Engine system

Abstract

An engine system (10) includes an internal combustion engine (12) having two sets of cylinders (16, 22), a turbocharger (28), two exhaust conduits (30, 32) providing fluid communication between the turbocharger and exhaust ports of the two sets of cylinders, and an exhaust gas recirculation system (34) including a recirculation valve (38). Two proportional exhaust valves (42, 46) are adapted to control exhaust flow in the two exhaust conduits. In a first configuration, the two exhaust valves are open and the recirculation valve is closed. In a second configuration, a first of the two exhaust valves is in a closed position. The engine system includes an actuator (50) and a kinematic chain (60-72) for operating at least two of the three valves. A first movement of the actuator operates each of the two valves, while a second movement of the actuator operates only one of the two valves.

Description

Technical Field

[0001] The present disclosure generally relates to vehicles powered by internal combustion engines. In certain aspects, the present disclosure relates to an engine system.

[0002] The present disclosure may be applicable to heavy vehicles, such as trucks, buses, and construction equipment.Although the present disclosure will be described with respect to a particular vehicle, the present disclosure is not limited to any particular vehicle. Background Art

[0003] In the field of heavy vehicles powered by internal combustion engines, such as trucks, it is known to provide an engine system comprising an internal combustion engine having two groups of cylinders, each group of cylinders having a separate exhaust gas collector in fluid communication with a turbocharger. Such an engine system typically comprises two proportional exhaust valves, each proportional exhaust valve being operable to control exhaust gas flow from the exhaust gas collector of one group of cylinders to the turbocharger.

[0004] When the vehicle is operating under normal conditions, the exhaust gas flow produced by each group of cylinders is directed from the exhaust gas collector of the corresponding group of cylinders to the turbocharger.

[0005] It is also known to use exhaust gas recirculation technology to reduce the nitrogen oxide emissions of the engine. This technology consists in redirecting the exhaust gas flow from a first exhaust gas collector to the air intake of the internal combustion engine, while allowing the exhaust gas flow from a second exhaust gas collector to flow to the turbocharger. Therefore, the engine system comprises a recirculation duct providing fluid communication between the first exhaust gas collector and the air intake of the internal combustion engine and a proportional recirculation valve for controlling the exhaust gas flow through the recirculation duct, the proportional recirculation valve being opened when the exhaust gas recirculation technology is used and closed otherwise.

[0006] It is also known to close the two proportional exhaust valves in certain operating conditions (for example, for braking the engine) in order to prevent exhaust gas flow from the two exhaust gas collectors to the turbocharger.

[0007] Therefore, such a typical engine system includes three actuators, each actuator operating two proportional exhaust valves and one of the proportional recirculation valves. Due to the presence of multiple actuators, these engine systems are expensive to manufacture, heavy and prone to failure.

[0008] It is with regard to these drawbacks that the present invention more particularly aims to remedy by proposing an engine system that is less expensive to manufacture, more compact and more reliable. Summary of the invention

[0009] The present invention is directed to improving the compactness of an engine system by reducing the number of actuators required to operate the engine system valves.

[0010] According to one aspect of the present disclosure, the present invention relates to an engine system, the engine system comprising: - an internal combustion engine comprising an air intake, a first group of cylinders comprising at least a first cylinder and a first exhaust gas collector, and a second group of cylinders comprising at least a second cylinder and a second exhaust gas collector, - Turbocharger, - a first exhaust gas duct providing fluid communication between the first exhaust gas collector and the turbocharger, - a second exhaust gas duct providing fluid communication between the second exhaust gas collector and the turbocharger, - an exhaust gas recirculation system, the exhaust gas recirculation system comprising: a recirculation duct providing fluid communication between the first exhaust gas collector and the air intake of the internal combustion engine, and a proportional recirculation valve adapted to control the exhaust gas flow in the recirculation duct and operable between an open position, in which the exhaust gas flow is allowed, and a closed position, in which the exhaust gas flow is prevented, the closed position being a rest position of the proportional recirculation valve, - a first proportional exhaust valve adapted to control the exhaust gas flow in the first exhaust duct and operable between an open position in which the exhaust gas flow is allowed and a closed position in which the exhaust gas flow is blocked, the open position being a rest position of the first proportional exhaust valve, and - a second proportional exhaust valve adapted to control the exhaust gas flow in the second exhaust gas duct and operable between an open position, in which the exhaust gas flow is allowed, and a closed position, in which the exhaust gas flow is blocked, the open position being a rest position of the second proportional exhaust valve.

[0011] The engine system is switchable between a first configuration in which the first and second proportional exhaust valves are in their open positions and the proportional recirculation valve is in its closed position, and a second configuration in which the first proportional exhaust valve is in its closed position.

[0012] The engine system includes an actuator and a kinematic chain configured to operate at least two of the proportional recirculation valve, the first proportional exhaust valve, and the second proportional exhaust valve. When the engine system is in the first configuration, an output member of the actuator is in a neutral position. A first movement of the output member from its neutral position in a first direction operates each of the two valves from its rest position to another position, and a second movement of the output member from its neutral position in a second direction opposite to the first direction operates only one of the two valves from its rest position to another position.

