dimensioned to maximize the ability to recirculate burnt gases in the combustion chamber of the cylinder or of each cylinder, this in particular in relatively low partial loads as previously mentioned and to minimize performance losses when the rapid control valve is closed.
- the control valve 13 is said to be fast because it can open during the opening range of the or each exhaust valve 19a during a motor cycle, which requires a very fast actuation of the control valve 13 , for example of the order of the time of an engine cycle divided by the number of cylinders (10 ms on an engine equipped with three cylinders).
- control valve 13 is associated with a mechanical, hydraulic, electrical or electromagnetic fast actuator.
- the rapid control valve 13 according to the present invention may have any suitable shape, for example without this being a limiting valve plug shape.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Health & Medical Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
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Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR1752971A FR3065033B1 (fr) | 2017-04-05 | 2017-04-05 | Ensemble moteur turbocompresse a deux conduits d’echappement a reintroduction de gaz brules |
PCT/FR2018/050573 WO2018185389A1 (fr) | 2017-04-05 | 2018-03-12 | Ensemble moteur turbocompresse a deux conduits d'echappement a reintroduction de gaz brules |
Publications (1)
Publication Number | Publication Date |
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EP3607191A1 true EP3607191A1 (fr) | 2020-02-12 |
Family
ID=58707926
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP18712994.5A Withdrawn EP3607191A1 (fr) | 2017-04-05 | 2018-03-12 | Ensemble moteur turbocompresse a deux conduits d'echappement a reintroduction de gaz brules |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP3607191A1 (fr) |
CN (1) | CN110520612A (fr) |
FR (1) | FR3065033B1 (fr) |
MA (1) | MA49337A (fr) |
WO (1) | WO2018185389A1 (fr) |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2334754A (en) * | 1998-02-27 | 1999-09-01 | Ford Global Tech Inc | Control of a gasoline i.c. engine power output/speed by exhaust gas recirculation |
CN101939529B (zh) * | 2008-02-22 | 2013-03-27 | 博格华纳公司 | 控制在涡轮增压与排气再循环之间分开的排气流动 |
DE102010060106B4 (de) * | 2010-10-21 | 2018-05-17 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Brennkraftmaschine |
RU2568025C2 (ru) * | 2011-05-02 | 2015-11-10 | Вольво Текнолоджи Корпорейшн | Способ и система двигателя внутреннего сгорания для поддержания интервала рабочих температур в системе доочистки отработавших газов |
FR3032486B1 (fr) * | 2015-02-09 | 2017-02-17 | Peugeot Citroen Automobiles Sa | Ensemble moteur turbocompresse a deux conduits d’echappement avec vanne de regulation rapide |
DE102015205848A1 (de) * | 2015-04-01 | 2016-10-06 | Volkswagen Aktiengesellschaft | Abgaseinrichtung zur Trennung von Abgasfluten eines Verbrennungsmotors mit mindestens zwei Zylindergruppen |
-
2017
- 2017-04-05 FR FR1752971A patent/FR3065033B1/fr active Active
-
2018
- 2018-03-12 EP EP18712994.5A patent/EP3607191A1/fr not_active Withdrawn
- 2018-03-12 CN CN201880023886.8A patent/CN110520612A/zh active Pending
- 2018-03-12 WO PCT/FR2018/050573 patent/WO2018185389A1/fr unknown
- 2018-10-11 MA MA049337A patent/MA49337A/fr unknown
Also Published As
Publication number | Publication date |
---|---|
MA49337A (fr) | 2020-02-12 |
FR3065033A1 (fr) | 2018-10-12 |
WO2018185389A1 (fr) | 2018-10-11 |
CN110520612A (zh) | 2019-11-29 |
FR3065033B1 (fr) | 2021-03-12 |
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