FR2814198A1 - METHOD AND DEVICE FOR RECIRCULATION OF BURNED GASES FROM A COMBUSTION ENGINE - Google Patents

Abstract

The invention provides a method for managing the recirculation of burnt gases from a combustion engine (12) which comprises an intake manifold (16) and an exhaust manifold (18) of burnt gases which is connected to the manifold. inlet (16) by a recirculation duct (22) in which is interposed a movable valve (40) controlled, so as to allow, or not respectively, the circulation of gas between the exhaust manifold (18) and the camber (14), characterized in that the valve (40) is in the closed position when the pressure of the burnt gases in the exhaust manifold (18) is lower than the pressure in the intake manifold (16) and that the valve (40) is opened and then closed when the pressure of the burnt gases in the exhaust manifold (18) is greater than or equal to the pressure in the intake manifold (16). also a device for recirculating (10) the burnt gases from an engine (12 ) combustion which includes a recirculation duct (22).

Description

"Method and device for recirculating the burnt gases of an engine

  The present invention relates to a method for managing

  the recirculation of the burnt gases from a combustion engine.

  The invention also relates to a recirculation device

  burnt gases from a combustion engine.

  Internal combustion engines, and in particular diesel engines as well as certain gasoline engines with spark ignition, produce exhaust gases. Exhaust gases contain toxic pollutants

  such as nitrogen oxides or NOx.

  Nitrogen oxides are mainly formed in the areas of the combustion chamber where the richness

  of the air-fuel mixture is close to the stoichiometric ratio.

  The reaction of formation of nitrogen oxides is favored by a

high temperature.

  The emission standards applicable to motor vehicles impose maximum quantities of polluting substances released into the atmosphere. To limit discharges and meet standards, several solutions are proposed. One of them consists in injecting burnt gases into the combustion chamber of cylinders. This process is called recirculation

exhaust gases.

  This process is based on the thermodynamic properties of exhaust gases which contain a large fraction of carbon dioxide whose heat capacity is greater than that of other species mainly present in the air.

  fresh such as nitrogen and oxygen.

  Thus, during the release of energy caused by combustion of the fuel, carbon dioxide absorbs a greater amount of energy than that which would be absorbed

  by the other species mainly present in the fresh air.

  Consequently, the temperature of the gases in the combustion chamber is reduced, which greatly reduces the quantity

of nitrogen oxides produced.

  To do this, it is known to arrange a recirculation duct between the exhaust manifold of the burnt gases and the manifold for admitting fresh air into the combustion chambers of the cylinders, in which a valve is interposed.

dosing.

  However, for certain engine operating points, the circulation of gases from the exhaust manifold to the intake manifold is not satisfactory. In fact it is necessary, in particular at low speeds, to use, in addition to the metering valve, devices such as venturis, non-return valves, or exhaust gas pumps so as to force the gas flow from

  i exhaust manifold to the intake manifold.

  Such devices do not always make it possible to obtain a

  satisfactory result, moreover they are expensive and their function-

  Sometimes it requires energy contributions which increase

  significantly the fuel consumption of the vehicle.

  In order to remedy these drawbacks, the invention proposes a method for managing the recirculation of the burnt gases of a combustion engine which comprises an intake manifold

  fresh air in at least one cylinder and one exhaust manifold

  ment of the burnt gas which is connected to the intake manifold by a recirculation duct in which is interposed a movable controlled valve, between an open position and a closed position so as to allow, or not respectively, the circulation of gas between the manifold and the intake manifold, characterized in that the valve is in the closed position when the pressure of the burnt gases in the exhaust manifold is lower than the pressure in the intake manifold and the opening and then closing of the valve when the pressure of the burnt gases in the exhaust manifold is greater than or equal to the pressure in the intake manifold so as to allow circulation of the burnt gases only from the exhaust manifold to the chamber

cylinder combustion.

