FR3059051A1 - THERMAL CONDITIONING DEVICE FOR FLUID FOR COMBUSTION ENGINE - Google Patents

Abstract

The present invention describes a device for thermal conditioning (50) of fluid for a combustion engine, comprising: - At least one heat exchanger (7), - Two mobile actuators (2a, 2b) arranged to selectively pass the fluid of a input (1) to an output (15) of the thermal conditioning device (50) according to at least three modes of operation: - In a first mode of operation, passing through a first section (21) of the heat exchanger (7) - In a second mode of operation through a second section (25) of the heat exchanger (7), the second section (25) having a heat exchange surface greater than that of the first section (21), - In a third mode of operation, directly from the inlet (1) to the outlet (15), characterized in that the transition from one mode of operation to another is ensured by a simultaneous displacement of the two mobile actuators (2a, 2b).

Description

Holder (s): VALEO MOTOR CONTROL SYSTEMS Simplified joint-stock company.

Extension request (s)

Agent (s): VALEO ENGINE CONTROL SYSTEMS Simplified joint-stock company.

THERMAL FLUID CONDITIONING DEVICE FOR A COMBUSTION ENGINE.

FR 3,059,051 - A1 f5 /) The present invention describes a thermal conditioning device (50) for fluid for a combustion engine, comprising:

- At least one heat exchanger (7),

- Two mobile actuators (2a, 2b) arranged to allow the fluid to pass selectively from an inlet (1) to an outlet (15) of the thermal conditioning device (50) according to at least three operating modes:

- In a first operating mode, by crossing a first section (21) of the heat exchanger (7),

- In a second operating mode by crossing a second section (25) of the heat exchanger (7), the second section (25) having a heat exchange surface greater than that of the first section (21),

- In a third operating mode, directly from the input (1) to the output (15), characterized in that the transition from one operating mode to another is ensured by simultaneous movement of the two movable actuators (2a , 2b).

i

Fluid thermal conditioning device for combustion engine

The present invention relates to a thermal fluid conditioning device for a combustion engine, in particular for a motor vehicle.

It is well known to recirculate part of the exhaust gas to the combustion air intake of a heat engine. In order to optimize engine operation, the flow of recirculated exhaust gases should be regulated. In addition, it is advantageous to also control the temperature of the recirculated exhaust gases.

To ensure fine regulation of the temperature of the recirculated exhaust gases, it is known, for example from patent DE 10 2006 052 972, to be able to modify the path of the exhaust gases through a heat exchanger. Thus, it is possible by controlling a first actuator to pass the gases without passing through the heat exchanger. Thanks to a second actuator, controlled independently of the first actuator, it is possible to selectively pass the recirculated exhaust gases either only in a part of the exchanger, or in the whole of the exchanger. By playing on the position of each of the two actuators, there is an operating mode without gas cooling, an operating mode with a first level of gas cooling and an operating mode with a second level of cooling of the gases. gas. It is thus possible to carry out thermal conditioning of the recirculated exhaust gases, that is to say to control the temperature at which the exhaust gases are readmitted at the intake of the engine.

The presence of two separate and independently controlled actuators makes the exhaust gas recirculation system more complex, and increases its cost.

The invention aims to provide a cooling system for recirculated exhaust gases making it possible to have the three operating modes already mentioned using a single command for the actuator.

Another aspect of the invention is to improve the lifetime of the heat exchanger, by avoiding the circulation of a leakage flow rate in the exchanger, which makes it possible to limit its fouling.

To this end, the invention provides a thermal fluid conditioning device for a combustion engine, comprising:

At least one heat exchanger,

Two mobile actuators arranged to selectively pass the fluid from an inlet to an outlet of the thermal conditioning device according to at least three operating modes:

In a first operating mode, allow the fluid to be conditioned to pass from the inlet to the outlet by passing through a first section of the heat exchanger,

In a second operating mode, allow the fluid to be conditioned to pass from the inlet to the outlet through a second section of the heat exchanger, the second section having a heat exchange surface greater than that of the first section,

In a third operating mode, allow the fluid to be conditioned to pass directly from the inlet to the outlet, characterized in that the transition from one operating mode to another operating mode is ensured by simultaneous displacement of the two movable actuators .

Each operating mode corresponds to a level of heat exchange efficiency with the fluid passing through the thermal conditioning device. It is thus possible to ensure control of the temperature at which the fluid leaves the thermal conditioning device.

According to one embodiment, each actuator is movable in rotation about an axis of rotation.

Advantageously, each actuator comprises a flap, each flap being arranged to selectively orient the passage of the fluid between the inlet and the outlet of the thermal conditioning device by cooperating with a plurality of fluid passage conduits of the thermal conditioning device.

The position of the flap of each of the two actuators makes it possible to modify the path of the fluid inside the conditioning device, and thus to modify the efficiency of the heat exchanges.

Preferably, the two actuators are linked in rotation.

The movement of the two actuators can thus be controlled by a single control means. The control of the packaging device is thus economical.

According to a preferred embodiment, the two actuators have a common rotation shaft.

The two actuators thus form a compact and rigid assembly.

According to another embodiment, the two actuators are linked in rotation by two toothed wheels meshing with each other directly or indirectly.

It is thus possible to offset one actuator relative to the other, which can facilitate the integration of the actuators.

Advantageously, a rotation of the mobile actuators in a first direction of rotation makes it possible to pass from the first mode to the second operating mode, and an additional rotation of the mobile actuators in the same direction of rotation makes it possible to pass from the second mode to the third operating mode.

The transition from one operating mode to another operating mode is thus easily carried out.

