Patent ID: 12240563

DETAILED DESCRIPTION

Various exemplary embodiments and details are described hereinafter, with reference to the figures when relevant. It should be noted that the figures may or may not be drawn to scale and that elements of similar structures or functions are represented by like reference numerals throughout the figures. It should also be noted that the figures are only intended to facilitate the description of the embodiments. They are not intended as an exhaustive description of the disclosure or as a limitation on the scope of the disclosure. In addition, an illustrated embodiment needs not have all the aspects or advantages shown. An aspect or an advantage described in conjunction with a particular embodiment is not necessarily limited to that embodiment and can be practiced in any other embodiments even if not so illustrated, or if not so explicitly described.

The figures are schematic and simplified for clarity, and they merely show details which aid understanding the disclosure, while other details have been left out. Throughout, the same reference numerals are used for identical or corresponding parts.

An air supply system for supplying air to an outside of a hull of a vessel is disclosed. The vessel comprises an engine. The air supply system uses an EGR system for recirculating exhaust gas into a combustion process in the engine for generating a compressed air flow that is provided to a set of ADUs. The ADUs may be configured to be arranged on the hull of the vessel below a waterline of the vessel, such as on the wetted surface of the hull of the vessel. The compressed air provided to the ADUs may be released into a turbulent boundary layer of the water surrounding the vessel, to reduce the resistance of the vessel in the water. The air supply system comprises one or more turbocharger(s) for supplying a compressed main air flow to the engine of the vessel via a respective first flow path. The compressed main air flow, which may also be referred to as a scavenging air flow, is configured to be used in the combustion process of the engine. The air supply system comprises the EGR system for recirculating exhaust gas, such as exhaust gas from the engine, into the compressed main air flow supplied to the engine, via a second flow path. The air supply system comprises a third flow path for supplying a sub-flow of compressed air to one or more ADUs. The EGR system comprises a blower arranged in the second flow path for supplying exhaust gas to the engine. The blower increases the flow and the pressure of the fluid, such as the exhaust gas, flowing through the second flow path. The first flow path and the second flow path have a first connecting path upstream of the blower and a second connecting path downstream of the blower. The first connecting path and the second connecting path provide a fluid connection between the first flow path and the second flow path. The third flow path is in fluid connection with the first flow path and the second flow path downstream of the blower, such that the sub-flow of compressed air may be extracted from the first flow path and/or the second flow path. The flow paths, such as the first, the second and the third flow paths, being in fluid connection means that the flow paths are connected such as via the first and/or the second connecting path, so that a fluid may flow between the flow paths. The flow paths, mentioned herein, such as the first flow path, the second flow path and the third flow path, may be a plurality of pipes configured to allow a flow of a fluid from one location to a second location. The connecting path may e.g. be provided by means of a connecting pipe or by the first and the second flow paths, such as pipes of the first and the second flow paths, intersecting each other.

By connecting the first and the second flow paths via the first and/or the second connecting path, the flow of compressed air from the one or more turbocharger(s) may be rerouted from the first flow path via the blower of the EGR system, where the pressure of the compressed air is increased prior to being supplied to the ADUs via the third flow path. The pressure of the compressed air flow may thus be increased to above the discharge pressure at the ADUs, without having to use a dedicated blower. Thereby, the cost and complexity of the air supply system may be reduced, which in turn increase the total net efficiency of the vessel. The blower of the EGR system, may depending on the compression ratio required to increase the pressure of the compressed air to above the discharge pressure at the ADUs be either a blower or a compressor. The blower may operate at a lower compression ratio than the compressor, such as for example a ratio of 1.1 to 1.2 for the blower compared to a ratio greater than 1.2 for the compressor.

The sub-flow of compressed air may be extracted from the first flow path via the first connecting path and the blower of the EGR system in the second flow path. This may for example be done when the compressed air flow in the first flow path is below the discharge pressure at the ADUs, to increase the pressure of the compressed air using the blower of the EGR system. The sub-flow of compressed air may be extracted from the first flow path via the second connecting path, such as without passing the blower of the EGR system. This may for example be done when the compressed air flow in the first flow path is above the discharge pressure at the ADUs, to increase the pressure of the compressed air using the blower of the EGR system. The sub-flow of compressed air may further be extracted from the second flow path, such as from the exhaust gas receiver, via the blower of the EGR system. This may be used when the further reduction of emissions is required, and exhaust gas is fed to the combustion process via the second flow path and the second connecting path11BA.