  According to other characteristics of the invention - the opening of the valve is controlled when the pressure in the exhaust manifold increases and becomes equal to the pressure in the intake manifold; - the valve is closed when the pressure in the exhaust manifold decreases and becomes equal to the pressure in the intake manifold; the pressure of the burnt gases in the exhaust manifold and / or the pressure of the fresh air in the intake manifold are determined from information representative of an engine parameter; - said engine parameter is the engine speed - said engine parameter is the angular position of the crankshaft. The invention also provides a device for recirculating the burnt gases of a combustion engine of the type which comprises a recirculation duct which connects an exhaust manifold for the burnt gases and the chamber of at least one cylinder of the engine and, in which is interposed a movable valve which is controlled

  according to the process according to any one of the claims

  previous, characterized in that the movable valve is actuated by an electromagnetic device allowing the opening and the

  the movable valve closes several times per engine revolution.

  According to other characteristics of the device according to the invention: - the recirculation duct connects the exhaust manifold of the burnt gases to the intake manifold of the cylinder chamber; - a device for mixing fresh air and burnt gases is interposed in the recirculation duct, between the exhaust manifold and the combustion chamber of the cylinder; - a device for cooling the burnt exhaust gas is interposed in the recirculation duct between the

  exhaust manifold and cylinder chamber.

  Other characteristics and advantages of the invention

  will appear on reading the following detailed description for the

  understanding of which reference will be made to the appended drawings in which: FIG. 1 schematically represents a combustion engine equipped with a circuit for recirculating the burnt gases; - Figure 2 shows the evolution of the pressure in the exhaust manifold, as well as the evolution of the pressure in the intake manifold; - Figure 3 is a sectional view of a controlled valve allowing the circulation of the burnt gases from the exhaust manifold to the intake manifold of the combustion engine; - Figure 4 is a view similar to that shown in

  Figure 1, the engine being equipped, in particular with a turbo-

  compressor, a device for mixing recirculated gases with

  fresh air, as well as gas cooling devices.

  FIG. 1 schematically represents a device 10 for recirculating the burnt gases which mainly comprises a combustion engine 12 which here comprises six cylinders comprising

  each a combustion chamber 14.

  An intake manifold 16 allows fresh air from the atmosphere to be introduced into each combustion chamber 14. The device 10 here comprises, facing the intake manifold 16, an exhaust manifold 18 which makes it possible to evacuate, to an exhaust manifold 20, the burnt gases which are expelled from the combustion chambers by the pistons of

motor 12.

  A treatment device, not shown, such as a particle filter or a nitrogen oxide trap, can be interposed in the exhaust pipe 20, so as to reduce the

  quantity of polluting substances released into the atmosphere.

  In known manner, the recirculation device 10 also includes a recirculation conduit 22 which connects the exhaust manifold 18 of the burnt gases to the intake manifold 16

fresh air.

  Here, the recirculation duct 22 connects a first downstream branch 24 of the exhaust manifold 18, which allows the recirculation of the burnt gases from three combustion chambers 14,

  io towards the free upstream end of the intake manifold 16.

  In order to allow the recirculation of the burnt gases from all the combustion chambers 14, the device may include a second recirculation duct, not shown, which connects a second downstream branch 26 of the exhaust manifold 18, and which allows the recirculation of the burnt gases from the other three combustion chambers 14, towards the free upstream end of the

intake manifold 16.

  According to variants, not shown, the intake manifold 16 and / or the exhaust manifold 18 comprise a connection point or a bifurcation on one of their ramifications 28 or 30 respectively. In this case, the treatment device 10 can comprise as many recirculation conduits 22 as necessary so that burnt gases can

  be introduced into each of the combustion chambers 14.

  The conduit 22 can also lead directly into a

chamber 14 of engine 12.

  A valve 40 is interposed in the duct 22. The valve is controlled, between an open position and a closed position so as to allow, or not respectively, the circulation of the burnt gases between the exhaust manifold 18 and

  the fresh air intake manifold 16.

  In order to remedy the drawbacks mentioned above, the invention proposes that the controlled valve 40 be in the closed position when the pressure in the exhaust manifold 18 is lower than the pressure in the intake manifold 16 and that it is in open position when the pressure in the exhaust manifold 18 is greater than or equal to the pressure in the intake manifold 16, so that the burnt gases flow only from the exhaust manifold

  18 to the intake manifold 16.

  FIG. 2 represents the evolution of the pressure P1 in the intake manifold 16, as well as the pressure P2 in the exhaust manifold 18 as a function of the angle of rotation ce

engine crankshaft 12.