According to one embodiment, the movable actuators are arranged so that, in the first operating mode, the fluid to be conditioned successively passes through a first heat exchange beam and a second heat exchange beam of the heat exchanger, an inlet of the first beam and an output of the second beam then being placed side by side.

This first operating mode corresponds to a first level of heat exchange. This operating mode is called "low efficiency" heat exchange. In this mode, the fluid travels only part of the heat exchanger.

Advantageously, the movable actuators are arranged so that, in the second operating mode, the fluid to be conditioned jointly crosses the first beam and the second heat exchange beam, and then crosses a third heat exchange beam.

This second operating mode corresponds to a second level of heat exchange. This operating mode is called "high efficiency" heat exchange. In this mode, the fluid travels a greater part of the heat exchanger than in the first mode. Preferably, the fluid traverses the entire heat exchanger so as to maximize the heat exchange between the fluid to be conditioned and the heat transfer fluid.

Advantageously also, the movable actuators are arranged so that, in the third operating mode, the fluid to be conditioned passes directly from the inlet to the outlet.

This third operating mode corresponds to a mode without forced heat exchange. This operating mode is qualified by the English acronym "by-pass". In this mode, the fluid travels through the conditioning device without passing through a heat exchanger.

According to one embodiment, the thermal conditioning device comprises a first intermediate chamber, the first intermediate chamber comprising:

An inlet arranged to receive the fluid to be conditioned,

A first output communicating with the first beam and the second heat exchange beam,

A second output communicating with a first output channel.

The first intermediate chamber makes it possible to selectively orient the fluid to be conditioned between several passageways inside the conditioning device.

According to one embodiment, the thermal conditioning device comprises a second intermediate chamber, the second intermediate chamber comprising:

An entry communicating with the third heat exchange bundle,

An output communicating with a second output channel.

The second intermediate chamber makes it possible to close or open certain passageways for the fluid.

Preferably, the first outlet channel and the second outlet channel are fluidly connected, the two outlet channels forming downstream of a junction a single outlet channel.

Each intermediate chamber opens into an outlet channel, the two outlet channels then being interconnected. The conditioning device thus supplies a single outlet with a fluid whose temperature has been regulated.

The first, second and third heat exchange bundles are in fluid communication. The different sections of the heat exchanger communicate with each other, so that the fluid to be conditioned can borrow one or more exchange sections and thus modulate the efficiency of the heat exchange between the fluid to be conditioned and the heat transfer fluid. . The respective position of the two actuators makes it possible to vary the heat exchange surface offered to the fluid to be conditioned.

According to one embodiment, the heat exchanger has a generally substantially parallelepiped shape.

The heat exchanger is thus compact.

Advantageously, the first, second and third heat exchange bundles are arranged in the same housing of the heat exchanger.

The heat exchanger is thus easy to assemble.

Preferably, the first, second and third heat exchange bundles comprise channels for circulation of the fluid to be conditioned, extending in the same direction.

According to one embodiment, the first and the second heat exchange bundle are arranged opposite in a first direction.

Preferably, the first and third heat exchange bundles are arranged opposite in a second direction, the second direction being perpendicular to the first direction. The different heat exchange bundles are adjacent.

According to one embodiment, the heat exchanger is of the air / water type, the heat transfer fluid being a coolant for the heat engine.

This solution provides good heat exchange efficiency combined with a small footprint of the exchanger.

As a variant, the heat exchanger is of the air / air type.

This solution avoids connections with the engine cooling circuit.

According to one embodiment, the first actuator comprises a movable flap in rotation arranged to allow, according to the first operating mode:

a connection between the inlet of the first intermediate chamber and the first heat exchange bundle, a connection between the second heat exchange beam and the second outlet, a separation between the inlet of the first intermediate chamber and the second exit.

According to one embodiment, the second actuator comprises a mobile shutter in rotation arranged to allow, according to the first operating mode:

a shutter at the outlet of the second intermediate chamber.

In this operating mode, the position of the first and second actuator means that the fluid to be conditioned runs through the first and the second bundle of the exchanger before leaving the conditioning device. The fluid does not pass through the third exchange beam. Thus, the entire exchange surface of the heat exchanger is not used, which makes it possible to obtain this mode qualified as "low efficiency".

According to one embodiment, the first actuator comprises a movable flap in rotation arranged to allow, according to the second operating mode:

a communication between the inlet of the first intermediate chamber and the assembly formed by the first beam and the second heat exchange beam, a separation between the inlet of the first intermediate chamber and the second outlet, a separation between the assembly constituted by the first beam and the second heat exchange beam and the second outlet.

According to one embodiment, the second actuator comprises a movable flap in rotation arranged to allow, according to the second operating mode:

communication between the inlet of the second intermediate chamber and the outlet of the second intermediate chamber.

In this operating mode, the position of the first and second actuator means that the fluid to be conditioned runs through the three heat exchange bundles, that is to say the entire exchanger. In this mode, the capacity of the exchanger is fully used, which makes it possible to obtain this mode qualified as "high efficiency".

According to one embodiment, the first actuator comprises a movable flap in rotation arranged to allow, according to the third operating mode:

a communication between the inlet of the first intermediate chamber and the second outlet, a separation between the inlet of the first intermediate chamber and the assembly constituted by the first beam and the second heat exchange beam, a separation between the assembly constituted by the first beam and the second heat exchange beam and the second outlet.

According to one embodiment, the second actuator comprises a movable flap in rotation arranged to allow, according to the third operating mode:

A shutter at the entrance to the second intermediate chamber.

In this operating mode, the position of the first and second actuator means that the fluid to be conditioned leaves the conditioning device without passing through the heat exchanger. This mode is called "bypass mode".