[0013] Therefore, the technical effects of the invention include that only one actuator is required to operate two of the three valves of the engine system, and to operate both valves or only one valve, depending on the direction of movement of the output member of the actuator. Due to the invention, the engine system is cheaper to manufacture, more compact and more reliable than existing engine systems.

[0014] In some examples, the output member of the actuator is configured to operate a first proportional exhaust valve and a second proportional exhaust valve. The first movement of the output member closes the first proportional exhaust valve and the second proportional exhaust valve, and the second movement of the output member closes the first proportional exhaust valve and does not operate the second proportional exhaust valve. Thus, the two proportional exhaust valves are controlled by the same actuator, which enables optimized control of the proportional exhaust valves while maintaining independent control of the proportional recirculation valve, which is more precise.

[0015] In some examples, the first movement of the output member closes the first proportional exhaust valve and the second proportional exhaust valve at the same speed. Therefore, the exhaust flow in the first exhaust conduit is the same as the exhaust flow in the second exhaust conduit, which improves the performance of the engine system.

[0016] In some examples, each of the first proportional exhaust valve and the second proportional exhaust valve is an asymmetric flap valve including a flap and a shaft. Rotation of the shaft causes the flap to open or close, and the rotation of the shaft is driven by the output member of the actuator. Due to the use of an asymmetric flap valve, when the actuator does not operate the proportional exhaust valve, the proportional exhaust valve naturally returns to the open position, thereby improving the operation of the engine system.

[0017] In some examples, the kinematic chain includes: a first transmission device, the first transmission device is connected to the output member of the actuator and the first proportional exhaust valve; a second transmission device, the second transmission device is connected to the first transmission device and the second proportional exhaust valve; and a first asymmetric linkage device, the first asymmetric linkage device is configured to transfer the first movement of the output member from the first transmission device to the second transmission device, and not transfer the second movement of the output member from the first transmission device to the second transmission device. Therefore, due to the asymmetric linkage device, it is possible to select whether the actuator operates the second proportional exhaust valve only by selecting the movement direction of the output member of the actuator.

[0018] In some examples, the first asymmetric linkage comprises a protrusion mounted on the first transmission means and an abutment surface located on the second transmission means. During the first movement of the output member, the protrusion abuts the abutment surface, and during the second movement of the output member, the protrusion does not contact the abutment surface. Therefore, the asymmetric linkage is particularly easy to implement and is therefore cost-effective and reliable.

[0019] In some examples, the output member of the actuator is configured to operate the first proportional exhaust valve and the proportional recirculation valve. The first movement of the output member closes the first proportional exhaust valve and opens the proportional recirculation valve, and the second movement of the output member closes the first proportional exhaust valve and does not operate the proportional recirculation valve. Thus, when exhaust gas recirculation is required, both valves are operated by the same actuator. This facilitates and reliably implements exhaust gas recirculation technology.

[0020] In some examples, the kinematic chain includes: a first transmission device, the first transmission device is connected to the output member of the actuator and the first proportional exhaust valve; a third transmission device, the third transmission device is connected to the first transmission device and the proportional recirculation valve; and a second asymmetric linkage device, the second asymmetric linkage device is configured to transfer the first movement of the output member from the first transmission device to the third transmission device, and not transfer the second movement of the output member from the first transmission device to the third transmission device. Therefore, due to the asymmetric linkage device, it is possible to select whether the actuator operates the proportional recirculation valve only by selecting the movement direction of the output member of the actuator.

[0021] In some examples, the proportional recirculation valve is a poppet valve, and the second asymmetric linkage includes a cam mounted on the first transmission and a roller attached to the third transmission. Due to the use of a poppet valve and the use of a cam system, controlling the proportional recirculation valve when gas recirculation is required is particularly simple, effective and reliable.

[0022] In some examples, the output member of the actuator is configured to operate the first proportional exhaust valve, the second proportional exhaust valve, and the proportional recirculation valve. The first movement of the output member closes the first proportional exhaust valve and the second proportional exhaust valve and does not operate the proportional recirculation valve, and the second movement of the output member closes the first proportional exhaust valve, opens the proportional recirculation valve, and does not operate the second proportional exhaust valve. Therefore, because the three valves are operated by the same actuator, the engine system is even cheaper to manufacture and more compact than existing engine systems.

[0023] In some examples, the kinematic chain includes: a first transmission device, the first transmission device is connected to the output member of the actuator and the first proportional exhaust valve; a second transmission device, the second transmission device is connected to the first transmission device and the second proportional exhaust valve; a third transmission device, the third transmission device is connected to the first transmission device and the proportional recirculation valve; a first asymmetric linkage device, the first asymmetric linkage device is configured to transfer the first movement of the output member from the first transmission device to the second transmission device, and not to transfer the second movement of the output member from the first transmission device to the second transmission device; and a second asymmetric linkage device, the second asymmetric linkage device is configured to transfer the second movement of the output member from the first transmission device to the third transmission device, and not to transfer the first movement of the output member from the first transmission device to the third transmission device. Therefore, due to the two asymmetric linkage devices, it is possible to select whether the actuator operates the second proportional exhaust valve and the proportional recirculation valve only by selecting the movement direction of the output member of the actuator.