  The evolution of the pressure P1 in the manifold

  intake 16 and pressure P2 in the exhaust manifold

  ment 18 is here represented on two turns of the crankshaft for the circuit 22 which connects the first downstream branch 24 of the exhaust manifold 18 and the intake manifold 16, in accordance

in Figure 1.

  To determine the pressure of the burnt gases in the exhaust manifold 18 and / or the pressure of the fresh air in the intake manifold 16, it is possible to use pressure sensors located in the first downstream branch 24 of the exhaust manifold 18 and in the intake manifold 16 respectively. According to the invention, it is also possible to determine the pressures P1, P2 from information representative of an engine operating parameter, such as the engine speed or the angular position of the crankshaft. Indeed, such parameters can be used for managing or controlling other devices of the engine 10 or of the vehicle. A calculation system makes it possible, from these parameters, to determine the pressures P1, P2 prevailing in the intake manifold 16 and the

  exhaust manifold 18 respectively.

  The pressure P1 in the intake manifold 16 is substantially constant while the pressure P2 in the

  exhaust manifold 18 has large variations.

There are then two phases.

  During a first phase designated by the reference PH1, the pressure P2 in the exhaust manifold 18 is

  higher than the pressure P1 in the intake manifold 16.

  It is represented in FIG. 2 by three pressure peaks which each correspond to the opening of the exhaust valve or valves of each of the chambers 14 connected to the first

downstream branch 24.

  When the valve 40 is in the open position, the burnt gases 1o then circulate from the exhaust manifold 18 to the manifold

admission 16.

  During a second phase designated by the reference PH2, the pressure P2 in the exhaust manifold 18 is

  lower than the pressure P1 in the intake manifold 16.

  In this case, if the controlled valve 40 is in the open position, the flow of gases located inside the recirculation conduit 22 tends to move from the intake manifold 16 to the exhaust manifold 18. Such circulation does not make it possible to ensure optimum control of the quantity of burnt gases which must be reintroduced into the combustion chambers 14 so as to reduce as much as possible the production of nitrogen oxides while ensuring the stability of combustion. In addition, the circulation

  gas from the intake manifold 16 to the exhaust manifold

  ment 18 does not allow, in certain cases, the reintroduction of the maximum flow rate of burnt gases in the combustion chambers 14.

  The valve 40 is then controlled as described above.

  so as to eliminate any risk of gas circulation in the duct 22, directed from the intake manifold 16 towards the

exhaust manifold 18.

  The controlled valve 40 must have a very short response time so as to open and close over a few degrees of angle of the crankshaft. In fact, the accuracy of the quantity of recirculated burnt gases depends on the speed of opening and closing of the controlled valve 40. In addition, the shorter the response time of the valve 40, the more the quantity of gases recirculated burns can be significant. In fact, the faster the opening and closing, the longer the time during which the valve is in the open opening position. The recirculation device 10 according to the invention is particularly advantageous during operation of the engine at low speed and at high load. In fact, it is in this case that the surfaces S1, hatched in FIG. 2, are representative of the maximum quantity of the burnt gases which are subjected to a pressure P2 in the exhaust manifold 18 greater than the pressure P1 which reigns in the intake manifold 16, are the smallest. The quantity of burnt gases recirculated to optimally reduce the production of nitrogen oxides can be

  substantially equal to said maximum quantity.

  In order to allow the maximum quantity of burnt gases to be recirculated, the invention proposes that the opening of valve 40 be controlled at time 10, that is to say when the pressure P2 in the exhaust manifold 18 increases and becomes equal to the pressure P1 in the intake manifold 16, so that the valve 40 is opened as soon as the pressure difference between the exhaust manifold 18 and the intake manifold 16 allows the circulation of gases burner from the collector

  exhaust 18 to the intake manifold 16.

  In order to anticipate the evolution of the pressure in the exhaust manifold 18, the instant of opening of the valve 40 can be slightly anticipated relative to the instant of opening

10 shown in Figure 2.