Advantageously, the closure of the inlet of the second intermediate chamber is obtained by bringing a first face of the flap of the second actuator into contact with the inlet of the second intermediate chamber.

Advantageously, the closure of the outlet of the second intermediate chamber is obtained by bringing a second face of the flap of the second actuator into contact with the outlet of the second intermediate chamber, the second face of the flap being opposite the first face. This type of shutter, called "door shutter", provides excellent sealing.

Preferably, a contact surface between the flap of the second actuator and the inlet of the second intermediate chamber is distant from the peripheral edge of the flap.

More preferably, a contact surface between the flap of the second actuator and the outlet of the second intermediate chamber is distant from the peripheral edge of the flap.

The dimensional dispersions affecting the width and the length of the shutter therefore do not affect the sealing of the shutter. The performance of the product in terms of sealing does not vary with the differential thermal expansions of the parts.

According to one embodiment, the flap of the first actuator comprises two wings extending on either side of the axis of rotation of the flap.

Preferably, the two wings of the flap of the first actuator are coplanar.

Advantageously, the two flaps of the flap are symmetrical with respect to the axis of rotation of the flap. In this case, the flap is naturally balanced, that is to say that the passage of the fluid does not generate a torque, since the forces are the same on both sides of the axis of rotation. The control of the position of the flap is thus facilitated.

Alternatively, the two wings of the flap of the first actuator are planar and extend in non-parallel planes.

This configuration can make it possible to modify the arrangement of the various inputs and outputs of the first intermediate chamber, and thus to influence the size of the device.

According to one embodiment, the flap is obtained by deformation of a metal strip, the deformed zone partially surrounding a radial surface of the rotation shaft.

The shutter is thus obtained in a simple and economical manner, the areas to be machined on the rotation shaft being limited.

According to one embodiment, the flap is welded to the rotation shaft.

The sub-assembly consisting of the shutter and the shaft is thus removable.

According to another embodiment, the flap is inserted in a through slot of the rotation shaft.

According to one embodiment, the first outlet channel extends in a direction forming an angle less than 20 ° with the axis of rotation of the first movable actuator.

The outlet channel therefore has a direction close to that of the axis of rotation of the flap.

According to one embodiment, the direction of passage of the fluid to be conditioned in the first heat exchange beam forms an angle greater than 70 ° with the axis of rotation of the first movable actuator.

The exchanger then extends in a direction close to the perpendicular to the axis of rotation of the first actuator. By having elements extending in directions close to the perpendicular, the use of space is optimized.

Advantageously, in each of the first, second and third operating modes, the flap of the first actuator is opposite a sealing surface of the first intermediate chamber.

Preferably, an axial edge of the flap faces a sealing surface of the first intermediate chamber.

The flap serving to guide the fluid to the different outlets in order to ensure the different operating modes, it is desirable to have a good seal between the flap and the wall of the first intermediate chamber.

According to one embodiment, the sealing surface of the first intermediate chamber is machined.

By machining the sealing surface, it is possible to better control the clearance between the edge of the flap and the wall of the first intermediate chamber, which improves sealing.

Preferably, the distance between the axial edge of the flap and the sealing surface of the first intermediate chamber is between 0.1 mm and 2 mm.

This value of the clearance allows a low level of leakage while allowing to take into account the differential expansions of the different components as a function of temperature variations.

According to one embodiment, the heat exchange surface of the first heat exchange bundle is between 15% and 50% of the heat exchange surface of the third beam. The third heat exchange beam is of a different type from the first and second beam, and has a higher heat exchange efficiency. This heat exchanger section, which is more sensitive to fouling due to the smaller section of the fluid circulation channels to be conditioned, is only used when the maximum heat exchange efficiency is sought. When the “low efficiency” mode is used, the exchanger section most sensitive to fouling is not crossed by the fluid and therefore does not foul. The performance of the packaging device remains stable over time.

Preferably, the thermal conditioning device comprises an electric motor arranged to rotate the two actuators.

The use of an electric motor allows rapid and precise actuation of the actuators.

Preferably, the electric motor rotates the two actuators via a gear train.

The reduction ratio provided by the gear train makes it possible to obtain a high actuation force with a motor of moderate power.

According to one embodiment, the electric motor rotates the two actuators by means of a rod connected to a rod secured to the rotation shaft of the actuators, the connection between the rod and the rod being spaced from the axis of rotation of the rotation shaft.

The electric motor can thus be positioned at a distance from the actuators, which facilitates its positioning in the available space.

According to another embodiment, the thermal conditioning device comprises a pneumatic actuator arranged to drive the two actuators in rotation.

A pneumatic actuator is simple and economical.

According to one embodiment, the fluid to be conditioned comprises exhaust gases from a heat engine.

A preferred application for the thermal conditioning device described is for regulating the temperature of the recirculated exhaust gases. Depending on the engine's operating points, it is useful to be able to apply several different levels of exhaust gas cooling efficiency, in order to obtain an optimized outlet temperature over the entire engine operating range.

According to one embodiment, the inlet of the thermal conditioning device is connected to an outlet of an exhaust gas recirculation valve of a heat engine, the valve being of the high pressure type.

The invention also relates to a process for thermal conditioning of fluid for a combustion engine, comprising at least one step of moving two movable actuators arranged to allow the fluid to pass selectively from an inlet to an outlet of a thermal conditioning device according to au minus three operating modes:

In a first operating mode, allow the fluid to be conditioned to pass from the inlet to the outlet by passing through a first section of a heat exchanger,

In a second operating mode, allow the fluid to be conditioned to pass from the inlet to the outlet through a second section of the heat exchanger, the second section having a heat exchange surface greater than that of the first section,

In a third operating mode, allow the fluid to be conditioned to pass directly from the inlet to the outlet, characterized in that the transition from one operating mode to another operating mode is ensured by simultaneous displacement of the two movable actuators .

