Engine system

Abstract

The engine system (10) comprises an internal combustion engine (12) having two cylinder sets (16, 22), a supercharger (28), two exhaust ducts (30, 32) providing fluid communication between the supercharger and the exhaust of the cylinder sets, and an exhaust gas recirculation system (34) comprising a recirculation valve (38). Two proportional exhaust valves (42, 46) are adapted to control the flow of exhaust gas in the two exhaust ducts. In a first configuration, the two exhaust valves are open and the recirculation valve is closed. In a second configuration, a first one of the two exhaust valves is in its closed position. The engine system comprises 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, and 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 engine systems.

[0002] The present disclosure can be applied to large vehicles such as trucks, buses, and construction equipment. Although the present disclosure is described with respect to particular vehicles, the present disclosure is not limited to any particular vehicle.

Background Art

[0003] In the field of large vehicles such as trucks powered by internal combustion engines, it is known to provide an engine system that includes an internal combustion engine having two cylinder sets, each cylinder set having a separate exhaust collector in fluid communication with a supercharger. Such an engine system typically includes two proportional exhaust valves, each proportional exhaust valve being operable to control the flow of exhaust gas from the exhaust collector of one of the cylinder sets to the supercharger.

[0004] When the vehicle is operating in a standard condition, the flow of exhaust gas generated by each cylinder set is directed from the exhaust collector of the corresponding cylinder set to the supercharger.

[0005] Also, it is known to use exhaust gas recirculation technology to reduce the nitrogen oxide emissions of the engine. This technology redirects the flow of exhaust gas from the first exhaust collector towards the intake of the internal combustion engine while allowing the flow of exhaust gas from the second exhaust collector to the supercharger. Accordingly, the engine system includes a recirculation conduit that provides fluid communication between the first exhaust collector and the intake of the internal combustion engine, and a proportional recirculation valve that controls the flow of exhaust gas through the recirculation conduit. The proportional recirculation valve is open when exhaust gas recirculation technology is used and is closed otherwise.

[0006] Also, for example, in order to brake the engine, it is also known to close two proportional exhaust valves to prevent the flow of exhaust gas from two exhaust collectors to the supercharger under specific operating conditions.

[0007] Therefore, such a normal engine system includes three actuators, and each actuator operates one valve out of two proportional exhaust valves and a proportional recirculation valve. Due to the existence of several actuators, these engine systems have high manufacturing costs, are complex, and are prone to failure.

[0008] The present invention aims at these drawbacks, and more specifically, aims to improve by proposing an engine system with lower manufacturing costs, more compactness, and higher reliability.

Summary of the Invention

[0009] An object of the present invention is to improve the compactness of an engine system by reducing the number of actuators required to operate the valves of the engine system.

[0010] According to an aspect of the present disclosure, the present invention relates to an engine system, the engine system comprising - an internal combustion engine including an intake section, a first cylinder set including at least a first cylinder and a first exhaust collector, and a second cylinder set including at least a second cylinder and a second exhaust collector; - a supercharger; - a first exhaust conduit providing fluid communication between the first exhaust collector and the supercharger; - a second exhaust conduit providing fluid communication between the second exhaust collector and the supercharger; - an exhaust gas recirculation system, - a recirculation conduit providing fluid communication between the first exhaust collector and the intake section of the internal combustion engine; A proportional recirculation valve adapted to control the flow of exhaust gas in a recirculation duct and operable between an open position allowing the flow of exhaust gas and a closed position preventing the flow of exhaust gas, wherein the closed position is the resting position of the proportional recirculation valve, the proportional recirculation valve, An exhaust gas recirculation system comprising, - A first proportional exhaust valve adapted to control the flow of exhaust gas in a first exhaust duct and operable between an open position allowing the flow of exhaust gas and a closed position preventing the flow of exhaust gas, wherein the open position is the resting position of the first proportional exhaust valve, the first proportional exhaust valve, - A second proportional exhaust valve adapted to control the flow of exhaust gas in a second exhaust duct and operable between an open position allowing the flow of exhaust gas and a closed position preventing the flow of exhaust gas, wherein the open position is the resting position of the second proportional exhaust valve, the second proportional exhaust valve, Comprising. The engine system is switchable between a first configuration in which the first proportional exhaust valve and the second proportional exhaust valve 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. The engine system comprises 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, the output component of the actuator is in a neutral position. A first movement of the output component from its neutral position in a first direction causes each of the two valves to move from their resting positions to another position, and a second movement of the output component from its neutral position in a second direction opposite to the first direction causes only one of the two valves to move from its resting position to another position.

[0011] As a result, the technical effects of the present 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 according to the moving direction of the output component of the actuator. As a result of the present invention, the engine system has a lower manufacturing cost, is more compact, and has higher reliability than existing engine systems.