  In addition, the valve 40 is closed at the closing time IF, that is to say when the pressure P2 in the exhaust manifold 18 decreases and becomes equal to the pressure P1 in the manifold. inlet 16 so that the valve 40 is closed as soon as the pressure difference between the exhaust manifold 18 and the intake manifold 16 allows more circulation of the burnt gases from the manifold

  exhaust 18 to the intake manifold 16.

  The closing of the valve 40 can be slightly delayed with respect to the closing instant IF, represented in FIG. 2, so as to take into account the inertia of the burnt gases moving in the duct 22 and to stop the flow gases in the duct 22, when the direction of movement of the burnt gases

io is reversed.

  When the optimum quantity of the burnt gases to be recirculated is less than the maximum quantity of the burnt gases which it is possible to reintroduce into the combustion chambers 14, when the controlled valve 40 is open at the instant 10 and is closed at i l instant IF, the opening and closing of the valve 40 are controlled by a control device 41, so as to be progressive so that the quantity of burnt gases recirculated

  corresponds to the optimal quantity of burnt gases to be recirculated.

  To obtain the same result, the instants of opening 10 and closing IF can also be offset within the first phase PH1, that is to say they can be delayed or anticipated with respect to the opening time 10 or at the time of

IF closing respectively.

  The opening 10 and closing instants IF can also be offset outside the first phase PH1, thus allowing gas to flow from the intake manifold 16 to the exhaust manifold 18, thereby reducing the amount of

recirculated burnt gases.

  The instants 10 for opening and closing IF for the valve 40 can vary from the situation with the valve kept closed until

  the valve position kept open.

  According to the invention, the movable valve 40 is actuated by an electromagnetic device 42. The movable valve 40 can also be actuated by an electrical or electro-hydraulic device, not shown. Such control types allow

  very rapid actuation of valve 40.

  Figure 3 shows an example of an electro-

  magnetic 42 which is similar to those used in engines without camshaft called camless type. The use of such an electromagnetic actuating device 42 has a time

very weak response.

  The electromagnetic device 42 mainly consists of

  Lement of a body 44 of generally cylindrical shape which is coaxial with the axis XX of a movable member 46 of the valve 40 which closes, or not, the recirculation conduit 22 so as to allow, or not respectively, the circulation of the burnt gases between the exhaust manifold 18 and the intake manifold 16. The body 44 can be fixed to the cylinder head of the engine 10 by

i5 screws not shown.

  The body 44 contains two upper 48 and lower 50 electromagnets which are capable of acting on a disc-shaped actuating plate 52 which is mounted crimped at the upper end 54 of a rod 56 for actuating the organ

mobile 46.

  The electromagnetic device 42 also includes two

actuator springs.

  The first upper 58 is interposed axially between the upper face 60 of the disc 52 and an upper wall 62 of the

device 42.

  The second lower spring 64 is interposed axially between the lower face 66 of the disc 52 and a lower wall 68

of device 42.

  During the operation of the controlled valve 40, a magnetic field controlled by the control device 41 is produced between the two upper 48 and lower 50 electromagnets so as to drive the disc 52 as well as the movable member 46 in a high position or a low position allowing, or not

  respectively, closing the recirculation duct 22.

  It The value of the magnetic field, as well as its orientation, makes it possible to control the opening and closing of the valve 40, that is to say the speed of movement of the valve 40, as well as its position. In some cases, the valve 40 is not fully opened so as to partially close the conduit of

  recirculation 22 and to limit the quantity of recirculated burnt gases.

  According to a variant shown in FIG. 4, the recirculation duct 22 connects the free downstream end of a first branch of the exhaust manifold 18 to the free upstream end of the intake manifold 16. Symmetrically and not shown in the diagram a second circuit can connect the second branch of the exhaust manifold 18 to the free upstream end of the intake manifold 16. In this case, during two crankshaft turns, there are six first phases PH1 , each s5 followed by a second phase PH2, i.e. a sequence of first phase PH1 - second phase PH2 for opening the

  exhaust valves of each combustion chamber 14.

  In order to favor the mixing of the burnt gases circulating in the duct 22 and the fresh air, a gas mixing device 70 is arranged at the connection point between the intake manifold 16 and the duct 22. Thus, the mixture constituted exhaust gas and fresh air is more homogeneous in composition and temperature when it enters the

combustion chambers 14.

