KR101400832B1 - Large two-stroke diesel engine with an exhaust gas purification system - Google Patents

Abstract

The present invention relates to a large-sized turbocharged two-stroke diesel engine of a crosshead type having a plurality of cylinders respectively connected to an exhaust gas receiving portion. And a selective catalytic reduction reactor is disposed on the downstream side of the exhaust gas receiving portion. The exhaust conduit connects the outlet of the selective catalytic reduction reactor to the turbine of the turbocharger. The turbine drives the compressor of the turbocharger which transfers the scavenging to the scavenging receiver through the scavenging path. The scavenging receptacle is connected to a plurality of cylinders. The auxiliary blower in the scavenging path assists the compressor under low load conditions. A controllable bypass line extends from the scavenging receiver to the exhaust conduit. At low engine loads, the desired controlled flow is directed from the scavenging receiver to the exhaust duct at a point downstream of the selective catalytic reduction reactor and upstream of the turbine of the turbocharger. This action increases the temperature of the exhaust entering the selective catalytic reduction reactor. Moreover, the cooler in the scavenging path can be partially or fully controlled to achieve a cooling effect. Alternatively, the cooler may be controlled to be a heater, or the heater may be installed in a scavenging path.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a large two-stroke diesel engine having an exhaust gas purification system,

The present invention relates to a diesel engine having a crosshead type large turbocharged two-stroke internal combustion piston engine, preferably an exhaust gas purifying system, and particularly to a crosshead type large two-stroke diesel engine with a selective catalytic reduction reactor .

The large two-stroke engines of the crosshead type are typically used in the propulsion system of a large ship or as a prime mover in a power plant. Emission requirements have been difficult to meet and are increasingly more difficult to meet, especially with regard to nitrogen oxides (NOx).

The use of selective catalytic reduction (SCR) reactors is known to assist in reducing nitrogen oxide emissions in diesel engines. For exhaust gases entering the SCR converter, a minimum temperature of approximately 300 to 350 DEG C is required for proper functioning of the SCR reactor.

However, due to the nature of the two-stroke turbocharged engine, at low engine loads, for example, at engine loads below 40% of the maximum continuous rating of the associated engine, the exhaust gas temperature is relatively low, Gas is too low to be converted in the SCR reactor.

Under the above-mentioned low load conditions, it is difficult to maintain sufficient scavenge pressure in a large turbocharged two-stroke diesel engine. Therefore, in such a low load condition, an auxiliary blower is used to maintain the desired pressure. Therefore, no action taken to increase the temperature of the exhaust gas at the inlet of the SCR reactor should have a negative effect on the scavenging pressure.

Thus, there is a need for a turbocharged two-stroke diesel engine that overcomes or at least reduces the above-mentioned disadvantages.

In this context, it is an object of the present invention to provide a large turbocharged two-stroke diesel engine which can be operated with an SCR reactor under a wide range of engine load conditions.

This object is achieved by providing a large turbocharged two stroke combustion engine of the crosshead type, comprising a plurality of cylinders respectively connected to the exhaust gas receiving portion; A selective catalytic reduction reactor having an inlet connected to the outlet of the exhaust gas receiver; An exhaust conduit connecting the outlet of the selective catalytic reduction reactor to the turbine of the turbocharger; CLAIMS 1. A compressor of a turbocharger driven by a turbine, comprising: a compressor for delivering the product to a scavenging receiver via a scavenging path including an scavenger; An auxiliary blower in the exhaust path for assisting the compressor under low load conditions; A scavenging portion connected to each of the plurality of cylinders; A controllable bypass line extending from a location within the scavenging path to a location downstream of the auxiliary blower or into the exhaust conduit between the outlet of the selective catalytic reduction reactor and the inlet of the turbine from the scavenging receiver; And an electronic control unit operatively connected to the bypass line, wherein when the engine load is below a predetermined threshold or the temperature of the exhaust entering the selective catalytic reduction reactor is below a given threshold, And an electronic control unit configured to allow the desired flow through the pass line to the exhaust conduit.

At low engine loads, the desired controlled flow is directed from the scavenging receiver to the exhaust conduit at a location downstream of the selective catalytic reduction reactor and upstream of the turbine of the turbocharger. This action increases the temperature of the exhaust entering the selective catalytic reduction reactor without adversely affecting the desired pressure.