[0012] In a specific example, the output component of the actuator is configured to operate the first proportional exhaust valve and the second proportional exhaust valve. The first movement of the output component closes the first proportional exhaust valve and the second proportional exhaust valve, and the second movement of the output component closes the first proportional exhaust valve and does not operate the second proportional exhaust valve. Thereby, the two proportional exhaust valves are controlled by the same actuator, and as a result, an optimized control of the proportional exhaust valve can be obtained while maintaining independent control of the proportional recirculation valve, and thus more accurate control.

[0013] In a specific example, the first movement of the output component closes the first proportional exhaust valve and the second proportional exhaust valve at the same speed. Thereby, the flow of the exhaust gas in the first exhaust duct becomes the same as the flow of the exhaust gas in the second exhaust duct, and as a result, the performance of the engine system is improved.

[0014] In a specific example, each of the first proportional exhaust valve and the second proportional exhaust valve is an asymmetric flap valve including a flap and a shaft. The rotation of the shaft causes the flap to open or close, and the rotation of the shaft is driven by the output component of the actuator. By using the asymmetric flap valve, when the actuator is not operating the proportional exhaust valve, the proportional exhaust valve naturally returns to the open position, thus improving the operation of the engine system.

[0015] In a specific example, the kinematic chain includes a first transmission device connected to the output component of the actuator and to the first proportional exhaust valve, a second transmission device connected to the first transmission device and to the second proportional exhaust valve, and a first asymmetric link mechanism. The first asymmetric link mechanism is configured to transmit a first movement of the output component from the first transmission device to the second transmission device and not to transmit a second movement of the output component from the first transmission device to the second transmission device. Thereby, the asymmetric link mechanism can select whether the actuator operates the second proportional exhaust valve only by selecting the movement direction of the output component of the actuator.

[0016] In a specific example, the first asymmetric link mechanism includes a tab assembled on the first transmission device and a contact surface arranged on the second transmission device. During the first movement of the output component, the tab is in contact with the contact surface, and during the second movement of the output component, the tab does not contact the contact surface. Therefore, the asymmetric link mechanism is particularly easy to implement, thus cost-effective and highly reliable.

[0017] In a specific example, the output component of the actuator is configured to operate the first proportional exhaust valve and the proportional recirculation valve. The first movement of the output component closes the first proportional exhaust valve and opens the proportional recirculation valve, and the second movement of the output component closes the first proportional exhaust valve and does not operate the proportional recirculation valve. Therefore, the two valves that operate when exhaust gas recirculation is required are operated by the same actuator. This facilitates the implementation of the exhaust gas recirculation technology and enhances the reliability.

[0018] In a specific example, the kinematic chain includes a first transmission device connected to the output component of the actuator and to a first proportional exhaust valve, a third transmission device connected to the first transmission device and to a proportional recirculation valve, and a second asymmetric link mechanism. The second asymmetric link mechanism is configured to transmit a first movement of the output component from the first transmission device to the third transmission device and not to transmit a second movement of the output component from the first transmission device to the third transmission device. Thereby, the asymmetric link mechanism can select whether the actuator operates the proportional recirculation valve only by selecting the movement direction of the output component of the actuator.

[0019] In a specific example, the proportional recirculation valve is a poppet valve, and the second asymmetric link mechanism includes a cam assembled to the first transmission device and a roller attached to the third transmission device. Thanks to the use of the poppet valve and the cam system, the control of the proportional recirculation valve when gas recirculation is required is particularly simple, effective and reliable.

[0020] In a specific example, the output component of the actuator is configured to operate a first proportional exhaust valve, a second proportional exhaust valve, and a proportional recirculation valve. A first movement of the output component closes the first proportional exhaust valve and the second proportional exhaust valve and does not operate the proportional recirculation valve. A second movement of the output component closes the first proportional exhaust valve, opens the proportional recirculation valve, and does not operate the second proportional exhaust valve. Therefore, since the three valves are operated by the same actuator, the engine system has a lower manufacturing cost and is more compact than existing engine systems.

[0021] In a specific example, the kinematic chain includes a first transmission device connected to the output component of the actuator and to the first proportional exhaust valve, a second transmission device connected to the first transmission device and to the second proportional exhaust valve, a third transmission device connected to the first transmission device and to the proportional recirculation valve, a first asymmetric link mechanism configured to transmit a first movement of the output component from the first transmission device to the second transmission device and not to transmit a second movement of the output component from the first transmission device to the second transmission device, and a second asymmetric link mechanism configured to transmit a second movement of the output component from the first transmission device to the third transmission device and not to transmit a first movement of the output component from the first transmission device to the third transmission device. Thereby, by the two asymmetric link mechanisms, 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 component of the actuator.