[0024] Additional features and advantages are disclosed in the following description, claims and drawings, and in part will be apparent to those skilled in the art or recognized by practicing the present disclosure as described herein. This article also discloses a control unit, a computer-readable medium and a computer program product associated with the technical benefits and corresponding advantages discussed above. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] With reference to the accompanying drawings, the following is a more detailed description of aspects of the disclosure cited as examples.

[0026] Figure 1is a schematic diagram of an exemplary engine system according to the present invention.

[0027] Figure 2 Is in the first configuration Figure 1 A perspective view of a portion of an engine system.

[0028] Figure 3 is similar to Figure 2 In the second configuration Figure 1 A perspective view of a portion of an engine system.

[0029] Figure 4 is similar to Figure 2 and Figure 3 In the third configuration Figure 1 A perspective view of a portion of an engine system. DETAILED DESCRIPTION

[0030] The various aspects set forth below represent the necessary information to enable those skilled in the art to practice the present disclosure.

[0031] exist Figure 1 An exemplary engine system 10 can be seen in FIG. The engine system 10 is intended to be installed in a vehicle to propel the vehicle. Such a vehicle may be, for example, a heavy vehicle such as a truck, a bus or construction equipment.

[0032] The engine system 10 includes an internal combustion engine 12 that is propelled by the combustion of a fuel (such as diesel, for example). The internal combustion engine 12 includes an air intake 14, a first group of cylinders 16 including at least a first cylinder 18 and a first exhaust gas collector 20, and a second group of cylinders 22 including at least a second cylinder 24 and a second exhaust gas collector 26. In the example described, the first group of cylinders and the second group of cylinders each include three cylinders 18, 24. As a variant (not shown), each group of cylinders includes a different number of cylinders, for example, four cylinders.

[0033] The engine system 10 includes an intake conduit 80 that provides fluid communication between the intake port 14 and the first and second groups of cylinders 16 and 22. The intake port 14 provides oxidant (eg, air) to the first and second groups of cylinders for fuel combustion.

[0034] The engine system 10 includes a fuel injection system (not shown) that provides fuel to the first group of cylinders 16 and the second group of cylinders 22 .

[0035] The engine system 10 includes a turbocharger 28 , a first exhaust conduit 30 providing fluid communication between the first exhaust collector 20 and the turbocharger, and a second exhaust conduit 32 providing fluid communication between the second exhaust collector 26 and the turbocharger.

[0036] Advantageously, the engine system 10 includes an exhaust aftertreatment system 82 in fluid communication at its intake with the output of the turbocharger 28 and in fluid communication at its output with an exhaust system (not shown). The exhaust aftertreatment system 82 is configured to clean the exhaust gas produced by the internal combustion engine 12 by filtering certain pollutants and converting other pollutants into non-polluting gases via chemical reactions.

[0037] Advantageously, the engine system 10 includes a charge air cooler 84. An output of the charge air cooler 84 is in fluid communication with the air intake 14 of the internal combustion engine 12. The charge air cooler 84 provides the internal combustion engine 12 with cooled air.

[0038] Advantageously, the engine system 10 includes a compressor 86 that provides compressed air to the charge air cooler 84. In the depicted example, the compressor 86 is driven by the turbocharger 28.

[0039] Advantageously, engine system 10 includes an air filter 88 in fluid communication with the air intake of compressor 86 to filter air provided to compressor 86 and charge air cooler 84 .

[0040] The engine system 10 comprises an exhaust gas recirculation system 34 allowing the exhaust gas of the first group of cylinders 16 to be recirculated to the intake 14 of the internal combustion engine 12. The exhaust gas recirculation system 34 comprises a recirculation duct 36 and a proportional recirculation valve 38, ie a continuously operable valve.

[0041] The recirculation conduit 36 ​​provides fluid communication between the first exhaust gas collector 20 of the first group of cylinders 16 and the air intake 14 of the internal combustion engine 12 .

[0042] The proportional recirculation valve 38 is adapted to control the exhaust gas flow 40 in the recirculation conduit 36. The proportional recirculation valve 38 is operable between an open position, in which the exhaust gas flow 40 is allowed, and a closed position, in which the exhaust gas flow 40 is blocked, the closed position being a rest position of the proportional recirculation valve 38. Figures 2 to 4 In FIG. 8 , the proportional recirculation valve 38 is shown in phantom because it is hidden by the first exhaust gas collector 20 and the recirculation duct 36 .

[0043] Thus, the air intake 14 of the internal combustion engine 12 is provided with air by the charge air cooler 84 and with exhaust gas by the exhaust gas recirculation system 34 when the proportional recirculation valve 38 is in its open position.

[0044] In the example described, the proportional recirculation valve 38 is a poppet valve, i.e. a linearly activated valve. Preferably, the engine system 10 comprises a return spring, not represented, which exerts a force on the proportional recirculation valve 38 tending to close the proportional recirculation valve. As a variant, the proportional recirculation valve 38 is another type of valve, such as a flap valve, for example.

[0045] The engine system 10 includes a first proportional exhaust valve 42 (i.e., a continuously operable valve) adapted to control exhaust gas flow 44 in the first exhaust conduit 30 and operable between an open position, in which exhaust gas flow is permitted, and a closed position, in which exhaust gas flow is prevented, the open position being a rest position of the first proportional exhaust valve.