The EGR system significantly reduces the formation of Nitrogen Oxides (NOx) in diesel engines. The EGR system helps the vessel to meet the International Maritime Organisation (IMO) NOx Tier 3 standard emission limits applying to the North American and United States Caribbean Sea, as well as any new NOx Emission Control Areas (NECA). In the EGR system, after a cooling and cleaning process of the exhaust gas, such as by using a scrubber, a part of the exhaust gas is recirculated to the engine, such as to the scavenge air receiver of the engine. In this way, part of the oxygen in the scavenge air is replaced by Carbon Dioxide (CO2) from the combustion process. By replacing some of the oxygen with CO2, the O2 content is decreased and the heat capacity of the scavenge air is increased, thus reducing the temperature peak of the combustion and the formation of NOx. The NOx reduction may be almost linear to the ratio of recirculated exhaust gas. IMO has also set a Tier 2 emission standard, which has less strict emission limits than the Tier 3 standard emission limits. The Tier 2 and Tier 3 NOx emission limits are defined in Regulation 13 of Annex VI of the “International Convention on the Prevention of Pollution from Ships”, also known as MARPOL 73/78. The Tier 2 and 3 emission limits apply to marine diesel engines with a power output of more than 130 kW installed on a vessel.

The EGR system may comprise a scrubber for cleaning the exhaust gases, and the blower for increasing the pressure and/or the flow of the exhaust gas. In one or more example air supply systems, the scrubber may be arranged in the second flow path. The scrubber may be arranged upstream of the blower and the first connecting path between the first and the second flow path. The scrubber may be configured to cool the exhaust gas and remove contaminants, such as sulphur dioxide and particulate soot. In one or more example air supply systems, the EGR system may comprise a cooler, such as a separate cooler, for cooling the exhaust gases, and a water mist catcher for removing moisture from the exhaust gas. By cooling the exhaust gas, the temperatures of the combustion process can be reduced, and the density of the exhaust gas can be increased, which improves the volumetric efficiency. The water mist catcher may remove moisture due to condensation of the exhaust gas due to the cooling of the exhaust gas. Removing the moisture may reduce the risk of corrosion in the components of the air supply system, such as in the flow paths or the blower.

In one or more example air supply systems, the air supply system may comprise a first flow control device for controlling a flow through the first connecting path between the first flow path and the second flow path. In one or more example air supply systems, the air supply system may comprise a second flow control device for controlling a flow through the second connecting path between the first flow path and the second flow path. In one or more example air supply systems, the air supply system may comprise a third flow control device for controlling a flow through the third flow path. In one or more example air supply systems, the air supply system may comprise a fourth flow control device for controlling a flow of exhaust gas into the second flow path. The flow control device(s), such as the first, the second, the third and/or the fourth flow control device may be an orifice or a control valve. The flow control device(s), such as the first, second, third and/or fourth flow control device, allow the flow of compressed air to be directed through different flow paths depending on the operating condition of the air supply system. By opening and closing different flow control device(s) the flow paths available for the compressed flow may be adapted. The flow control device(s) may be controlled based on an engine load, a pressure of the compressed air flow provided by the turbocharger, the discharge pressure at the ADUs and/or a flow rate of the compressed air flow. In some example air supply systems, the air supply system may comprise one or more sensors for monitoring the engine load, the pressure of the compressed air flow provided by the turbocharger, the discharge pressure at the ADUs and/or the flow rate of the compressed air flow.

The flow control device may in one or more example air supply systems be a fixed orifice, such as a fixed ratio orifice, configured to passively control the flow through the flow path. In one or more example air supply systems, the third flow control device may be an orifice such as a fixed ratio orifice, configured to extract a fraction of the fluid, such as the compressed air, flowing through the first and/or the second flow path. The orifice may e.g. be configured to extract 0-20%, such as 6-10%, of the fluid flowing through the first and/or the second flow path and provide it to the third flow path for supplying a sub-flow of compressed air to one or more ADUs. The fixed ratio orifice can ensure that only a predetermined amount of compressed air flow is extracted from the first flow path, such that a sufficient amount of compressed air is supplied to the engine of the vessel to allow cooling of the engine and combustion of the fuel injected into the combustion chamber of the engine.

In one or more example air supply systems, the flow control device may be variable, such as being a control valve, such as a diaphragm control valve, which can actively control the amount of gas allowed to be extracted to the air supply system.

In one or more example air supply systems, the first, second and fourth flow control device may be control valves. Thereby, the flow through the valves can be controlled in order to change the route of the flow of air through the flow paths and connecting paths of the air supply system.

The one or more turbochargers may comprise a turbine driven by an exhaust gas flow from the combustion engine, such as from the exhaust gas receiver of the engine, and a compressor for generating the compressed air flow, such as a scavenging air flow. The energy from the exhaust gas may thus be used to compress the flow of air.

In one or more example air supply systems, the air supply system may comprise two or more turbocharger(s). The air supply system may further comprise one or more cut out valves for controlling an exhaust gas flow to at least a first turbocharger of the two or more turbochargers. The one or more cut-out valves may be used for turning on or off a gas flow to a turbine side and/or from a compressor side of at least one of the two or more turbocharger(s). By turning off an exhaust gas flow to the turbine side of the at least one of the turbochargers by closing the cut-out valves a larger flow of exhaust gas may be provided to the remaining turbochargers, thereby increasing their compressing capacity, which will increase the pressure generated by the active turbocharger(s). By cutting out a first of the two or more turbochargers, all of the exhaust gas will flow through one or more second of the plurality of turbochargers, which may also be referred to as one or more active turbocharger(s). Since the available exhaust gas flow has to drive a smaller number of turbochargers, the exhaust gas flow to each of the active turbochargers, such as the turbochargers that have not been cut-out, will increase. The increase in exhaust gas to the one or more active turbochargers causes them to spin faster which will increase the pressure of the compressed air from the compressor side of these turbochargers through the first flow path. The higher exhaust gas pressure to the one or more active turbocharger(s) will increase the turbocharger efficiency and may thus allow a higher air pressure to flow through the first flow path to the engine, compared to a scenario where all of the turbochargers are active.