[0022] Additional features and advantages are disclosed in the following detailed description of embodiments for carrying out the invention, the claims, and the drawings, some of which will be readily apparent to those skilled in the art from the description or will be recognized by practicing the present disclosure described herein. Also disclosed herein are control units, computer-readable media, and computer program products related to the above-described technical effects and corresponding advantages.

[0023] A more detailed description of aspects of the present disclosure, cited by way of example, follows with reference to the accompanying drawings.

Brief Description of the Drawings

[0024]

Figure 1

Figure 2

Figure 3

Figure 4

DETAILED DESCRIPTION OF THE INVENTION

[0025] The aspects described below represent the information necessary for those skilled in the art to implement the present disclosure.

[0026] An exemplary engine system 10 is shown in FIG. 1. The engine system 10 is intended to be mounted on a vehicle to propel the vehicle. Such a vehicle can be, for example, a large vehicle such as a truck, a bus, or construction equipment.

[0027] The engine system 10 includes an internal combustion engine 12 that is propelled by the combustion of fuel such as diesel. The internal combustion engine 12 includes an intake section 14, a first cylinder set 16 including at least a first cylinder 18 and a first exhaust collector 20, and a second cylinder set including at least a second cylinder 24 and a second exhaust collector 26. In this example, each of the first cylinder set and the second cylinder set includes three cylinders 18, 24. As a variant not shown, each cylinder set includes a different number of cylinders, for example, four cylinders.

[0028] The engine system 10 includes an intake conduit 80 that provides fluid communication between the intake section 14 and the first cylinder set 16 and the second cylinder set 22. The intake section 14 supplies an oxidant such as air to the first cylinder set and the second cylinder set for fuel combustion.

[0029] The engine system 10 includes a fuel injection system (not shown) that supplies fuel to a first cylinder set 16 and a second cylinder set 22.

[0030] The engine system 10 includes a turbocharger 28, a first exhaust duct 30 that provides fluid communication between a first exhaust collector 20 and the turbocharger, and a second exhaust duct 32 that provides fluid communication between a second exhaust collector 26 and the turbocharger.

[0031] Advantageously, the engine system 10 includes an exhaust aftertreatment system 82 that is in fluid communication with the output of the turbocharger 28 on its intake side and in fluid communication with an exhaust system (not shown) on its output side. The exhaust aftertreatment system 82 is configured to purify the exhaust gas generated by the internal combustion engine 12 by filtering certain pollutants and converting other pollutants into non-polluting gases through chemical reactions.

[0032] Advantageously, the engine system 10 includes a charge air cooler 84. The output of the charge air cooler 84 is in fluid communication with the intake portion 14 of the internal combustion engine 12. The charge air cooler 84 supplies cooled air to the internal combustion engine 12.

[0033] Advantageously, the engine system 10 includes a compressor 86 that supplies compressed air to the charge air cooler 84. In one example, the compressor 86 is driven by the turbocharger 28.

[0034] Advantageously, the engine system 10 includes an air filter 88 that is in fluid communication with the intake portion of the compressor 86 and as a result filters the air supplied to the compressor 86 and the charge air cooler 84.

[0035] The engine system 10 includes an exhaust gas recirculation system 34, which enables the exhaust gas of the first cylinder set 16 to be recirculated to the intake section 14 of the internal combustion engine 12. The exhaust gas recirculation system 34 includes a recirculation conduit 36 and a proportional recirculation valve 38, i.e., a valve that can operate continuously.

[0036] The recirculation conduit 36 provides fluid communication between the first exhaust collector 20 of the first cylinder set 16 and the intake section 14 of the internal combustion engine 12.

[0037] The proportional recirculation valve 38 is adapted to control the flow of the exhaust gas 40 in the recirculation conduit 36. The proportional recirculation valve 38 is operable between an open position that allows the flow of the exhaust gas 40 and a closed position that prevents the flow of the exhaust gas 40, and the closed position is the rest position of the proportional recirculation valve 38. In FIGS. 2-4, the proportional recirculation valve 38 is shown by a dotted line because it is hidden by the first exhaust collector 20 and the recirculation conduit 36.

[0038] Accordingly, air is supplied to the intake section 14 of the internal combustion engine 12 by the charge air cooler 84, and exhaust gas is supplied by the exhaust gas recirculation system 34 when the proportional recirculation valve 38 is in its open position.

[0039] In this example, the proportional recirculation valve 38 is a poppet valve, i.e., a valve that operates linearly. Preferably, the engine system 10 includes a return spring (not shown) that exerts a force on the proportional recirculation valve 38 to tend to close the proportional recirculation valve. As a variant, the proportional recirculation valve 38 is another type of valve, such as a flap valve.

[0040] The engine system 10 includes a first proportional exhaust valve 42 that is adapted to control the flow 44 of the exhaust gas in the first exhaust conduit 30 and is operable between an open position that allows the flow of the exhaust gas and a closed position that prevents the flow of the exhaust gas, and the open position is the rest position of the first proportional exhaust valve, i.e., a valve that can operate continuously.