[0046] The engine system 10 includes a second proportional exhaust valve 46 (i.e., a continuously operable valve) adapted to control exhaust gas flow 48 in the second exhaust conduit 32 and operable between an open position, in which exhaust gas flow is permitted, and a closed position, in which exhaust gas flow is prevented, the open position being a rest position of the second proportional exhaust valve.

[0047] In the example described, the first proportional exhaust valve 42 is an asymmetric flap valve comprising a flap 52 and a shaft 56 to which the flap is fixed. Rotation of the shaft 56 results in opening or closing of the flap 52. Advantageously, the shaft 56 is eccentric relative to the flap 52. Similarly, the second proportional exhaust valve 46 is an asymmetric flap valve comprising a flap 54 and a shaft 58 to which the flap is fixed. Rotation of the shaft 58 results in opening or closing of the flap 54. Advantageously, the shaft 58 is eccentric relative to the flap 54.

[0048] As a variation, the first proportional exhaust valve 42 and the second proportional exhaust valve 46 are another type of valve, such as poppet valves, for example.

[0049] Practically speaking, the open position of the first and second proportional exhaust valves 42, 46 is the rest position of the proportional exhaust valves due to the non-centering of the shafts 56, 58 relative to the flaps 52, 54 and due to the action of the exhaust gas from the exhaust collectors 20, 26, which exerts pressure on the flaps 52, 54 causing the flaps to open. Optionally, the first and second proportional exhaust valves 42, 46 include return springs to force the flaps 52, 54 open. With such springs, the proportional exhaust valves 42, 46 can be symmetrical flap valves in which the shafts 56, 58 are centered relative to the flaps 52, 54.

[0050] The engine system may be switched between a plurality of configurations by operating the proportional recirculation valve 38, the first proportional exhaust valve 42, and the second proportional exhaust valve 46. Three exemplary configurations are described below.

[0051] In the normal operating configuration of the engine system 10, the first proportional exhaust valve 42 and the second proportional exhaust valve 46 are in their open positions, and the proportional recirculation valve 38 is in its closed position. In other words, in the normal operating position, exhaust gas flow 40 is blocked while exhaust gas flows 44 and 48 are allowed, so that the exhaust gas generated by the internal combustion engine 12 is completely redirected to the turbocharger 28. Normal operating conditions are Figure 2 Indicated in.

[0052] In the braking configuration of the engine system 10, the first proportional exhaust valve 42 and the second proportional exhaust valve 46 are in their closed positions and the proportional recirculation valve 38 is in its closed position. In other words, in the braking configuration, the exhaust gas flow 40 is blocked and the exhaust gas flows 44 and 48 are also blocked, so that the exhaust gas generated by the internal combustion engine 12 is blocked from leaving the internal combustion engine, thereby increasing the pressure in the internal combustion engine. For example, the pressure inside the internal combustion engine may rise to 6 bar. The increase in pressure causes a braking torque, thereby reducing the rotational speed of the internal combustion engine 12 and braking a vehicle propelled by the engine system. Therefore, the braking configuration can be used to brake the vehicle. The braking configuration in Figure 3 Indicated in.

[0053] In the recirculation configuration of the engine system 10, the first proportional exhaust valve 42 is in its closed position, the second proportional exhaust valve 46 is in its open position, and the proportional recirculation valve 38 is in its open position. In other words, in the recirculation configuration, exhaust gas flow 40 is permitted, exhaust gas flow 44 is blocked, and exhaust gas flow 48 is permitted. Thus, in this configuration, the first exhaust gas collector 20 is in fluid communication with the intake port 14, and the second exhaust gas collector 26 is in fluid communication with the turbocharger 28. Thus, the recirculation configuration may be used when recirculation of exhaust gas is desired, for example, to reduce nitrogen oxide emissions from the internal combustion engine 12. The recirculation configuration is Figure 4 Indicated in.

[0054] To operate the first and second proportional exhaust valves 42 and 46 and the proportional recirculation valve 38, the engine system 10 includes a single actuator 50 that includes an output member 51. The output member 51 can be operated in two different movement directions by the actuator 50. Therefore, the actuator 50 can be operated in two different modes.

[0055] In the example described, the actuator 50 is a rotary actuator, and the output member 51 is operable by the actuator 50 in two different rotational directions.

[0056] As an alternative (not shown), the actuator 50 is a linear actuator and the output member 51 is operable in two different translation directions by the actuator 50. The actuator is for example a rack and pinion system, or any other type of actuator having two different directions of movement.

[0057] When the engine system 10 is in a normal operating configuration, the output member 51 is in a neutral position. When the actuator 50 is operated in a first mode, the output member moves from its neutral position according to a first movement R1, and when the actuator 50 is operated in a second mode, the output member moves from its neutral position according to a second movement R2.

[0058] In the example described, the first movement is a first rotation R1 about the axis of rotation A51 of the part 51 with a first orientation, while the second movement is a second rotation R2 about the axis A51 of the part 51 with a second orientation opposite to the first orientation.