In a first example operating mode of the air supply system, the first flow control device, such as a control valve, and the third flow control device, such as a control valve, may be configured to be open. The second flow control device and the fourth flow control device are configured to be closed. Thereby, a flow of exhaust gas through the second flow path is prevented and a sub-flow of air is extracted from the first flow path and routed via the first connecting path via the blower of the EGR system to the ADUs. By routing the sub-flow of air through the first connecting path, the sub-flow of air is routed through the blower of the EGR system, where the sub-flow of air is compressed. The pressure of the sub-flow of air may thereby be increased to a pressure above the discharge pressure at the ADUs by the blower of the EGR system. Thereby, the discharge of compressed air through the ADUs may be started at lower engine loads. The increase of the pressure of the compressed air may also be performed without the use of a dedicated blower for the air supplied to the ADUs. Existing blower may be used.

In a second example operating mode of the air supply system, such as when the load of the engine is low, such as below a load threshold, the one or more cut out valves may be closed, so that the exhaust gas flow to at least the first turbocharger of the two or more turbochargers is prevented. Thereby, the pressure of the compressed air in the first flow path generated by the one or more second, active, turbochargers is increased. Thus, the air provided to the blower will also be higher, which reduces the work required by the booster to increase the pressure above the discharge pressure at the ADUs.

In a third example operating mode of the air supply system, such as when the load of the engine is high, such as above a load threshold, the one or more cut out valves may be open, so that the exhaust gas flow to at least the first turbocharger of the two or more turbochargers is allowed. Thereby, a higher flow of compressed air may be provided to the first flow path for supplying the compressed main air flow to the engine, when the engine is operating at higher loads.

In a fourth example operating mode of the air supply system, such as when the vessel is operating in a Tier 3 NOx emission mode, the first flow control device and the third flow control device may be configured, such as be controlled, to be closed and the second flow control device and fourth flow control device may be configured, such as be controlled, to be open. Thereby, a flow of exhaust gas through the second flow path is allowed and the exhaust gas is fed into the first flow path via the blower of the EGR system and the second connecting path.

In a fifth operating mode, such as when the vessel is operating in a Tier 3 NOx emission mode, the second flow control device and the third flow control device and the fourth flow control device are configured to be open and the first flow control device is configured to be closed, so that a flow of exhaust gas through the second flow path is allowed and fed into the first flow path and the third flow path via the blower of the EGR system and the second connecting path. Thereby, the emissions from the combustion process may be reduced while simultaneously reducing the friction of the vessel in the water by discharging air through the ADUs.

A vessel comprising the air supply system according to the current disclosure is further disclosed.

FIG.1illustrates an example of a pressure of the compressed air, such as a scavenging air (Pscav), provided to the engine by the one or more turbocharger(s) as a function of engine load. The discharge pressure at the ADUs is indicated by the draft pressure line inFIG.1. The discharge pressure at the ADUs is dependent on their location on the hull. When the ADUs are arranged at the bottom of the hull, the discharge pressure corresponds to the draft pressure of the vessel. In order for air to be released to the outside of the hull of the vessel via the ADUs, the pressure of the compressed air has to overcome the discharge pressure at the ADUs. As can be seen inFIG.1, the pressure of the compressed air is below the discharge pressure at the ADUs for engine loads below approximately 55%. For an air supply system using only compressed air provided by the turbochargers according to the example shown inFIG.1, air would only be released at engine loads above 55%. In the following, an air supply system will be disclosed which allows a discharge of air to the outside of the hull of the vessel also at lower engine loads.

In the following figures, dashed lines represent the flow of compressed air through the air supply system, black valves represent a closed valve preventing a flow through the vale and white valves represent an open valve allowing a flow through the valve.