The invention will be better understood on reading the figures.

FIGS. 1a, 1b, are general views of a thermal conditioning device according to the invention,

FIGS. 2 and 3 show a partial section view of the thermal conditioning device during an operating phase according to the first mode known as “low efficiency”,

FIGS. 4 and 5 show a partial section view of the packaging device during an operating phase according to the second mode known as “high efficiency”,

FIGS. 6 and 7 show a partial sectional view of the thermal conditioning device during an operating phase according to the third mode called "by-pass",

FIG. 8 schematically illustrates the path of the fluid to be conditioned in each of the modes of use,

FIG. 9 represents an embodiment of the flaps of the thermal conditioning device,

- Figure 10 shows a heat exchanger that can be integrated into the thermal conditioning device.

In order to facilitate the reading of the figures, the various elements are not necessarily shown to scale.

FIGS. 1a, 1b show a thermal conditioning device 50 for a fluid for a combustion engine, comprising:

At least one heat exchanger 7,

Two mobile actuators 2a, 2b arranged to allow the fluid to pass selectively from an inlet 1 to an outlet 15 of the thermal conditioning device 50 according to at least three operating modes:

In a first operating mode, allow the fluid to be conditioned to pass from the inlet 1 to the outlet 15 by crossing a first section 21 of the heat exchanger 7,

In a second operating mode, allow the fluid to be conditioned to pass from the inlet 1 to the outlet 15 through a second section 25 of the heat exchanger 7, the second section 25 having a heat exchange surface greater than that of the first section 21,

In a third operating mode, allow the fluid to be conditioned to pass directly from the inlet 1 to the outlet 15, characterized in that the passage from one operating mode to another operating mode is ensured by a simultaneous displacement of the two mobile actuators 2a, 2b.

By the term “thermal conditioning” of a fluid, it is meant that the device which will be described makes it possible to subject the fluid passing through it to a heat exchange, in order to modify its temperature. In the example shown, thermal conditioning consists, in nominal operating conditions of the heat engine, in cooling the fluid.

Each operating mode corresponds to a level of efficiency in cooling the fluid passing through the thermal conditioning device. It is thus possible to ensure control of the temperature at which the fluid leaves the thermal conditioning device.

Each actuator 2a, 2b is movable in rotation about an axis of rotation.

More specifically, each actuator 2a, 2b comprises a flap, each flap 17,18 being arranged to selectively direct the passage of the fluid between the inlet 1 and the outlet 15 of the thermal conditioning device 50 by cooperating with a plurality of passage conduits of fluid from the thermal conditioning device 50.

The position of each of the two actuators makes it possible to modify the path of the fluid inside the conditioning device, and thus to modify the efficiency of the heat exchanges.

The path of the fluid in the first operating mode is shown diagrammatically in FIG. 1a by the sign 40. The path of the fluid in the second operating mode is shown diagrammatically in FIG. 1b by the sign 41. The course of the fluid in the third mode of operation is shown diagrammatically in FIG. 1 a by the sign 42.

The two actuators 2a, 2b are linked in rotation.

The movement of the two actuators can thus be controlled by a single control means. The control of the packaging device is thus economical.

In the example described, and as seen in FIG. 9, the two actuators 2a, 2b have a common rotation shaft 16.

A rotation of the mobile actuators 2a, 2b in a first direction of rotation makes it possible to pass from the first mode to the second mode of operation, and an additional rotation of the mobile actuators 2a, 2b in the same direction of rotation makes it possible to pass from the second mode to the third operating mode. In FIGS. 3 and 4, the arrow R ₁₂ illustrates the direction of rotation of the actuators 2a and 2b during the transition from the first to the second operating mode.

In FIGS. 5 and 6, the arrow R ₂₃ illustrates the direction of rotation of the actuators 2a and 2b during the transition from the second to the third mode.

Depending on the position occupied by the two actuators 2a and 2b, the fluid to be conditioned will pass through different portions of the exchanger 7, and will therefore receive different levels of heat exchange.

FIG. 10 details the constitution of the heat exchanger 7.

The heat exchanger 7 here has a generally substantially parallelepiped shape.

The first bundle 22, second bundle 23 and third bundle 24 of heat exchange are arranged in the same casing of the heat exchanger 7.

The first bundle 22, second bundle 23 and third bundle 24 of heat exchange comprise channels for circulation of the fluid to be conditioned, extending in the same direction.

The first beam 22 and the second heat exchange beam 23 are arranged opposite in a first direction. A horizontal rib 34 of the plate 20 marks the separation between the two parts 22 and 23, which are arranged one below the other.

The first beam 22 and the third heat exchange beam 24 are arranged opposite in a second direction, the second direction being perpendicular to the first direction. A rib 35 of the plate 20 forms a separation between the part 24 and the part 22. This marked rib also forms a separation between the part 24 and the part 23.

The face of the parallelepiped located on the side opposite to the plate 20 is closed by a bottom 26. There is a clearance between the end of the exchange bundles 22, 23, 24 and the bottom 26. Thus, the first 22, second 23 and third 24 heat exchange bundle are in fluid communication.

According to the example illustrated, the heat exchanger 7 is of the air / water type, the heat transfer fluid being the coolant of the heat engine. The exchanger 7 comprises an inlet pipe for the admission of the heat transfer fluid into the heat exchange bundles 22, 23, 24, and an outlet pipe for discharging the heat transfer fluid after the circulation thereof in the bundles exchange 22,23, 24. The inlet and outlet pipes have not been shown in the figures.