[0041] The engine system 10 is adapted to control the flow 48 of exhaust gas in the second exhaust conduit 32 and includes a second proportional exhaust valve 46 operable between an open position allowing the flow of exhaust gas and a closed position preventing the flow of exhaust gas, the open position being the rest position of the second proportional exhaust valve, i.e., a continuously operable valve.

[0042] In this example, the first proportional exhaust valve 42 is an asymmetric flap valve including a flap 52 and a shaft 56 to which the flap is fixed. Rotation of the shaft 56 causes the opening or closing of the flap 52. Advantageously, the shaft 56 is offset from the center with respect to the flap 52. Similarly, the second proportional exhaust valve 46 is an asymmetric flap valve including a flap 54 and a shaft 58 to which the flap is fixed. Rotation of the shaft 58 causes the opening or closing of the flap 54. Advantageously, the shaft 58 is offset from the center with respect to the flap 54.

[0043] As a variant, the first proportional exhaust valve 42 and the second proportional exhaust valve 46 are another type of valve, for example a poppet valve.

[0044] In fact, the open positions of the first proportional exhaust valve 42 and the second proportional exhaust valve 46 are the rest positions of the proportional exhaust valves because the shafts 56, 58 are not centered with respect to the flaps 52, 54 and pressure is applied to the flaps 52, 54 by the action of the exhaust gas from the exhaust collectors 20, 26 to open the flaps. Optionally, the first proportional exhaust valve and the second proportional exhaust valves 42, 46 include return springs that bias the opening of the flaps 52, 54. Such springs can make the proportional exhaust valves 42, 46 symmetric flap valves with the shafts 56, 58 centered with respect to the flaps 52, 54.

[0045] By operating the proportional recirculation valve 38, the first proportional exhaust valve 42, and the second proportional exhaust valve 46, the engine system is switchable between multiple configurations. Three exemplary configurations are described below in this specification.

[0046] In the normal operating configuration of the engine system 10, the first proportional exhaust valve and the second proportional exhaust valves 42, 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, the flow of the exhaust gas 40 is blocked, and the flows of the exhaust gases 44 and 48 are enabled, so that the exhaust gas generated by the internal combustion engine 12 is redirected entirely towards the supercharger 28. The normal operating conditions are represented in FIG. 2.

[0047] In the braking configuration of the engine system 10, the first proportional exhaust valve and the second proportional exhaust valves 42, 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 flow of the exhaust gas 40 is prevented, and the flows of the exhaust gases 44 and 48 are also prevented, whereby the exhaust gas generated by the internal combustion engine 12 is prevented from exiting the internal combustion engine, and as a result, the pressure within the internal combustion engine increases. For example, the pressure inside the internal combustion engine can increase up to 6 bar. This pressure increase generates a braking torque, and thus, the rotational speed of the internal combustion engine 12 decreases, and the vehicle propelled by the engine system is braked. Thus, the braking configuration can be used to brake the vehicle. The braking configuration is represented in FIG. 3.

[0048] 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, the flow of the exhaust gas 40 is enabled, the flow of the exhaust gas 44 is blocked, and the flow of the exhaust gas 48 is enabled. Thus, in this configuration, the first exhaust collector 20 is in fluid communication with the intake section 14, and the second exhaust collector 26 is in fluid communication with the supercharger 28. Thus, the recirculation configuration can be used, for example, when exhaust gas recirculation is required to reduce the nitrogen oxide emissions of the internal combustion engine 12. The recirculation configuration is shown in FIG. 4.

[0049] To operate the first proportional exhaust valve and the second proportional exhaust valves 42, 46, and the proportional recirculation valve 38, the engine system 10 includes a single actuator 50 that includes an output component 51. The output component 51 is operable by the actuator 50 in two different directions of movement. Thus, the actuator 50 is operable in two different modes.

[0050] In this example, the actuator 50 is a rotary actuator, and the output component 51 can be operated by the actuator 50 in two different rotational directions.

[0051] As an alternative not shown, the actuator 50 is a linear actuator, and the output component 51 can be operated by the actuator 50 in two different translational directions. The actuator is, for example, a rack and pinion system, or any other type of actuator having two different directions of movement.

[0052] The output component 51 is in a neutral position when the engine system 10 is in its normal operating configuration. When the actuator 50 is operated in the first mode, the output component moves from its neutral position according to a first movement R1, and when the actuator 50 is operated in the second mode, the output component moves from its neutral position according to a second movement R2.

[0053] In this example, the first movement is a first rotation R1 about the axis A51 of the component 51 and is in a first direction, whereas the second movement is a second rotation R2 about the axis A51 of the component 51 and is in a second direction opposite the first direction.