FIG.2illustrates an example air supply system100for supplying air to an outside of the hull201of a vessel200according to the current disclosure. The vessel200comprises an engine, such as an internal combustion engine, such as a diesel engine, such as a two-stroke diesel engine. The engine is not disclosed inFIG.2but is indicated by the exhaust gas receiver for receiving exhaust from the engine and the scavenging air receiver for providing scavenging air to the engine, which are both peripheral to the engine. The air supply system100comprises a turbocharger10for supplying a compressed main air flow, such as a scavenging air flow, to the engine of the vessel200via a first flow path11A. The turbocharger10may be driven by exhaust gas from the exhaust gas receiver. In order to prevent the turbocharger from overrevving, the air supply system100may comprise an exhaust gas bypass valve34for releasing exhaust gas in order to reduce the flow of exhaust gas to the turbocharger10. The first flow path11A may also be referred to as a scavenging flow path. The first flow path may comprise an air cooler13for cooling the compressed air from the turbocharger10, a water mist catcher14for removing moisture from the compressed air flow, and/or a non-return valve15for preventing contaminated air from the combustion process to flow from the scavenging air receiver backwards towards the turbocharger10. The water mist catcher14may be arranged downstream of the air cooler13in the first flow path11A. The non-return valve15may be arranged downstream of the water mist catcher14in the first flow path11A. The air supply system100comprises an EGR system30for recirculating exhaust gas into the compressed main air flow of the first flow path via a second flow path11B. The EGR system may comprise a scrubber32for cleaning the exhaust gas, an EGR cooler33for cooling the exhaust gas and a blower31arranged in the second flow path11B for supplying exhaust gas to the engine, such as to the scavenging air receiver. The scrubber32may be arranged in the second flow path11B upstream of the blower31and the first connecting path11AB. The EGR system30may use the water mist catcher14in the first flow path11A for removing moisture from the exhaust gas. The exhaust gas from the EGR system30may thus be routed via the water mist catcher14in the first flow path11A. The air supply system100comprises a third flow path110for supplying a sub-flow of compressed air to one or more ADUs20. The one or more ADUs20are configured to be arranged in the hull201of the vessel200below a waterline. The first flow path11A and the second flow path11B have a first connecting path11AB upstream of the blower31and a second connecting path11BA downstream of the blower31. The third flow path110is in fluid connection with the first flow path11A and the second flow path11B downstream of the blower31, such that the sub-flow of compressed air may be extracted from the first flow path11A and/or the second flow path11B. The sub-flow of compressed air may be extracted from the first flow path11A via the first connecting path11AB, the second flow path11B and the blower31of the EGR system30. The sub-flow of compressed air may also be extracted from the first flow path11A via the second connecting path11AB, without passing through the blower31of the EGR system30. The sub-flow of compressed air may also be extracted from the second flow path11B, such as from the exhaust gas receiver, via the blower31of the EGR system30. In some example air supply systems100, the air supply system may comprise a cylinder bypass path11D connecting the scavenging air receiver and the exhaust gas receiver. The air supply system may comprise a cylinder bypass valve9for controlling the air flow through the cylinder bypass path.

The cylinder bypass11D may allow excess air to bypass the combustion process. The cylinder bypass valve9may be opened at a high load of engine, when the air supply system comprises only a single turbocharger, to compensate for a reduced flow capacity of the single turbocharger.

The air supply system100may comprise a first flow control device12A for controlling, such as opening and/or closing, a flow through the first connecting path11AB between the first flow path11A and the second flow path11B, a second flow control device12B for controlling a flow through the second connecting path11BA between the first flow path11A and the second flow path11B, a third flow control device12C for controlling a flow through the third flow path110, and/or a fourth flow control device12D for controlling a flow of exhaust gas into the second flow path11B. The first, second, third and fourth flow control devices11A-D are in the example shown here, control valves. However, the flow control devices, such as the third flow control device12C may also be an orifice having a fixed flow rate. The first flow control device12A is arranged in the first connecting path11AB between the first flow path11A and the second flow path11B. The second flow control device12B is arranged in the second connecting path11BA between the second flow path11B and the first flow path11A.

FIG.3illustrates an example air supply system100for supplying air to an outside of the hull201of a vessel200according to the current disclosure. The example air supply system100ofFIG.3differs from the example air supply system ofFIG.2in that the air supply system100comprises two or more turbocharger(s)10, such as a first turbocharger10and a second turbocharger10A. The air supply system100further comprises one or more cut out valves17for controlling an exhaust gas flow to at least the first turbocharger10A of the two or more turbochargers10,10A. By closing the cut-out valve17the exhaust gas flow to the first turbocharger10A can be turned off. This allows a larger flow of exhaust gas to be provided to the remaining turbochargers, such as the first turbocharger10. By cutting out a first of the two or more turbochargers, all of the exhaust gas will flow through the first turbocharger10, which may also be referred to as the active turbocharger(s). Since the available exhaust gas flow has to drive a smaller number of turbochargers, the exhaust gas flow to the first turbocharger10will increase. The increase in exhaust gas to the active turbochargers causes the active turbocharger to spin faster, which will increase the pressure of the compressed air from this turbocharger through the flow path11A, compared to a scenario where all of the turbochargers10,10A are active. The second turbocharger10A may be of a different size than the first turbocharger10. The second turbocharger10A may provide the compressed air to the scavenging air receiver via a dedicated flow path. In the example air supply system100shown inFIG.3, the second turbocharger may share the flow path with the EGR system30, such that the compressed air from the second turbocharger10A is provided to the scavenging air receiver via the second flow path11B. The EGR system30and the second turbocharger10A may thus share the cooler and the water mist catcher14. The air cooler13for the second turbocharger10A and the EGR cooler33may thus be the same cooler. The second turbocharger10A and the EGR system30may not use second flow path simultaneously. The second flow path may thus be used either by the second turbocharger10A or by the EGR system30. The first turbocharger10may thus be used together with the EGR without the second turbocharger10A or with the second turbocharger10A but without the EGR. The second turbocharger may be sized, which may also be referred to as being matched, for the maximum allowable EGR flow through the second flow path. The engine may thus either receive a flow of gas from the second flow path11B comprising normal air from the second turbocharger10A, such as during Tier 2 operation, or cleaned exhaust gas with reduced 02 content from the EGR system, such as from the scrubber32, during Tier 3 operation. The flow rate of the two different flows may be substantially the same, but the O2 content may differ.