FIG. 3 illustrates the path of the fluid in the first operating mode.

The movable actuators 2a, 2b are arranged so that, in the first operating mode, the fluid to be conditioned successively passes through a first heat exchange bundle 22 and a second heat exchange bundle 23 of the heat exchanger 7, l ' input of the first beam 22 and the output of the second beam 23 then being placed side by side. The arrow F ₂ in FIG. 3 diagrams the path of the fluid in the bundle 22. The arrow F ₃ in the same figure diagrams the path of the fluid in the exchange beam 23.

This first operating mode corresponds to a first level of heat exchange. This operating mode is called "low efficiency" heat exchange. In this mode, only part of the heat exchanger 7 is traversed by the fluid. The elements traversed by the fluid are the elements 22 and 23, visible in FIG. 10. The exchange section used is thus designated in FIG. 10 by the sign 21, which designates the assembly constituted by the exchange bundles 22 and 23. The fluid enters through the lower part of the plate 20 and exits through the upper part of the plate 20. The fluid carries out a U-shaped path. The direction of the path in the beam 23 is the opposite direction of the path in the bundle 22, the fluid changing direction of circulation at the level of the space situated between the end of the exchange bundles and the bottom 26 of the exchanger 7.

The element 24 is not itself traversed by the fluid.

FIG. 5 illustrates the path of the fluid in the second operating mode.

The movable actuators 2a, 2b are arranged so that, in the second operating mode, the fluid to be conditioned jointly crosses the first beam 22 and the second heat exchange beam 23, and then crosses a third heat exchange beam 24. The arrows F ′ ₂ in FIG. 5 diagrammatically show the path of the fluid in the bundles 22 and 23. The arrows F ′ ₃ in FIG. 6 diagrammatically show the path of the fluid in the exchange bundle 24.

This second operating mode corresponds to a second level of heat exchange. This operating mode is called "high efficiency" heat exchange. In this mode, the fluid traverses the entire heat exchanger so as to maximize the heat exchange between the fluid to be conditioned and the heat transfer fluid. The fluid to be conditioned enters the two bundles 22 and 23, crosses them both with the same direction of travel, then crosses the bundle 24. In total, the exchange section used is thus designated in FIG. 10 by the sign 25, which groups the exchange beams 22, 23 and 24. The direction of travel in the beam 24 is the opposite direction of the travel in the beams 22 and 23, the fluid changing direction of circulation at the level of the space located between the end of the exchange bundles and the bottom 26 of the exchanger 7.

FIG. 7 illustrates the path of the fluid in the third operating mode.

The movable actuators are arranged so that, in the third operating mode, the fluid to be conditioned passes directly from the inlet 1 to the outlet 15. The arrow F _{2 shows} diagrammatically the path of the fluid in the third operating mode.

In this mode, called "bypass", the fluid passes through the conditioning device without passing through the heat exchanger.

The manner of obtaining the various circuits for circulation of the fluid inside the exchanger 7 will now be detailed.

As shown in particular in FIG. 3, the thermal conditioning device 50 comprises a first intermediate chamber 3, the first intermediate chamber 3 comprising:

An inlet arranged to receive the fluid to be conditioned,

A first outlet 4 communicating with the first beam 22 and the second heat exchange beam 23,

A second outlet 6 communicating with a first outlet channel 11.

The first intermediate chamber makes it possible to selectively orient the fluid to be conditioned between several passageways inside the conditioning device.

As shown in particular in FIG. 4, the thermal conditioning device 50 comprises a second intermediate chamber 8, the second intermediate chamber 8 comprising:

An input 9 communicating with the third heat exchange bundle 24,

An output 10 communicating with a second output channel 12.

The second intermediate chamber makes it possible to close or open certain passageways for the fluid.

As shown in particular in FIG. 2, the first outlet channel 11 and the second outlet channel 12 are fluidly connected, the two outlet channels 11, 12 forming downstream of a junction 13 a single outlet channel 14.

The outlet channel 14 extends to the outlet 15. The fluid conditioning device thus supplies the member using the fluid whose temperature has been regulated.

The first mode of operation will be detailed below.

As illustrated in FIG. 3, the first actuator 2a comprises a flap 17 movable in rotation arranged to allow, according to the first operating mode:

a connection between the inlet 1a of the first intermediate chamber 3 and the first heat exchange bundle 22, a connection between the second heat exchange beam 23 and the second outlet 6, a separation between the inlet the of the first intermediate chamber 3 and the second outlet 6.

By separation, it is meant that the fluid cannot pass from the inlet la to the second outlet, except for a negligible leak rate.

As illustrated in FIG. 4, the second actuator 2b comprises a flap 18 movable in rotation arranged to allow, according to the first operating mode:

a closure of the outlet 10 of the second intermediate chamber 8.

By closing the outlet, it is meant that the flow of fluid leaving the second intermediate chamber is zero, with the exception of a negligible leakage flow.

As can be seen in FIG. 9, the flap 17 of the first actuator 2a comprises two wings 19a, 19b extending on either side of the axis of rotation 16 of the flap 17. The two wings 19a, 19b of the flap 17 of the first actuator 2a are coplanar. More specifically, the two wings 19a, 19b of the flap 17 are symmetrical with respect to the axis of rotation of the flap 17. The flap 17 is obtained by deformation of a metal strip, the deformed zone partially surrounding a radial surface of the rotation shaft 16. Next, the flap 17 is welded to the rotation shaft 16.

The flap 17 and the flap 18 are offset axially along the rotation shaft 16. The flap 17 and the flap 18 are angularly offset, in other words the two flaps are not in the same plane.