[0059] In the example described, the first movement R1 of the output member 51 switches the engine system 10 from its normal operating configuration to its braking configuration. Thus, the first movement of the output member 51 operates the two proportional exhaust valves 42 and 44 from their open positions to their closed positions and does not operate the proportional recirculation valve 38.

[0060] In the example depicted, the second movement R2 of the output member 51 switches the engine system 10 from its normal operating configuration to its recirculation configuration. Thus, the second movement of the output member 51 operates the first proportional exhaust valve 42 from its open position to its closed position, operates the proportional recirculation valve 38 from its closed position to its open position, and does not operate the second proportional exhaust valve 46.

[0061] In other words, in the example described, the first proportional exhaust valve 42 is operated by both movements R1 , R2 of the output member 51 , the second proportional exhaust valve 46 is operated only by the first movement R1 of the output member, and the proportional recirculation valve 38 is operated only by the second movement R2 of the output member.

[0062] In order to selectively operate the valves 38 , 42 , and 46 with the output member 51 depending on the direction of movement of the output member, the engine system 10 includes a kinematic chain connecting the output member to the valves.

[0063] The kinematic chain includes an output member 51 connected to the actuator 50 and a first transmission device 60 of the first proportional exhaust valve 42. The first transmission device 60 is driven by the output member 51 regardless of the direction of movement of the output member. In other words, the movements R1, R2 of the output member 51 are transmitted to the first proportional exhaust valve 42 through the first transmission device 60. Therefore, the first movement R1 of the output member 51 corresponds to the first movement of the first transmission device 60, and the second movement R2 of the output member corresponds to the second movement of the first transmission device.

[0064] In the example described, the first transmission 60 includes an input member 60A that interacts with the output member 51 of the actuator 50 so that the movement of the output member is transmitted to the input member 60A; a main shaft 60B that rotates about the rotation axis A60; a first crank 60C, one of the ends of which is connected to the main shaft 60B; and a second crank 60D, one of the ends of which is connected to the first crank 60C and the other of the ends of which is connected to the first shaft 56 of the first proportional exhaust valve 42. In the example described, the output member 51 and the input member 60A are gears that are engaged together. Other designs of the first transmission 60 are contemplated.

[0065] In the example described, the first movement R1 of the output member is converted by the cooperation of the gears into a first movement of the main shaft 60B in the first movement direction, i.e. a first rotation R11 around the axis A60 in the first orientation. The second movement R2 of the output member is converted by the cooperation of the gears into a second movement of the main shaft 60B in the second movement direction, i.e. a second rotation R12 around the axis A60 in the second orientation opposite to the first orientation.

[0066] As a variant (not shown), the output member 51 directly drives the spindle 60B, or is part of the spindle 60B. In other words, in this variant, the spindle 60B is part of the actuator 50.

[0067] The kinematic chain includes: a second transmission device 62, which is connected to the first transmission device 60 and the second proportional exhaust valve 46; and a first asymmetric linkage device 64, which is interposed between the first transmission device 60 and the second transmission device 62. The first asymmetric linkage device 64 transmits the first movement R11 of the first transmission device 60 to the second transmission device 62, but does not transmit the second movement R12 of the transmission device to the second transmission device. In other words, only the first movement of the output member 51 is transmitted to the second proportional exhaust valve 46 through the first transmission device 60, the first asymmetric linkage device 64 and the second transmission device 62. Therefore, the first movement of the output member 51 causes the movement of the second transmission device 62, while the second movement of the output member does not cause the second transmission device to move.

[0068] In the example described, the second transmission 62 includes a main shaft 62A, which is aligned with the axis A60, a first crank 62B, one of the ends of which is connected to the main shaft 62A, and a second crank 62C, one of the ends of which is connected to the first crank 62B and the other of the ends of which is connected to the second shaft 58 of the second proportional exhaust valve 46. Other designs of the second transmission 62 are contemplated.

[0069] In the example described, the first asymmetric linkage 64 comprises a protrusion 66 mounted on the first transmission 60 and an abutment surface 68 located on the second transmission 62. More precisely, the protrusion 66 is mounted on the end of the main shaft 60B of the first transmission 60, while the abutment surface 68 is located on the end of the main shaft 62A of the second transmission 62. During a first movement of the output member 51, the protrusion 66 abuts the abutment surface 68, so that it transmits the first movement of the output member to the second transmission 62, and during a second movement of the output member, the protrusion does not contact the abutment surface, so that it does not transmit the second movement of the output member to the second transmission 62. Other designs of the first asymmetric linkage 64 are contemplated.

[0070] In the example described, due to the concept of the first asymmetric linkage 64, during the first movement of the output member 51, the movement of the first proportional exhaust valve 42 is advantageously identical to the movement of the second proportional exhaust valve 46. In other words, the closing of the first proportional exhaust valve 42 is identical to the closing of the second proportional exhaust valve 46, i.e., the first movement of the output member 51 closes the first proportional exhaust valve 42 and the second proportional exhaust valve 46 simultaneously and at the same speed.