FIG.4discloses an example operating mode of the air supply system disclosed herein. In this example operating mode, the air supply system operates in IMO Tier 2 mode without air being supplied to the ADUs20. In this operating condition, the flow control devices12A and12B are both closed, which is indicated inFIG.3with the valves being black. The compressed air flow, indicated by the dashed arrow, thus follows the first flow path11A, such as the scavenging flow path, from the turbocharger to the scavenging air receiver. No flow of compressed air will pass through the connecting paths11AB,11BA, through the second flow path11B or through the third flow path110.

FIG.5discloses an example operating mode of an example air supply system disclosed herein. In this example operating mode, the air supply system10operates in IMO Tier 2 mode with air being supplied to the ADUs20. The engine of the vessel may operate at a load below the load threshold, so that the pressure of the compressed air from the turbocharger10is not sufficient to overcome the discharge pressure at the ADUs20. In this operating mode, the first flow control device12A and the third flow control device12C are configured to be opened, as indicated by the valves being white in the figure. The second flow control device12B and the fourth flow control device12D are configured to be closed, so that a flow through the second connecting path11BA and a flow of exhaust gas through the second flow path is prevented. A sub-flow of air is extracted from the first flow path11A through the first connecting path11AB and routed via the first connecting path11AB via the second flow path11B to the blower31of the EGR system30, where the pressure of the sub-flow of air is boosted by the blower to a pressure above the discharge pressure at the ADUs20. When the pressure of the sub-flow of air has been increased by the blower to a pressure level higher than the discharge pressure at the ADUs, the sub-flow of air may overcome the discharge pressure at the ADUs and may flow through the third flow path110via the third flow control device12C to the one or more ADUs20. The third flow control device12C may be throttled to provide a target flow for the ADUs20.

FIG.6shows the same operating mode as shown inFIG.5, but for an air supply system100comprising more than one turbocharger, such as the air supply system100shown inFIG.3. For the example air supply system comprising more than one turbocharger, such as comprising the first turbocharger10and the second turbocharger10A, the one or more cut out valves17may, while the pressure of the compressed air is below the discharge pressure at the ADUs, be closed as indicated by the black valves inFIG.6, so that the exhaust gas flow to at least the turbocharger10A of the two or more turbochargers10,10A is prevented. This increases the exhaust gas flow to the remaining active turbochargers, such as to the turbocharger10of the two or more turbochargers10,10A. The first flow control device12A and the third flow control device12C are configured to be open, as indicated by the valves being white in the figure. The second flow control device12B and the fourth flow control device12D are configured to be closed, so that a flow through the second connecting path11BA and a flow of exhaust gas through the second flow path is prevented. A sub-flow of air is extracted from the first flow path11A through the first connecting path11AB and routed via the second flow path11B to the blower31of the EGR system30, where the pressure of the sub-flow of air is boosted by the blower to a pressure above the discharge pressure at the ADUs20. When the pressure of the sub-flow of air has been increased by the blower to a pressure level higher than the discharge pressure at the ADUs, the sub-flow of air may overcome the discharge pressure at the ADUs and may flow through the third flow path110via the third flow control device12C to the one or more ADUs20. The third flow control device12C may be throttled to provide a target flow for the ADUs20.

FIG.7discloses an example operating mode of an example air supply system disclosed herein. In this example operating mode, the air supply system10operates in IMO Tier 2 mode with air being supplied to the ADUs20. The engine of the vessel operates at a load above the load threshold, so that the pressure of the compressed air from the turbocharger10is sufficient to overcome the discharge pressure at the ADUs20. The second flow control device12B and the third flow control device12C are configured to be open, as indicated by the valves being white in the figure. The first flow control device12A and the fourth flow control device12D are configured to be closed, so that a flow through the first connecting path11AB and a flow of exhaust gas through the second flow path11B is prevented. A sub-flow of air is extracted from the first flow path11A through the second connecting path11BA and routed via the second connecting path11BA to the third flow path110, such that the blower31of the EGR system30is bypassed. Since the pressure of the sub-flow of compressed air is higher than the discharge pressure at the ADUs, the sub-flow of compressed air flows through the third flow path110via the open third flow control device12C to the one or more ADUs20in the hull201of the vessel200. By bypassing the blower, pressure losses in the sub-flow of compressed air may be reduced since the route via the second connecting path11BA has less restrictions than the route via the first connecting path11AB and the blower31. The third flow control device12C and/or the second flow control device12B may be throttled to provide a target flow for the ADUs20. The same operating mode may be applied to the example air supply system100ofFIG.3comprising more than one turbocharger, such as comprising the first turbocharger10and the second turbocharger10A. The sub-flow of air to the ADUs20is thus extracted from the first flow path11A via the second connecting path11BA and supplied to the ADUs20via the third flow path110.