In FIG. 3, the arrow Fi diagrams the path of the fluid between the inlet 1 of the thermal conditioning device and the inlet 1a of the first intermediate chamber 3.

In this position of the flaps 17 and 18, the fluid to be conditioned is admitted into the lower part of the exchanger 7. The flap 17, in a horizontal position in FIG. 3, separates the bundle 22 from the bundle 23 and thus prevents the fluid from join the upper half of the exchanger 7. The second intermediate chamber 8 being closed at its outlet, the fluid having passed through part 22 of the exchanger cannot circulate in the bundle 24 of the exchanger. On the other hand, the fluid can circulate in the upper part of the exchanger and join the intermediate chamber 3, as shown schematically by the arrow F ₃ . The position of the flap 17 allows the fluid leaving the bundle 22 of the exchanger to reach the outlet 6, then the outlet channel 11, as far as the outlet 15. This path between the first intermediate chamber 3 and the outlet 15 is shown diagrammatically by arrows F ₄ and F ₅ . Only the exchange bundles 22 and 23 are here traversed by the fluid to be conditioned. The entire exchange surface of the heat exchanger 7 is not used, this mode is therefore qualified as "low efficiency".

The second operating mode will now be detailed.

As illustrated in FIG. 5, the first actuator 2a comprises a flap 17 movable in rotation arranged to allow, according to the second operating mode:

a connection between the inlet 1a of the first intermediate chamber 3 and of the assembly formed by the first beam 22 and the second heat exchange beam 23, a separation between the inlet 1a of the first intermediate chamber 3 and the second outlet 6, a separation between the assembly 21 constituted by the first bundle 22 and the second heat exchange bundle 23 and the second outlet 6.

As illustrated in FIG. 6, the second actuator 2b comprises a flap 18 movable in rotation arranged to allow, according to the second operating mode:

a connection between the inlet 9 of the second intermediate chamber 8 and the outlet 10 of the second intermediate chamber 8.

In this operating mode, the two exchange bundles 22 and 23 are located on the same side of the flap 17. After transfer between the inlet 1 and the first intermediate chamber 3, shown diagrammatically by the arrow F ′ _n, the fluid can be distributed between the two beams 22 and 23, which are both traversed. After passing through the two beams 22 and 23, the fluid passes through the exchange beam 24, since the flap 18 is in a position where the second intermediate chamber 8 is open. Indeed, the flap 18 is in a position where neither the inlet nor the outlet of the second intermediate chamber 8 is closed. The arrow F ' ₄ diagrams the passage of the fluid between the inlet and the outlet of the second intermediate chamber 8. The arrow F' ₅ diagrams the transfer to the outlet 15. The fluid to be conditioned traverses the three bundles 22, 23 , 24 heat exchange, that is to say the entire exchanger. In this mode, the capacity of the exchanger is fully used.

The heat exchange surface of the first heat exchange bundle 22 is between 15% and 50% of the heat exchange surface of the third beam. In other words, the third heat exchange beam has a heat exchange surface greater than that of the first and second beams, and therefore has a higher heat exchange efficiency. This upper exchange surface is obtained by channels of finer section than those of the first and second bundles.

Thus, not only in this mode the whole of the exchange surface is used, but the exchange efficiency of the added beam is higher, which makes it possible to obtain this mode qualified as "high efficiency".

We will now detail the third mode of operation.

As illustrated in FIG. 7, the first actuator 2a comprises a flap 17 movable in rotation arranged to allow, according to the third operating mode:

a communication between the input la of the first intermediate chamber 3 and the second output 6, a separation between the input la of the first intermediate chamber 3 and the assembly constituted by the first beam 22 and the second beam 23 d heat exchange, a separation between the assembly 21 constituted by the first beam 22 and the second heat exchange beam 23 and the second outlet 6.

As illustrated in FIG. 8, the second actuator 2b comprises a flap 18 movable in rotation arranged to allow, according to the third operating mode:

A closure of the inlet 9 of the second intermediate chamber 8.

As before, the terms “separation” and “obturation” signify a zero flow with the exception of a negligible leakage flow.

In this operating mode, the flap 17 prevents the admitted fluid from joining the exchange bundles 22 and 24. The flap 18 closes the outlet of the exchange beam 24. The flap 17 allows the direct communication of the inlet with outlet 6. The fluid to be conditioned therefore leaves the packaging device without passing through the heat exchanger. The path of the fluid between the inlet 1 and the outlet 15 is shown diagrammatically by the arrows F _n F ₂ and F ₃ . This mode is called "bypass mode".

We will now detail the management of the watertightness of flaps 17 and 18.

The inlet 9 of the second intermediate chamber 8 is closed by bringing a first face of the flap 18 of the second actuator 2b into contact with the inlet 9 of the second intermediate chamber 8.

Similarly, closing the outlet 10 of the second intermediate chamber 8 is obtained by bringing a second face of the flap 18 of the second actuator 2b into contact with the outlet 10 of the second intermediate chamber 8, the second face of the flap 18 being opposite the first face.

In other words, the flap 18 pivots between two extreme positions, one extreme position corresponding to the closing of the inlet of the intermediate chamber 8 and the other extreme position corresponding to the closing of the outlet of the intermediate chamber 8. This type of flap, called "door flap", provides excellent sealing.

The contact surface between the shutter 18 of the second actuator 2b and the inlet 9 of the second intermediate chamber 8 is distant from the peripheral edge 28 of the shutter 18.

Likewise, the contact surface between the flap 18 of the second actuator 2b and the outlet 10 of the second intermediate chamber 8 is distant from the peripheral edge 28 of the flap 18.