[0071] The kinematic chain includes a third transmission 70 connected to the first transmission 60 and the proportional recirculation valve 38, and a second asymmetric linkage 72 between the first transmission 60 and the third transmission 70. The second asymmetric linkage 72 transmits the second movement R12 of the first transmission 60 to the third transmission 70, but does not transmit the first movement R11 of the transmission to the third transmission. In other words, only the second movement of the output member 51 is transmitted to the proportional recirculation valve 38 through the third transmission 70. Therefore, the second movement of the output member 51 causes the movement of the third transmission 70, while the first movement of the output member does not cause the third transmission to move.

[0072] In the example described, the third transmission 70 is fixed at the end of the proportional recirculation valve 38 .

[0073] In the example described, the second asymmetric linkage 72 comprises a cam 72B and a roller 72A, the cam being mounted on the first transmission 60, more precisely on the main shaft 60B of the first transmission, the roller being attached to the third transmission 70. The roller 72A rolls onto the cam 72B. The profile of the cam 72B is selected so that during the first movement of the output member 51, the cam 72B does not move the roller 72A, and thus the first movement of the output member is not transmitted to the third transmission 70, so that the proportional recirculation valve 38 is not operated and remains in its closed position. Furthermore, the profile of the cam 72B is selected so that during the second movement of the output member 51, the cam 72B moves the roller 72A, so that the second movement of the output member is transmitted to the third transmission, so that the proportional recirculation valve 38 is operated by the third transmission from its closed position to its open position. Other designs of the second asymmetric linkage 72 are conceivable.

[0074] Due to the kinematic chain of the engine system 10 , the first movement of the output component 51 operates the first proportional exhaust valve 42 and the second proportional exhaust valve 46 and does not operate the proportional recirculation valve 38 , and the second movement of the output component 51 operates the first proportional exhaust valve 42 and the proportional recirculation valve 38 and does not operate the second proportional exhaust valve 46 .

[0075] Therefore, due to the kinematic chain of the engine system 10, only the actuator 50 is sufficient to operate the three valves 38, 42 and 46. Therefore, the engine system 10 can be switched from the normal operating state to the braking configuration, or the recirculation configuration, simply by actuating the output member 51 of the actuator 50 in the first movement direction or in the second movement direction.

[0076] The number of actuators required to operate the engine system 10 is thus reduced compared to existing engine systems, resulting in reduced manufacturing costs and greater compactness of the engine system 10. The control of the valves 38, 42, and 46 is also facilitated and more reliable because only one actuator operates all of these valves, and therefore only one actuator needs to be controlled to modify the configuration of the engine system 10.

[0077] It should be understood that the above describes in detail the switching of the engine system 10 from its normal operating condition to its braking configuration or its recirculation configuration, but the actuator 50 and the kinematic chain 60-72 also allow the engine system to switch from its braking configuration to its normal operating condition and from its recirculation configuration to its normal operating condition. Specifically, the reverse movement of the first movement R1 of the output component 51 causes the first proportional exhaust valve 42 and the second proportional exhaust valve 46 to open through the operation of the kinematic chain and due to the pressure applied by the exhaust gas to the proportional exhaust valve, and the proportional recirculation valve 38 is not operated, and thus allows the engine system to be switched from its braking configuration to its normal operating condition. In addition, the reverse movement of the second movement R2 of the output component 51 causes the first proportional exhaust valve 42 to open through the operation of the kinematic chain and due to the pressure applied by the exhaust gas to the first proportional exhaust valve, the proportional recirculation valve 38 to close due to the force applied by the return spring on the proportional recirculation valve, and the second proportional exhaust valve 46 is not operated, thereby allowing the engine system to be switched from its recirculation configuration to its normal operating condition. More precisely, the reverse movement of the first movement of the output component 51 corresponds to the movement of the output component from the position obtained after the first movement to the neutral position in the same direction as the second movement, and the reverse movement of the second movement of the output component 51 corresponds to the movement of the output component from the position obtained after the second movement to the intermediate position in the same direction as the first movement.

[0078] In the example described, the first proportional exhaust valve 42 and the second proportional exhaust valve 46 are located at the exhaust ports of the first exhaust collector 20 and the second exhaust collector 26, upstream of the first exhaust duct 30 and the second exhaust duct 32 in the direction of the gas flow 44 and 48. As a variant (not shown), the first proportional exhaust valve 42 and the second proportional exhaust valve 46 are located inside the turbocharger 28, or inside the first exhaust collector 20 and inside the second exhaust collector 26, respectively.

[0079] As a variation (not shown), the engine system 10 includes a secondary actuator dedicated to the operation of the proportional recirculation valve 38, and the actuator 50 operates only the first proportional exhaust valve 42 and the second proportional exhaust valve 46. The secondary actuator is used only to switch the engine system 10 to the recirculation configuration. In this variation, the first movement direction R1 of the output member 51 (corresponding to the first movement direction R1 described above) causes the output member 51 to operate both the first proportional exhaust valve 42 and the second proportional exhaust valve 46, and the second movement direction R2 of the output member 51 (corresponding to the second movement direction R2 described above) causes the output member 51 to operate only the first proportional exhaust valve 42 and not the second proportional exhaust valve 46. In this variation, the operation of the proportional recirculation valve 38 is separated from the operation of the first proportional exhaust valve 42 and the second proportional exhaust valve 46. Therefore, the proportional recirculation valve 38 can also be used in other situations where it is necessary to actuate the proportional exhaust valves 42, 46, resulting in a more versatile and reliable operation of the engine system 10.