[0054] In this example, the first movement R1 of the output component 51 switches the engine system 10 from its normal operating configuration to its braking configuration. Thus, the first movement of the output component 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.

[0055] In this example, the second movement R2 of the output component 51 switches the engine system 10 from its normal operating configuration to its recirculation configuration. Thus, the second movement of the output component 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.

[0056] In other words, in this example, the first proportional exhaust valve 42 is operated by both movements R1 and R2 of the output component 51, the second proportional exhaust valve 46 is operated only by the first movement R1 of the output component, and the proportional recirculation valve 38 is operated only by the second movement R2 of the output component.

[0057] To selectively operate valves 38, 42, and 46 at the output component 51 depending on the movement direction of the output component, the engine system 10 comprises a kinematic chain connecting the output component to the valves.

[0058] The kinematic chain comprises a first transmission device 60 connected to the output component 51 of the actuator 50 and connected to the first proportional exhaust valve 42. The first transmission device 60 is driven by the output component 51 regardless of the movement direction of the output component. In other words, the movements R1 and R2 of the output component 51 are transmitted to the first proportional exhaust valve 42 via the first transmission device 60. Thus, the first movement R1 of the output component 51 corresponds to the first movement of the first transmission device 60, and the second movement R2 of the output component corresponds to the second movement of the first transmission device.

[0059] In this example, the first transmission device 60 includes an input component 60A that interacts with the output component 51 of the actuator 50 such that the movement of the output component is transmitted to the input component 60A, a main shaft 60B that rotates around the rotation axis A60, a first crank 60C having one end connected to the main shaft 60B, and a second crank 60D having one end connected to the first crank 60C and the other end connected to the first shaft 56 of the first proportional exhaust valve 42. In this example, the output component 51 and the input component 60A are gears that engage with each other. Other designs of the first transmission device 60 are also conceivable.

[0060] In this example, the first movement R1 of the output component is converted by the cooperation of the gears into a first movement of the main shaft 60B in a first movement direction that is a first rotation R11 around the shaft A60 having a first direction. The second movement R2 of the output component is converted by the cooperation of the gears into a second movement of the main shaft 60B in a second movement direction that is a second rotation R12 around the shaft A60 having a second direction opposite to the first direction.

[0061] As a variant (not shown), the output component 51 directly drives the main shaft 60B or is part of the main shaft 60B. In other words, in such a variant, the main shaft 60B is part of the actuator 50.

[0062] The kinematic chain includes a second transmission device 62 connected to the first transmission device 60 and also connected to the second proportional exhaust valve 46, and a first asymmetric link mechanism 64 interposed between the first transmission device 60 and the second transmission device 62. The first asymmetric link mechanism 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 component 51 is transmitted to the second proportional exhaust valve 46 via the first transmission device 60, the first asymmetric link mechanism 64, and the second transmission device 62. Therefore, the first movement of the output component 51 induces the movement of the second transmission device 62, and the second movement of the output component does not cause the movement of the second transmission device.

[0063] In this example, the second transmission device 62 includes a main shaft 62A aligned on the axis A60, a first crank 62B having one end connected to the main shaft 62A, and a second crank 62C having one end connected to the first crank 62B and the other end connected to the second shaft 58 of the second proportional exhaust valve 46. Other designs of the second transmission device 62 are also conceivable.

[0064] In this example, the first asymmetric link mechanism 64 includes a tab 66 assembled on the first transmission device 60 and a contact surface 68 disposed on the second transmission device 62. More precisely, the tab 66 is assembled at the tip of the main shaft 60B of the first transmission device 60, and the contact surface 68 is disposed at the tip of the main shaft 62A of the second transmission device 62. During the first movement of the output component 51, since the tab 66 is in contact with the contact surface 68, the tab 66 transmits the first movement of the output component to the second transmission device 62. During the second movement of the output component, since the tab 66 is not in contact with the contact surface 68, the tab does not transmit the second movement of the output component to the second transmission device 62. Other designs of the first asymmetric link mechanism 64 are also conceivable.

[0065] In this example, due to the concept of the first asymmetric link mechanism 64, the movement of the first proportional exhaust valve 42 is advantageously identical to the movement of the second proportional exhaust valve 46 during the first movement of the output component 51. In other words, the closing of the first proportional exhaust valve 42 is identical to the closing of the second proportional exhaust valve 46. That is, the first movement of the output component 51 closes the first proportional exhaust valve 42 and the second proportional exhaust valve 46 simultaneously and at the same speed.