FIG.8ashows the same operating mode as shown inFIG.7, but for an air supply system100comprising more than one turbocharger, such as the air supply system100shown inFIG.3. For the example air supply system comprising more than one turbocharger, such as comprising the first turbocharger10and the second turbocharger10A, the one or more cut out valves17may be opened as indicated by the white valves inFIG.8, so that the exhaust gas flow to the turbocharger10A is allowed. The cut-out valves17may for example be opened upon the pressure of the compressed air from the first turbocharger10being above the discharge pressure at the ADUs20, or when the first turbocharger10has reached a maximum load limit. The first flow control device12A and the third flow control device12C are configured to be open, as indicated by the valves being white in the figure. The second flow control device12B and the fourth flow control device12D are configured to be closed, so that a flow through the second connecting path11BA and a flow of exhaust gas through the second flow path11B is prevented. A sub-flow of compressed air, as indicated by the dashed line in theFIG.8a, is extracted from the first flow path11A through the first connecting path11AB and routed via the second flow path11B, where the sub-flow of compressed air from the first turbocharger mixes with the flow of compressed air from the second turbocharger10A. A sub-flow of the mixed compressed air is extracted from the second flow path via the blower31of the EGR system30, where the pressure of the sub-flow of air may be further boosted by the blower31. If the pressure of the sub-flow of air is higher than the capacity of the blower31, the blower may windmill in the sub-flow of compressed air. The sub-flow of the mixed compressed air then flows through the third flow path110via the open third flow control device12C to the one or more ADUs20.

FIG.8bshows a further operating mode of the example air supply system100comprising more than one turbocharger. Upon the pressure of the sub-flow of air provided by the plurality of turbochargers, such as the first and the second turbochargers10,10A is higher than the capacity of the blower31, instead of the blower31windmilling in the sub-flow of compressed air the blower may be bypassed. The first flow control device12A and the second flow control device12B may be opened. A sub-flow of compressed air, as indicated by the dashed line in theFIG.8b, may be extracted from the second flow path11B through the first connecting path11AB and routed via the first flow path11A, where the sub-flow of compressed air from the first turbocharger10mixes with the flow of compressed air from the second turbocharger10A. A sub-flow of the mixed compressed air is extracted from the first flow path via second connecting path11BA and then flows through the third flow path110via the open third flow control device12C to the one or more ADUs20. This may be the case when the air supply system100operates in Tier 2 mode and the engine operates at high load, such as at a load level above the load threshold.

FIG.9discloses an example operating mode of an example air supply system disclosed herein. In the operating mode shown inFIG.10the air supply system10operates in IMO Tier 2 mode. The third flow control device12C and the fourth flow control device12D are open, while the first flow control device12A and the second flow control device are closed. The exhaust gas can thus flow through the second flow path11B via the scrubber32and the blower31of the EGR system30to the third flow path110. The cleaned, cooled and/or compressed exhaust gas flow may then be provided to the ADUs20. The EGR system30may thus be used as an air source for supplying compressed air, such as clean exhaust gas, to the ADUs20when the air supply system is operating in IMO Tier 2 mode. Thereby, no air has to be extracted from the scavenging air flow supplied to the engine for supplying the ADUs20with air, thus increasing the amount of air available for the combustion process and cooling of the engine.

FIG.10discloses an example operating mode of an example air supply system disclosed herein. In the operating mode shown inFIG.10the air supply system10operates in IMO Tier 3 mode with decreased NOx emission limits. In order to meet the Tier 3 NOx emission limits, the EGR system is activated. The fourth flow control device12D is opened, as indicated by the white valve12D, so that an exhaust gas flows through the second flow path11B via the scrubber32. The second flow control device12B is also opened. The first flow control device12A and the third flow control device12C are configured to be closed, as indicated by the valves being black in the figure. Hence, no air will be supplied to the ADUs20. The cleaned exhaust gas is routed via the blower31of the EGR system30and the second connecting path11BA to the first flow path11A, where the exhaust gas is mixed with the compressed air flow from the turbocharger10. The flow of exhaust gas is thus fed into the first flow path11A via the blower31of the EGR system30and the second connecting path11BA. The exhaust gas may be mixed with the compressed air flow upstream of the water mist catcher14, so that moisture is removed when the mixed flow passes through the water mist catcher14before it enters the scavenging air receiver and is provided to the engine.