  In order to decrease the temperature of the burnt gases which are mixed with the fresh air, to decrease the temperature in the combustion chambers 14 and, consequently, the formation of nitrogen oxides, a gas cooling device 72 is arranged.

  in the recirculation conduit 22.

  Here, the cooler 72 is arranged downstream of the controlled valve 40, it is then called a hot valve. However, the cooler 72 can be placed upstream of the valve 40

  which is then called the cold valve.

  According to FIG. 4, the engine 10 comprises a turbocharger 74 which consists of a compressor 76 which pressurizes the atmospheric fresh air and a turbine 78 which is arranged in the exhaust pipe 20 and which supplies the energy mechanics required to drive compressor 76.

  The compression of atmospheric air in compressor 76 causes its temperature to increase.

  In order to limit the temperature of the gases injected into the combustion chambers 14 as well as the formation of oxides during combustion, the intake duct 80 which connects the

  compressor 76 at the intake manifold 16 includes an air cooler device 82.

Claims (10)

  1. Method for managing the recirculation of the burnt gases of a combustion engine (12) which comprises an intake manifold (16) of fresh air into at least one cylinder and an exhaust manifold (18) of the gases burnt which is connected to the intake manifold (16) by a recirculation duct (22) in which is interposed a movable valve (40) controlled, between an open position and a closed position so as to allow, or not respectively, the gas circulation between the exhaust manifold (18) and the intake manifold (16), characterized in that the valve (40) is in the closed position when the pressure of the burnt gases in the exhaust manifold (18 ) is lower than the pressure in the intake manifold (16) and that the opening and then closing of the valve (40) is controlled when the pressure of the burnt gases in the exhaust manifold (18) is higher or equal to the pressure in the intake manifold (16) so is not   allow circulation of burnt gases only from the exhaust manifold   pement (18) to the combustion chamber (14) of the cylinder.   2. Method for managing the recirculation of the burnt gases according to the preceding claim, characterized in that the opening of the valve (40) is controlled when the pressure (P2) in the exhaust manifold (18) increases and becomes equal   at pressure (P1) in the intake manifold (16).   3. Method for managing the recirculation of burnt gases   according to one of claims 1 or 2, characterized in that   controls the closing of the valve (40) when the pressure (P2) in the exhaust manifold (18) decreases and becomes equal to   the pressure (P1) in the intake manifold (16).   4. Method for managing the circulation of burnt gases   according to any one of the preceding claims,   characterized in that the pressure (P2) of the burnt gases in the exhaust manifold (18) and / or the pressure (P1) of the fresh air in the intake manifold (16) are determined from   information representative of an engine parameter (12).   5. A method of managing the circulation of burnt gases according to the preceding claim, characterized in that said parameter of the engine (12) is the engine speed. 6. Method for managing the circulation of burnt gases   according to one of claims 4 or 5, characterized in that said   parameter of the engine (12) is the angular position (cc) of the crankshaft. 7. Device for recirculating (10) the burnt gases of a combustion engine of the type which comprises a recirculation duct (22) which connects an exhaust manifold (18) of the burnt gases and the combustion chamber (14) d '' at least one engine cylinder (12) and, in which is interposed a movable valve i5 (40) which is controlled according to the method according to one   any one of the preceding claims, characterized in   that the movable valve (40) is actuated by an electromagnetic device (42) allowing the opening and closing of the   valve (40) movable several times per revolution of the engine.   8. Device for recirculating (10) the burnt gases of an engine (12) according to the preceding claim, characterized in that the recirculation duct (22) connects the exhaust manifold (18) of the burnt gases to the collector admission (16)   from the combustion chamber (14) of the cylinder.   9. Device for recirculating (10) the burnt gases of a   motor (12) according to one of claims 7 or 8, characterized in   that a device (70) mixing fresh air and burnt gases is interposed in the recirculation duct (22), between the exhaust manifold (18) and the combustion chamber (14) 3o of the cylinder.   10. Recirculation device (10) for the burnt gases of a   motor according to any one of claims 7 to 9,   characterized in that a device (72) for cooling the burnt exhaust gases is interposed in the recirculation duct (22) between the exhaust manifold (18) and the   combustion chamber (14) of the cylinder.