[0066] The kinematic chain includes a third transmission device 70 connected to the first transmission device 60 and also connected to the proportional recirculation valve 38, and a second asymmetric link mechanism 72 interposed between the first transmission device 60 and the third transmission device 70. The second asymmetric link mechanism 72 transmits the second movement R12 of the first transmission device 60 to the third transmission device 70, but does not transmit the first movement R11 of the transmission device to the third transmission device. In other words, only the second movement of the output component 51 is transmitted to the proportional recirculation valve 38 via the third transmission device 70. Thus, the second movement of the output component 51 induces the movement of the third transmission device 70, and the first movement of the output component does not cause the movement of the third transmission device.

[0067] In this example, the third transmission device 70 is fixed to the end of the proportional recirculation valve 38.

[0068] In this example, the second asymmetric link mechanism 72 includes a cam 72B assembled on the first transmission device 60, more precisely on the main shaft 60B of the first transmission device, and a roller 72A attached to the third transmission device 70. The roller 72A rolls on the cam 72B. The contour of the cam 72B is selected such that during the first movement of the output component 51, the roller 72A is not moved by the cam 72B, and thus the first movement of the output component is not transmitted to the third transmission device, and as a result, the proportional recirculation valve 38 remains in its closed position without being operated. Further, the contour of the cam 72B is selected such that during the second movement of the output component 51, the roller 72A is moved by the cam 72B, whereby the second movement of the output component is transmitted to the third transmission device, and thus the proportional recirculation valve 38 is operated by the third transmission device from its closed position to its open position. Other designs of the second asymmetric link mechanism 72 are also conceivable.

[0069] Due to the kinematic chain of the engine system 10, the first movement of the output component 51 actuates the first proportional exhaust valve 42 and the second proportional exhaust valve 46, and does not actuate the proportional recirculation valve 38. The second movement of the output component 51 actuates the first proportional exhaust valve 42 and the proportional recirculation valve 38, and does not actuate the second proportional exhaust valve 46.

[0070] Therefore, it is sufficient to operate the three valves 38, 42, and 46 only with the actuator 50 due to the kinematic chain of the engine system 10. Therefore, it is possible to switch the engine system 10 from the normal operating state to the braking configuration or to the recirculation configuration only by operating the output component 51 of the actuator 50 in the first movement direction or the second movement direction.

[0071] Therefore, compared with the existing engine system, the number of actuators required to operate the engine system 10 is reduced, the manufacturing cost of the engine system 10 is reduced, and the compactness of the engine system is improved. Also, the control of the valves 38, 42, and 46 is facilitated and more reliable because only one actuator operates all of these valves, and thus only one actuator needs to be controlled to change the configuration of the engine system 10.

[0072] Although switching the engine system 10 from its normal operating state to its braking configuration or recirculation configuration is described in detail herein, it should be understood that the actuator 50 and the kinematic chain 60-72 also enable the engine system to be switched from its braking configuration to its normal operating state and from its recirculation configuration to its normal operating state. Specifically, the reversal of the first movement R1 of the output component 51, through the operation of the kinematic chain and by the pressure applied to the proportional exhaust valve by the exhaust gas, opens the first proportional exhaust valve 42 and the second proportional exhaust valve 46 and does not operate the proportional recirculation valve 38, thus enabling the engine system to be switched from its braking configuration to its normal operating state. Further, when the second movement R2 of the output component 51 is reversed, through the operation of the kinematic chain and by the pressure applied to the first proportional exhaust valve by the exhaust gas, the first proportional exhaust valve 42 opens, and the action of the return spring applies a force to the proportional recirculation valve 38, closing the proportional recirculation valve 38 and not operating the second proportional exhaust valve 46, thus enabling the engine system to be switched from its recirculation configuration to its normal operating state. More precisely, the reversal of the first movement of the output component 51 corresponds to the movement of the output component in the same direction as the second movement from the position obtained after the first movement to the neutral position, and the reversal of the second movement of the output component 51 corresponds to the movement of the output component in the same direction as the first movement from the position obtained after the second movement to the neutral position.

[0073] In this example, the first proportional exhaust valve 42 and the second proportional exhaust valve 46 are arranged on the exhaust sides 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 directions of the gas flows 44 and 48. As a variant not shown, the first proportional exhaust valve and the second proportional exhaust valves 42, 46 are arranged inside the supercharger 28 or inside the first exhaust collector 20 and the second exhaust collector 26, respectively.

[0074] As a deformation mode 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 and the second proportional exhaust valve 42, 46. The secondary actuator is used only to switch the engine system 10 to the recirculation configuration. In this deformation mode, the output component 51 operates both the first proportional exhaust valve 42 and the second proportional exhaust valve 46 by the first direction R1 of the movement of the output component 51 corresponding to the first movement direction R1 described above in this specification. The output component 51 operates only the first proportional exhaust valve 42 and does not operate the second proportional exhaust valve 46 by the movement direction R2 of the output component 51 corresponding to the second movement direction R2 described above in this specification. In such a deformation mode, the operation of the proportional recirculation valve 38 is separated from the operations of the first proportional exhaust valve and the second proportional exhaust valve 42, 46. Therefore, the proportional recirculation valve 38 can be used in other situations where the operation of the proportional exhaust valves 42, 46 is not necessarily required, resulting in a more versatile and reliable operation of the engine system 10.