The exhaust conduit may include a mixing point of three ports for mixing the bypassed scavenger with the exhaust gas.

The bypass line may include a valve for regulating the desired flow through the bypass line.

The valve may be an on-off type valve that is electronically controlled within an open loop by an electronic control unit.

Alternatively, the valve may be a proportional control type valve electronically controlled in a closed loop by an electronic control unit.

The engine may further comprise a temperature sensor near the inlet of the selective catalytic reduction reactor.

The engine can be configured so that the scavenging cooler can be deactivated by the electronic control unit.

The electronic control unit may be configured to open to the bypass line as a first action and deactivate the scavenge cooler as a second action.

The engine can be configured such that the scavenging cooler can be converted to a heater by an electronic control unit.

The engine may be configured so that the electronic control unit converts the scavenge cooler to a heater as a third measure.

The object of the present invention is achieved by providing a large turbocharged two stroke combustion engine of the crosshead type comprising a plurality of cylinders respectively connected to the exhaust gas receiving portion; A selective catalytic reduction reactor having an inlet connected to the outlet of the exhaust gas receiver; An exhaust conduit connecting the outlet of the selective catalytic reduction reactor to the turbine of the turbocharger); CLAIMS 1. A compressor of a turbocharger driven by a turbine, comprising: a compressor for delivering the product to a scavenging receiver via a scavenging path including an scavenger; An auxiliary blower in the exhaust path for assisting the compressor under low load conditions; A scavenging portion connected to each of the plurality of cylinders; And an electronic control unit configured to reduce or deactivate the cooling function of the scavenge cooler when the engine load is below a predetermined threshold or when the temperature of the exhaust gas entering the selective catalytic reduction reactor is below a given threshold.

The engine may further include a scavenging bypass conduit for bypassing the scavenger.

The engine may further include one or more electronically controlled valves under command of an electronic control unit for controlling the desired flow through the scavenge bypass conduit.

The engine may further include a cooling medium bypass conduit having a cooling medium supply conduit with an electronically controlled isolation valve, a cooling medium return conduit and an electronically controlled bypass valve.

The engine may further comprise a recirculation conduit and a recirculation pump.

The engine may further include a heat exchanger within the recirculation conduit for heating the medium flowing through the recirculation conduit.

The engine may further comprise a second scavenger cooler, and the electronic control unit is configured to control the cooling capacity of the at least one scavenger cooler.

The engine may further comprise a steam injection conduit connected to the desired path, and the steam injection conduit has an electronically controlled steam injection control valve under command of the electronic control unit.

The engine may further comprise an exhaust gas injection conduit connected to the exhaust path, said exhaust gas injection conduit having an electronically controlled exhaust gas injection control valve under command of the electronic control unit.

The engine may further include a heater unit in the scavenging path. The heater unit can be operated by hot air as a heating medium.

The engine may further include a heat exchanger within the cooling medium supply conduit for supplying heat to the medium flowing through the cooling medium supply conduit.

Other objects, features, advantages and characteristics of a large two-stroke internal combustion engine according to the present invention will become apparent from the detailed description.

In the following detailed description of the present invention, the invention will be described in more detail with reference to exemplary embodiments shown in the drawings.
1 is a schematic view of an engine according to a first embodiment of the present invention.
2 is a schematic view of a second embodiment of the present invention.
Figs. 3-7 illustrate other embodiments that utilize reduced cooling. Fig.
Figures 8-12 illustrate other embodiments that utilize the desired active heating.

In the following detailed description, a method of operating a large turbocharged two-stroke diesel engine of the crosshead type and a large turbocharged two-stroke diesel engine of the crosshead type according to the present invention will be described with reference to an exemplary embodiment.

The construction and operation of a crosshead type large turbocharged diesel engine is well known and need not be described further herein. More details regarding the operation of the exhaust gas purification system are provided below.

Fig. 1 shows a first embodiment of a large two-stroke diesel engine 1 according to the present invention. The engine 1 can be used, for example, as a main engine in a marine vessel, or as a stationary engine for operating a generator in a power plant. The total output of the engine may range, for example, from 5,000 to 110,000 kW.