Although, the operating mode ofFIG.10is disclosed for the example air supply system100comprising only one turbocharger10, the same operating mode may also be used with the example air supply system ofFIG.3, comprising two or more turbochargers. The operating mode may further be combined with turbocharger cut-out, by closing the cut-out valves17of the second turbocharger10A, wherein the operation of the air supply system corresponds to the air supply system100comprising only one turbocharger10, such as disclosed inFIG.10.

FIG.11discloses an example operating mode of an example air supply system disclosed herein. In the operating mode shown inFIG.11the air supply system10operates in IMO Tier 3 mode with decreased, such as stricter, NOx emission limits. In order to meet the Tier 3 NOx emission limits, the EGR system is activated. The fourth flow control device12D is opened, as indicated by the white valve12D, so that an exhaust gas flows through the second flow path11B via the scrubber32. The first flow control device12A and the third flow control device12C are open, as indicated by the valves being white in the figure. The second flow control device12B is closed. The air supply to the ADUs20is thus active and cleaned exhaust gas is routed via the blower31of the EGR system30and the second connecting path11BA to the third flow path110. The first connecting path11AB is also open so that the cleaned exhaust gas is routed via the first connecting path11AB to the first flow path11A, where the exhaust gas is mixed with the compressed air flow from the turbocharger10. The exhaust gas may be mixed with the compressed air flow upstream of the water mist catcher14, so that moisture is removed when the mixed flow passes through the water mist catcher14before it enters the scavenging air receiver and is provided to the engine. In order to enhance the flow through the first connecting path11AB, an additional blower31A may be provided in the first connecting path11AB. In some example air supply systems, the blower31may be in connected to both the first connecting path11AB and the second connecting path11BA. In some example air supply systems100, a dedicated blower may be provided in the first connecting path11AB. In the operating mode shown inFIG.11, the EGR system30and the supply of compressed air to the ADUs may be active simultaneously. Thereby, the NOx emissions may be reduced to achieve IMO Tier 3 emission limits, while the efficiency of the vessel is further improved by reducing the resistance of the vessel in the water. The operating mode disclosed inFIG.11may correspondingly also be applied to the example air supply system100disclosed inFIG.3.

FIG.12discloses an example operating mode of an example air supply system disclosed herein. In the operating mode shown inFIG.12the air supply system10also operates in IMO Tier 3 mode with decreased, such as stricter, NOx emission limits. In order to meet the Tier 3 NOx emission limits, the EGR system is activated. The fourth flow control device12D is opened, as indicated by the white valve12D, so that an exhaust gas flows through the second flow path11B via the scrubber32. The second flow control device12B and the third flow control device12C are open, as indicated by the valves being white in the figure. The first flow control device12A is closed. The air supply to the ADUs20is thus active and cleaned exhaust gas is routed via the blower31of the EGR system30through the second connecting path11BA to the first flow path11A and the third flow path110. A first sub-flow of the cleaned exhaust gas is provided to the first flow path11A where the exhaust gas is mixed with the compressed air flow from the turbocharger10. The exhaust gas may be mixed with the compressed air flow upstream of the water mist catcher14, so that moisture is removed when the mixed flow passes through the water mist catcher14before it enters the scavenging air receiver and is provided to the engine. A second sub-flow of the cleaned exhaust gas is provided to the third flow path110and further to the ADUs20. The ratio of the first and the second sub-flow is controlled using the second flow control device12B and the third flow control device12C. The second flow control device12B and the third flow control device12C may be control valves. The second flow control device12B and the third flow control device12C may be throttled, such as being controlled, to provide the desired flow ratio. The ratio may depend on the amount of exhaust gas required by the combustion process in the engine to achieve the IMO Tier 3 or 2 emission limits. In the operating mode shown inFIG.12, the EGR system30and the supply of compressed air to the ADUs20may be active simultaneously. Thereby, the NOx emissions may be reduced to achieve IMO Tier 3 emission limits, while the efficiency of the vessel is further improved by reducing the resistance of the vessel in the water. The operating mode disclosed inFIG.12may correspondingly also be applied to the example air supply system100disclosed inFIG.3.

It shall be noted that the features mentioned in the embodiments described inFIGS.2-12are not restricted to these specific embodiments. Any features relating to the operating modes for the air supply system comprising a single turbocharger and the components comprised therein and mentioned in relation to the air supply system ofFIG.2, such as the operation of the flow control devices, are thus also applicable to the air supply system comprising more than one turbochargers as described in relation toFIG.3.