[0075] As a deformation mode not shown in the drawings, the engine system 10 includes a secondary actuator dedicated to the operation of the second proportional recirculation 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 for switching the engine system 10 to the braking configuration. In this deformation mode, the output component 51 operates both the first proportional exhaust valve 42 and the proportional recirculation valve 38 by the first direction R1' of the movement of the output component 51 corresponding to the second movement direction R2 described above in this specification. The output component 51 operates only the first proportional exhaust valve 42 and does not operate the proportional recirculation valve 38 by the second movement direction R2' of the output component 51 corresponding to the first movement direction R1 described above in this specification. In such a deformation mode, the operation of the second proportional exhaust valve 46 is separated from the operations 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, by having another actuator that operates the second proportional exhaust valve 46, fine adjustment of the opening degree of the second proportional exhaust valve 46 becomes possible, and the back pressure inside the second exhaust collector 26 of the second cylinder set 22 can be controlled.

[0076] As a deformation mode not shown in the drawings, the actuator 50 and the kinematic chain are used to operate other valves within the engine system 10 other than the valves described hereinabove, for example, valves that control the air flow passing through the charge air cooler 84, and / or valves that control the gas flow between the supercharger 28 and the exhaust aftertreatment system 82 or downstream of the exhaust aftertreatment system 82, and / or valves that control the gas flow upstream of the compressor 86.

[0077] The terms used in this specification are for the purpose of describing particular aspects only and are not intended to limit the disclosure. As used herein, the singular forms "a", "an", and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. As used herein, the term "and / or" includes any and all combinations of one or more of the associated listed items. The terms "comprises", "comprising", "includes" and / or "including", when used herein, specify the presence of the stated feature, integer, step, operation, element, and / or component, but do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and / or groups thereof.

[0078] The terms, such as first, second, etc., may be used herein to describe various elements, but it is also understood that these elements should not be limited by these terms. These terms are only used to distinguish one element from another. For example, without departing from the scope of the present disclosure, a first element may be termed a second element, and similarly, a second element may be termed a first element.

[0079] Relative terms such as "downward", "upward", "upper", "lower", "horizontal", "vertical", etc. may be used herein to describe the relationship of one element to another as shown in the figures. It will be understood that these terms and the terms described above are intended to encompass different orientations of the device in addition to the orientation shown in the figures. When an element is referred to as being "connected" or "coupled" to another element, it will be understood that the element may be directly connected or coupled to the other element, or intervening elements may be present. In contrast, when an element is referred to as being "directly connected" or "directly coupled" to another element, no intervening elements are present.

[0080] Unless otherwise defined, all terms (including technical and scientific terms) used in this specification shall have the same meaning as commonly understood by one of ordinary skill in the art to which this disclosure belongs. The terms used in this specification should be interpreted as having a meaning that is consistent with their meaning in the context of this specification and the related art, and it should be further understood that they will not be interpreted in an idealized or overly formal sense unless explicitly so defined herein.

[0081] It should be understood that the present disclosure is not limited to the embodiments described above and illustrated in the drawings, but rather that one of ordinary skill in the art will recognize that many variations and modifications may be made within the scope of the present disclosure and the appended claims. The drawings and the specification are disclosed for purposes of illustration only and not for purposes of limitation, and the scope of the inventive concept is set forth in the following claims.