The dimensional dispersions of the shutter, affecting its width or its length, therefore have no influence on the tightness of the shutter. This type of flap, called "door flap", allows a very low level of leakage to be obtained. Consequently, when the conditioning system operates in “low efficiency” mode or in “bypass” mode, there is no parasitic flow of fluid in the exchange beam 24. This beam, which has a channel surface of lower circulation than that of the beams 22 and 23 is naturally more sensitive to fouling. In addition, being located downstream of the beams 22 and 23, it is crossed by already cooled fluid, therefore unlikely to create a natural elimination of accumulated deposits, according to a mechanism similar to pyrolysis. It is therefore particularly advantageous to avoid a parasitic leakage rate, which tends to clog the “high efficiency” exchanger and to degrade its performance.

In each of the first, second and third operating modes, the flap 17 of the first actuator 2a faces a sealing surface 30, 31, 32 of the first intermediate chamber 3.

The axial edge 33 of the flap 17 faces a sealing surface 30, 31, 32 of the first intermediate chamber.

The flap serving to guide the fluid to the different outlets in order to ensure the different operating modes, it is desirable to have a good seal between the flap and the wall of the first intermediate chamber.

The sealing surface 30, 31, 32 of the first intermediate chamber 3 is machined.

The distance between the axial edge 33 of the flap 17 and the sealing surface 30, 31, 32 of the first intermediate chamber 3 is between 0.1 mm and 2 mm.

The first outlet channel 11 extends in a direction forming an angle less than 20 ° with the axis of rotation of the first movable actuator 2a.

The direction of passage of the fluid to be conditioned in the first heat exchange bundle 22 forms an angle greater than 70 ° with the axis of rotation of the first movable actuator 2a.

In other words, the outlet channel 11 has a direction close to that of the axis of rotation of the flap and the circulation of the fluid in the exchanger takes place in a direction close to the perpendicular to this axis of rotation. The use of space is thus optimized and makes it possible to obtain a compact device. Depending on the space available to house the conditioning device, it is possible to adapt the arrangement of the various inlets and outlets on the periphery of the intermediate chamber 3.

The thermal conditioning device 50 comprises an electric motor arranged to drive the two actuators 2a, 2b in rotation.

The electric motor rotates the two actuators 2a, 2b via a gear train.

More specifically, the electric motor rotates the two actuators 2a, 2b by means of a rod connected to a link integral with the rotation shaft 16 of the actuators 2a, 2b, the connection between the rod and the link being distant from the axis of rotation of the rotation shaft 16. The choice of the length of the link as well as the gear ratio of the electric motor makes it possible to adapt the force available according to the size of the flaps and the operating pressure of the fluid conditioning device 50.

In the example described, the fluid to be conditioned comprises exhaust gases from a heat engine.

More specifically, the inlet 1 of the thermal conditioning device 50 is connected to an outlet of an exhaust gas recirculation valve of a heat engine, the valve being of the high pressure type.

The exhaust gas conditioning device 50 thus makes it possible to control the temperature of the recirculated exhaust gases at the intake of the engine. The temperature of the exhaust gases admitted to the thermal conditioning device varies between about 100 ° C and 1050 ° C, and it is useful to be able to apply several different levels of cooling efficiency to the exhaust gases, in order to obtain an outlet temperature optimized for instantaneous engine operating conditions. The electric motor is controlled by the electronic unit controlling all of the motor actuators from information from the various sensors. A single command is necessary, since the two actuators 2a and 2b are linked.

The invention finally applies to a process for thermal conditioning of fluid for a combustion engine, comprising at least one step of moving two movable actuators 2a, 2b arranged to allow the fluid to pass selectively from an inlet 1 to an outlet 15 d 'A thermal conditioning device 50 according to at least three operating modes:

In a first operating mode, allow the fluid to be conditioned to pass from the inlet 1 to the outlet 15 by passing through a first section 21 of a heat exchanger 7,

In a second operating mode, allow the fluid to be conditioned to pass from the inlet 1 to the outlet 15 through a second section 25 of the heat exchanger 7, the second section 25 having a heat exchange surface greater than that of the first section 21,

In a third operating mode, allow the fluid to be conditioned to pass directly from the inlet 1 to the outlet 15, characterized in that the passage from one operating mode to another operating mode is ensured by a simultaneous displacement of the two mobile actuators 2a, 2b.

According to embodiments not shown, the fluid thermal conditioning device can also include one or more of the characteristics below, considered individually or combined with each other:

The two actuators 2a, 2b can be linked in rotation by two toothed wheels meshing with each other directly or indirectly.

It is thus possible to offset one actuator relative to the other, which can facilitate the integration of the actuators.

The two wings 19a, 19b of the flap 17 of the first actuator 2a can extend in non-parallel planes.

This configuration can make it possible to modify the arrangement of the various inputs and outputs of the first intermediate chamber, and thus to influence the size of the device.

The shutter 17 and the shutter 18 can extend in the same plane.

The flap 17 can be inserted into a through slot of the rotation shaft 16.

- The heat exchanger 7 can be of the air / air type.

The electric motor can rotate the two actuators 2a, 2b by means of a toothed wheel secured to the rotation shaft 16 of the actuators 2a, 2b. In this case, the axis of rotation of the electric motor can be parallel to the rotation shaft 16 of the actuators 2a, 2b.

The thermal conditioning device may include a pneumatic actuator arranged to rotate the two actuators 2a, 2b. In this case, the pneumatic actuator has three positions of stable equilibrium, each position corresponding to an operating mode.