Embodiments of products (air supply system and vessel) according to the disclosure are set out in the following items:Item 1. An air supply system (100) for supplying air to an outside of a hull (201) of a vessel (200), the vessel (200) comprising an engine, the air supply system (100) comprising:one or more turbocharger(s) (10) for supplying a compressed main air flow to the engine of the vessel via a respective first flow path (11A),an exhaust gas recirculation, EGR, system (30) for recirculating exhaust gas into the compressed main air flow supplied to the engine via a second flow path (11B) anda third flow path (110) for supplying a sub-flow of compressed air to one or more air discharge units, ADUs, (20), wherein the one or more ADUs (20) are configured to be arranged in the hull (201) of the vessel (200) below a waterline,wherein the EGR system (30) comprises a blower (31) arranged in the second flow path (11B) for supplying exhaust gas to the engine,wherein the first flow path (11A) and the second flow path (11B) have a first connecting path (11AB) upstream of the blower (31) and a second connecting path (11BA) downstream of the blower (31), for providing a fluid connection between the first flow path and the second flow path, andwherein the third flow path (110) is in fluid connection with the first flow path (11A) and the second flow path (11B) downstream of the blower (31), such that the sub-flow of compressed air can be extracted from the first flow path (11A) and/or the second flow path (11B).Item 2. The air supply system (100) of Item 1, the air supply system (100) comprising a first flow control device (12A) for controlling a flow through the first connecting path (11AB) between the first flow path (11A) and the second flow path (11B), a second flow control device (12B) for controlling a flow through the second connecting path (11BA) between the first flow path (11A) and the second flow path (11B), a third flow control device (12C) for controlling a flow through the third flow path (110), and/or a fourth flow control device (12D) for controlling a flow of exhaust gas into the second flow path (11B).Item 3. The air supply system (100) according to any one of the previous Items, wherein the air supply system (100) comprises two or more turbocharger(s) (10,10A), wherein the air supply system (100) further comprises one or more cut out valves (17) for controlling an exhaust gas flow to at least a first turbocharger (10A) of the two or more turbochargers (10,10A).Item 4. The air supply system (100) according to Item 2, wherein, in a first operating mode, the first flow control device (12A) and the third flow control device (12C) are configured to be opened and the second flow control device (12B) and fourth flow control device (12D) are configured to be closed, so that a flow of exhaust gas through the second flow path (11B) is prevented and a sub-flow of air is extracted from the first flow path (11A) and routed via the first connecting path (11AB) via the blower (31) of the EGR system (31) to the ADUs (20).Item 5. The air supply system (100) according to Item 4, wherein, in a second operating mode, the one or more cut out valves (17) are closed, so that the exhaust gas flow to at least the first turbocharger (10A) of the two or more turbochargers (10) is prevented.Item 6. The air supply system (100) according to Item 4 or 5, wherein, in a third operating mode, the one or more cut out valves (17) are open, so that the exhaust gas flow to at least the first turbocharger (10A) of the two or more turbochargers (10) is allowed.Item 7. The air supply system (100) according to any one of the Items 1 to 6, wherein, in a fourth operating mode, the first flow control device (12A) and the third flow control device (12C) are configured to be closed and the second flow control device (12B) and fourth flow control device (12D) are configured to be open, so that a flow of exhaust gas through the second flow path (11B) is allowed and fed into the first flow path (11A) via the blower (31) of the EGR system (30) and the second connecting path (11BA).Item 8. The air supply system (100) according to any one of the Items 1 to 7, wherein, in a fifth operating mode, the second flow control device (12B) and the third flow control device (12C) and the fourth flow control device (12D) are configured to be open and the first flow control device (12A) is configured to be closed, so that a flow of exhaust gas through the second flow path (11B) is allowed and fed into the first flow path (11A) and the third flow path (110) via the blower (31) of the EGR system (31) and the second connecting path (11BA).Item 9. The air supply system (100) according to any one of the previous Items, wherein the EGR system (30) comprises a scrubber (32) arranged in the second flow path (11B) for cleaning the exhaust gas, wherein the scrubber is arranged upstream of the blower (31) and the first connecting path (11AB).Item 10. A vessel (200) comprising an engine and the air supply system (100) according to any one of the Items 1-9.

The use of the terms “first”, “second”, “third” and “fourth”, “primary”, “secondary”, “tertiary” etc. does not imply any particular order, but are included to identify individual elements. Moreover, the use of the terms “first”, “second”, “third” and “fourth”, “primary”, “secondary”, “tertiary” etc. does not denote any order or importance, but rather the terms “first”, “second”, “third” and “fourth”, “primary”, “secondary”, “tertiary” etc. are used to distinguish one element from another. Note that the words “first”, “second”, “third” and “fourth”, “primary”, “secondary”, “tertiary” etc. are used here and elsewhere for labelling purposes only and are not intended to denote any specific spatial or temporal ordering. Furthermore, the labelling of a first element does not imply the presence of a second element and vice versa.

It is to be noted that the word “comprising” does not necessarily exclude the presence of other elements or steps than those listed.

It is to be noted that the words “a” or “an” preceding an element do not exclude the presence of a plurality of such elements.

Although features have been shown and described, it will be understood that they are not intended to limit the claimed disclosure, and it will be made obvious to those skilled in the art that various changes and modifications may be made without departing from the scope of the claimed disclosure. The specification and drawings are, accordingly to be regarded in an illustrative rather than restrictive sense. The claimed disclosure is intended to cover all alternatives, modifications, and equivalents.