Claims

1. - An internal combustion engine (12) comprising an intake section (14), a first cylinder set (16) including at least a first cylinder (18) and a first exhaust collector (20), and a second cylinder set including at least a second cylinder (24) and a second exhaust collector (26), - A supercharger (28), - A first exhaust duct (30) providing fluid communication between the first exhaust collector and the supercharger, - A second exhaust duct (32) providing fluid communication between the second exhaust collector and the supercharger, - An exhaust gas recirculation system (34), A recirculation duct (36) providing fluid communication between the first exhaust collector and the intake section of the internal combustion engine, A proportional recirculation valve (38) adapted to control the flow (40) of exhaust gas in the recirculation duct and operable between an open position allowing the flow of the exhaust gas and a closed position preventing the flow of the exhaust gas, wherein the closed position is the stationary position of the proportional recirculation valve, the proportional recirculation valve (38), Comprising the exhaust gas recirculation system (34), - A first proportional exhaust valve (42) adapted to control the flow (44) of exhaust gas in the first exhaust duct (30) and operable between an open position allowing the flow of the exhaust gas and a closed position preventing the flow of the exhaust gas, wherein the open position is the stationary position of the first proportional exhaust valve, the first proportional exhaust valve (42), - A second proportional exhaust valve (46) adapted to control the flow (48) of exhaust gas in the second exhaust duct (32) and operable between an open position allowing the flow of the exhaust gas and a closed position preventing the flow of the exhaust gas, wherein the open position is the stationary position of the second proportional exhaust valve, the second proportional exhaust valve (46), Comprising an engine system (10), The engine system (10) is - 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, - A second configuration in which the first proportional exhaust valve (42) is in its closed position, And is switchable between them. The engine system (10) includes an actuator (50) and a kinematic chain (60-72) configured to operate at least two of the proportional recirculation valve (38), the first proportional exhaust valve (42), and the second proportional exhaust valve (46). When the engine system (10) is in the first configuration, the output component (51) of the actuator (50) is in a neutral position. A first movement of the output component from its neutral position in a first direction (R1, R1') causes each of the two valves to move from its rest position to another position. The engine system (10) in which a second movement of the output component from its neutral position in a second direction (R2, R2') opposite to the first direction causes only one of the two valves to move from its rest position to another position. **Claim 2** 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). The first movement of the output component (51) closes the first proportional exhaust valve and the second proportional exhaust valve. The second movement of the output component closes the first proportional exhaust valve and does not operate the second proportional exhaust valve. The engine system (10) according to claim 1. **Claim 3** The engine system (10) according to claim 2, wherein the first movement of the output component (51) closes the first proportional exhaust valve (42) and the second proportional exhaust valve (46) at the same speed. **Claim 4** Each of the first proportional exhaust valve (42) and the second proportional exhaust valve (46) is an asymmetric flap valve provided with a flap (52, 54) and a shaft (56, 58). The rotation of the shaft causes the opening or closing of the flap, and the rotation of the shaft is driven by the output component (51) of the actuator (50). The engine system (10) according to any one of claims 2 and 3. **Claim 5** The kinematic chain (60-72) is connected to the output component (51) of the actuator (50) and includes a first transmission device (60) connected to the first proportional exhaust valve (42), a second transmission device (62) connected to the first transmission device and to the second proportional exhaust valve (46), and a first asymmetric link mechanism (64), and the first asymmetric link mechanism is configured to - transmit the first movement of the output component (51) from the first transmission device to the second transmission device, - not transmit the second movement of the output component from the first transmission device to the second transmission device, The engine system (10) according to any one of claims 2 to 4, which is configured to perform the above.

6. The first asymmetric link mechanism (64) includes a tab (66) assembled to the first transmission device (60) and a contact surface (68) disposed on the second transmission device (62), - during the first movement of the output component (51), the tab is in contact with the contact surface, - during the second movement of the output component, the tab does not contact the contact surface. The engine system according to claim 5.

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

8. The kinematic chain (60-72) is connected to the output component (51) of the actuator (50) and includes a first transmission device (60) connected to the first proportional exhaust valve (42), a third transmission device (70) connected to the first transmission device and to the proportional recirculation valve (38), and a second asymmetric link mechanism (72), and the second asymmetric link mechanism is configured to - transmitting the first movement of the output component (51) from the first transmission device to the third transmission device; - not transmitting the second movement of the output component from the first transmission device to the third transmission device; The engine system according to claim 7, which is configured to perform the above.

9. The proportional recirculation valve (38) is a poppet valve, and the second asymmetric link mechanism (72) includes a cam (72B) assembled to the first transmission device (60) and a roller (72A) attached to the third transmission device (70). The engine system according to claim 8.

10. The output component (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). The first movement of the output component closes the first proportional exhaust valve and the second proportional exhaust valve and does not operate the proportional recirculation valve. The second movement of the output component closes the first proportional exhaust valve, opens the proportional recirculation valve, and does not operate the second proportional exhaust valve. The engine system according to claim 1.

11. The kinematic chain (60-72) is - a first transmission device (60) connected to the output component (51) of the actuator (50) and connected to the first proportional exhaust valve (42); - a second transmission device (62) connected to the first transmission device and connected to the second proportional exhaust valve (46); - a third transmission device (70) connected to the first transmission device and connected to the proportional recirculation valve (38); - a first asymmetric link mechanism (64), wherein the first asymmetric link mechanism transmits the first movement of the output component (51) from the first transmission device to the second transmission device; does not transmit the second movement of the output component from the first transmission device to the second transmission device; The first asymmetric link mechanism (64) configured to perform the above. - a second asymmetric link mechanism (72), wherein the second asymmetric link mechanism transmits the second movement of the output component (51) from the first transmission device to the third transmission device, and does not transmit the first movement of the output component from the first transmission device to the third transmission device, and is configured to perform the above, the second asymmetric link mechanism (72); The engine system according to claim 10, comprising.

Images