Of course, the invention is in no way limited to the embodiments described and illustrated, which have been given only by way of examples.

Claims (5)

1. A thermal conditioning device (50) for a fluid for a combustion engine, comprising: At least one heat exchanger (7), Two movable actuators (2a, 2b) arranged to allow the fluid to pass selectively from one 5 inlet (1) to an outlet (15) of the thermal conditioning device (50) according to at least three operating modes: In a first operating mode, allow the fluid to be conditioned to pass from the inlet (1) to the outlet (15) by passing through a first section (21) of the heat exchanger (7), 10 - In a second operating mode, allow the fluid to be conditioned to pass from the inlet (1) to the outlet (15) through a second section (25) of the heat exchanger (7), the second section (25 ) having a heat exchange surface greater than that of the first section (21), In a third operating mode, allow the fluid to be conditioned to pass 15 directly from the input (1) to the output (15), characterized in that the transition from one operating mode to another operating mode is ensured by a simultaneous movement of the two mobile actuators (2a, 2b). 2. A thermal conditioning device (50) according to the preceding claim, wherein the two actuators (2a, 2b) have a common rotation shaft (16). 20 3. A thermal conditioning device (50) according to one of the preceding claims, in which the movable actuators (2a, 2b) are arranged so that, in the first operating mode, the fluid to be conditioned successively passes through a first beam (22 ) heat exchange and a second heat exchange bundle (23) of the heat exchanger (7), an inlet of the first beam (22) and an outlet of the second beam (23) being 25 then joined together. 4. A thermal conditioning device (50) according to the preceding claim, in which the movable actuators (2a, 2b) are arranged so that, in the second operating mode, the fluid to be conditioned jointly crosses the first beam (22) and the second heat exchange bundle (23), and then pass through a third heat exchange bundle (24). 5. A thermal conditioning device (50) according to one of claims 3 or 4, in which the thermal conditioning device (50) comprises a first intermediate chamber (3), the first intermediate chamber (3) comprising: An inlet (la) arranged to receive the fluid to be conditioned, A first outlet (4) communicating with the first beam (22) and the second heat exchange beam (23), A second outlet (6) communicating with a first outlet channel (11). 6. A thermal conditioning device (50) according to claim 5, in which the thermal conditioning device (50) comprises a second intermediate chamber (8), the second intermediate chamber (8) comprising: An input (9) communicating with the third heat exchange bundle (24), An output (10) communicating with a second output channel (12). 7. A thermal conditioning device (50) according to claim 6, in which the first actuator (2a) comprises a flap (17) movable in rotation arranged to allow, according to the first operating mode: a connection between the inlet (la) of the first intermediate chamber (3) and the first heat exchange bundle (22), a connection between the second heat exchange bundle (22) and the second outlet (6), a separation between the inlet (la) of the first intermediate chamber (3) and the second outlet (6). 8. A thermal conditioning device (50) according to one of claims 6 or 7, in which the second actuator (2b) comprises a flap (18) movable in rotation arranged to allow, according to the first operating mode: a closure of the outlet (10) of the second intermediate chamber (8). 9. A thermal conditioning device (50) according to one of claims 6 to 8, in which the first actuator (2a) comprises a flap (17) movable in rotation arranged to allow, according to the second operating mode: placing the inlet (la) of the first intermediate chamber (3) and the assembly constituted by the first bundle (22) and the second heat exchange bundle (23) in communication, a separation between the inlet (la) of the first intermediate chamber (3) and the second outlet (6), a separation between the assembly constituted by the first beam (22) and the second heat exchange beam (23) and the second outlet (6 ). 10. A thermal conditioning device (50) according to one of claims 6 to 9, in which the second actuator (2b) comprises a flap (18) movable in rotation arranged to allow, according to the second operating mode: placing the inlet (9) of the second intermediate chamber (8) and the outlet (10) of the second intermediate chamber (8) in communication. 11. A thermal conditioning device (50) according to one of claims 6 to 10, in which the first actuator (2a) comprises a flap (17) movable in rotation arranged to allow, according to the third operating mode: a communication between the inlet (la) of the first intermediate chamber (3) and the second outlet (6), a separation between the inlet (la) of the first intermediate chamber (3) and the assembly constituted by the first beam (22) and the second heat exchange beam (23), a separation between the assembly constituted by the first beam (22) and the second heat exchange beam (23) and the second outlet (6) . 12. A thermal conditioning device (50) according to one of claims 6 to 11, in which the second actuator (2b) comprises a flap (18) movable in rotation arranged to allow, according to the third operating mode: A closure of the inlet (9) of the second intermediate chamber (8). 13. A thermal conditioning device (50) according to one of the preceding claims, in which the inlet (1) of the thermal conditioning device (50) is connected to an outlet of an exhaust gas recirculation valve d 'A heat engine, the valve being of the high pressure type. 14. A method of thermal conditioning of fluid for a combustion engine, comprising at least one step of moving two movable actuators (2a, 2b) arranged to allow the fluid to selectively pass from an inlet (1) to an outlet (15) of a thermal conditioning device (50) according to at least three operating modes: In a first operating mode, allow the fluid to be conditioned to pass from the inlet (1) to the outlet (15) by passing through a first section (21) of a heat exchanger (7), In a second operating mode, allow the fluid to be conditioned to pass from the inlet (1) to the outlet (15) through a second section (25) of the heat exchanger (7), the second section (25) having a heat exchange surface greater than that of the first section (21), In a third operating mode, let the fluid to be conditioned pass directly from the inlet (1) to the outlet (15), 5 characterized in that the transition from one operating mode to another operating mode is ensured by simultaneous movement of the two movable actuators (2a, 2b). 1/5