[0080] As a variation (not shown), the engine system 10 includes a secondary actuator dedicated to the operation of the second proportional exhaust valve 46, and the actuator 50 operates only the first proportional exhaust valve 42 and the proportional recirculation valve 38. Therefore, the secondary actuator is used only to switch the engine system 10 to the braking configuration. In this variation, the first movement direction R1' (corresponding to the second movement direction R2 described above) of the output component 51 causes the output component 51 to operate both the first proportional exhaust valve 42 and the proportional recirculation valve 38, and the second movement direction R2' (corresponding to the first movement direction R1 described above) of the output component 51 causes the output component 51 to operate only the first proportional exhaust valve 42 and not the proportional recirculation valve 38. In this variation, the operation of the second proportional exhaust valve 46 is separated from the operation of the first proportional exhaust valve 42 and the proportional recirculation valve 38. In a configuration where the proportional recirculation valve 38 is open and the first proportional exhaust valve 42 is closed, using a separate actuator to operate the second proportional exhaust valve 46 allows fine adjustment of the opening of the second proportional exhaust valve 46 , thereby allowing control of the back pressure inside the second exhaust collector 26 of the second group of cylinders 22 .

[0081] As a variation (not shown), the actuator 50 and the kinematic chain are used to operate other valves in the engine system 10 in addition to the valves described above, such as, for example, a valve controlling air flow through the charge air cooler 84, and / or a valve controlling gas flow between the turbocharger 28 and the exhaust aftertreatment system 82 or downstream of the exhaust aftertreatment system 82, and / or a valve controlling gas flow upstream of the compressor 86.

[0082] The terms used herein are only for the purpose of describing specific aspects and are not intended to limit the present disclosure. As used herein, unless the context clearly indicates otherwise, the singular forms "a", "a kind of" and "the" are intended to also include plural forms. As used herein, the term "and / or" includes any and all combinations of one or more of the associated listed items. It should also be understood that when used in this article, the terms "include" and / or "comprising" indicate the presence of the features, integers, steps, operations, elements and / or parts, but do not exclude the presence or addition of one or more other features, integers, steps, operations, elements, parts and / or their groups.

[0083] It should be understood that although the terms first, second, etc. may be used herein to describe various elements, these elements should not be limited by these terms. These terms are only used to distinguish one element from another element. For example, without departing from the scope of the present disclosure, a first element may be referred to as a second element, and similarly, a second element may be referred to as a first element.

[0084] Relative terms such as "below" or "above" or "upper" or "lower" or "horizontal" or "vertical" may be used herein to describe the relationship of one element to another element, as shown in the figures. It should be understood that these terms and those discussed above are intended to cover different device orientations in addition to the orientations depicted in the figures. It will be understood that when an element is referred to as being "connected" or "coupled" to another element, the element may be directly connected or coupled to the other element, or there may be intervening elements. In contrast, when an element is referred to as being "directly connected" or "directly coupled" to another element, there are no intervening elements.

[0085] Unless otherwise defined, all terms (including technical and scientific terms) used herein have the same meaning as commonly understood by those of ordinary skill in the art to which the present disclosure belongs. It should also be understood that, unless otherwise clearly defined herein, the terms used herein should be interpreted as meanings consistent with their meanings in the context of this specification and the relevant art, and should not be interpreted in an idealized or overly formal sense.

[0086] It should be understood that the present disclosure is not limited to the aspects described above and shown in the accompanying drawings; rather, the skilled person will recognize that many changes and modifications can be made within the scope of the present disclosure and the appended claims. In the drawings and description, various aspects have been disclosed for illustrative purposes only and not for limiting purposes, and the scope of the inventive concept is set forth in the appended claims.

Claims

1. An engine system (10), the engine system comprising: - an internal combustion engine (12) comprising an air intake (14), a first group of cylinders (16) comprising at least a first cylinder (18) and a first exhaust gas collector (20), and a second group of cylinders (22) comprising at least a second cylinder (24) and a second exhaust gas collector (26), - turbocharger (28), - a first exhaust duct (30) providing fluid communication between the first exhaust collector and the turbocharger, - a second exhaust gas duct (32) providing fluid communication between the second exhaust gas collector and the turbocharger, - an exhaust gas recirculation system (34), said exhaust gas recirculation system comprising: a recirculation conduit (36) providing fluid communication between the first exhaust gas collector and the air intake of the internal combustion engine, and a proportional recirculation valve (38) adapted to control the exhaust gas flow (40) in the recirculation duct and operable between an open position, in which the exhaust gas flow is allowed, and a closed position, in which the exhaust gas flow is prevented, the closed position being a rest position of the proportional recirculation valve, - a first proportional exhaust valve (42) adapted to control an exhaust gas flow (44) in the first exhaust duct (30) and operable between an open position in which the exhaust gas flow is allowed and a closed position in which the exhaust gas flow is blocked, the open position being a rest position of the first proportional exhaust valve, and - a second proportional exhaust valve (46) adapted to control the exhaust gas flow (48) in the second exhaust gas duct (32) and operable between an open position in which the exhaust gas flow is allowed and a closed position in which the exhaust gas flow is blocked, the open position being a rest position of the second proportional exhaust valve, The engine system (10) is capable of switching between: - a first configuration in which the first proportional exhaust valve (42) and the second proportional exhaust valve (46) are in their open positions and the proportional recirculation valve (38) is in its closed position, and - a second configuration, in which the first proportional exhaust valve (42) is in its closed position, The engine system comprises an actuator (50) and a kinematic chain (60-72) configured to operate at least two valves among the proportional recirculation valve (38), the first proportional exhaust valve (42) and the second proportional exhaust valve (46), wherein when the engine system (10) is in the first configuration, the output member (51) of the actuator (50) is in a neutral position, A first movement of the output member from its neutral position in a first direction (R1; R1') operates each of the two valves from its rest position to the other position, and wherein a second movement of the output member from its neutral position in a second direction (R2; R2') opposite to the first direction operates only one of the two valves from its rest position to the other position.

2. The engine system (10) of claim 1, wherein the output component (51) of the actuator (50) is configured to operate the first proportional exhaust valve (42) and the second proportional exhaust valve (46), wherein the first movement of the output component (51) closes the first proportional exhaust valve and the second proportional exhaust valve, and wherein the second movement of the output component closes the first proportional exhaust valve and does not operate the second proportional exhaust valve.

3. The engine system (10) of claim 2, wherein the first movement of the output member (51) closes the first proportional exhaust valve (42) and the second proportional exhaust valve (46) at the same speed.

4. The engine system (10) of any one of claims 2 and 3, wherein each of the first proportional exhaust valve (42) and the second proportional exhaust valve (46) is an asymmetric flap valve including a flap (52, 54) and a shaft (56, 58), wherein rotation of the shaft causes opening or closing of the flap, and wherein the rotation of the shaft is driven by the output member (51) of the actuator (50).

5. The engine system (10) according to any one of claims 2 to 4, wherein the kinematic chain (60-72) comprises a first transmission (60) connected to the output member (51) of the actuator (50) and the first proportional exhaust valve (42), a second transmission (62) connected to the first transmission and the second proportional exhaust valve (46), and a first asymmetric linkage (64), wherein the first asymmetric linkage is configured as follows: - transmitting the first movement of the output member (51) from the first transmission means to the second transmission means, and - the second movement of the output member is not transmitted from the first transmission to the second transmission.

6. The engine system of claim 5, wherein the first asymmetric linkage (64) comprises a protrusion (66) mounted on the first transmission (60) and an abutment surface (68) located on the second transmission (62), wherein: - during said first movement of said output member (51), said projection abuts said abutment surface, and - During said second movement of said output member, said projection is not in contact with said abutment surface.

7. The engine system of claim 1, wherein the output component (51) of the actuator (50) is configured to operate the first proportional exhaust valve (42) and the proportional recirculation valve (38), wherein the first movement of the output component (51) closes the first proportional exhaust valve and opens the proportional recirculation valve, and wherein the second movement of the output component closes the first proportional exhaust valve and does not operate the proportional recirculation valve.

8. The engine system of claim 7, wherein the kinematic chain (60-72) comprises a first transmission (60) connected to the output member (51) of the actuator (50) and the first proportional exhaust valve (42), a third transmission (70) connected to the first transmission and the proportional recirculation valve (38), and a second asymmetric linkage (72), the second asymmetric linkage being configured as follows: - transmitting the first movement of the output member (51) from the first transmission means to the third transmission means, and - the second movement of the output member is not transmitted from the first transmission to the third transmission.

9. The engine system of claim 8, wherein the proportional recirculation valve (38) is a poppet valve, and wherein the second asymmetric linkage (72) includes a cam (72B) mounted on the first transmission (60) and a roller (72A) attached to the third transmission (70).

10. The engine system of claim 1, wherein the output member (51) of the actuator (50) is configured to operate the first proportional exhaust valve (42), the second proportional exhaust valve (46), and the proportional recirculation valve (38), wherein the first movement of the output member closes the first proportional exhaust valve and the second proportional exhaust valve and does not operate the proportional recirculation valve, and wherein the second movement of the output member closes the first proportional exhaust valve, opens the proportional recirculation valve, and does not operate the second proportional exhaust valve.

11. The engine system of claim 10, wherein the kinematic chain (60-72) comprises: - a first transmission device (60) connected to the output member (51) of the actuator (50) and the first proportional exhaust valve (42), - a second transmission (62) connected to the first transmission and the second proportional exhaust valve (46), - a third transmission (70) connected to the first transmission and the proportional recirculation valve (38), - a first asymmetric linkage (64), the first asymmetric linkage being configured to: o transmitting the first movement of the output member (51) from the first transmission device to the second transmission device, and o not transmitting the second movement of the output member from the first transmission device to the second transmission device, - a second asymmetric linkage (72), the second asymmetric linkage being configured to: o transmitting the second movement of the output member (51) from the first transmission device to the third transmission device, and The first movement of the output member is not transmitted from the first transmission device to the third transmission device.

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