The engine 1 is provided with a plurality of cylinders arranged side by side. Each cylinder is provided with an exhaust valve associated with its cylinder lid. The exhaust channels can be opened and closed by an exhaust valve. The crosshead of the engine connects the piston rod to the large end of the crankshaft. Exhaust bends are connected to the exhaust gas receiving portion 6. The exhaust gas receiving portion 6 is disposed parallel to the rows of the cylinders. The exhaust gas receiving portion 6 is a large container and has dimensions that are specifically adapted to the characteristics of the engine for optimal gas flow, counter pressure and acoustical considerations. Normally, the exhaust gas receiving portion 6 is a large hollow cylinder body made of a steel plate. Because of its large size and weight, the exhaust gas receiving portion is suspended from the engine structure for the purpose of handling vibration problems.

From the outlet of the exhaust gas receiving portion 6 the exhaust gas flow is directed through the selective catalytic reactor 8 (SCR reactor) and the exhaust conduit 10 towards the turbine 12 of the turbocharger. Therefore, the outflow portion of the exhaust gas receiving portion 6 is connected to the inlet portion of the SCR reactor 8. The exhaust gas flows through the SCR reactor 8 and the nitrogen oxides in the exhaust gas are removed, or the amount thereof is at least substantially reduced to convert the nitrogen oxides to nitrogen and oxygen. The outlet of the SCR reactor is connected to an exhaust conduit (10), which leads the hot pressurized exhaust gas to the turbine (12). The exhaust gas is treated as an atmosphere downstream of the turbine 12. [

The turbocharger also has a compressor (14) driven by the turbine (12). The compressor 14 is connected to the air suction portion. The compressor 14 delivers scavenge air through the scavenging flow path 16 to the scavenging receiver 22 and the scavenging flow path includes the scavenging cooler 18 and the auxiliary blower 20.

The scavenging cooler 18 is operated by water as a cooling medium. Waste cooler 18 may be of various types. One possibility is as a plate cooler, in which the cooling medium does not make direct physical contact with the scavengers. Another possibility is a scrubber, in which the cooling medium is in direct contact with the scavengers.

The auxiliary blower 20 is generally driven by an electric motor (which may also be driven by a hydraulic motor) and is operated under low load conditions (typically at a maximum continuous rating Of less than 40%). When the auxiliary blower is not in use, it is bypassed via bypass not shown.

The scavenging accommodating portion 22 is a long hollow cylinder body extending along the cylinders of the engine. The scavenging is passed from the scavenging receptacle 22 to the scavenge air ports of the individual cylinders.

The controllable bypass line 26 branches off from the scavenging accommodating portion 22. The other end of the controllable bypass line 26 is connected to the exhaust conduit 10 at a three port mixing point 30. The mixing point 30 is located on the downstream side of the outlet of the SCR reactor 8 and on the upstream side of the inlet of the turbine 12.

Otherwise, the beginning of the controllable bypass line 26 may be located in the scavenging conduit 16 at a location downstream of the auxiliary blower 20.

The electronically controlled valve 28 under the command of the electronic control unit 33 regulates the desired flow from the scavenging flow path 16 to the exhaust conduit 10. In one embodiment, the valve 28 is an on / off type valve, which is controlled by the electronic control unit 33 within the open loop. In this embodiment, the electronic control unit 33 is configured to open the valve 28 when the engine load falls below a predetermined threshold, and to close the valve 28 when the engine load rises above a predetermined threshold. These two thresholds do not have to be the same and can be defined as a percentage of the maximum continuous rating of the engine.

In another embodiment, the electronically controlled valve 28 is a proportional valve, which is controlled by the electronic control unit 33 within the closed loop. Here, the controller receives information about the temperature of the exhaust gas at the inlet of the SCR reactor 8 from the temperature sensor 35, and the electronic control unit 33 calculates the measured value of the exhaust gas entering the SCR reactor 8 And to control the degree of opening of the valve 28 in response to the temperature. Accordingly, the electronic control unit 33 will increase the opening degree of the valve 28 to raise the temperature of the exhaust gas when the measured temperature is lower than the minimum desired temperature.

The thresholds may be controlled by the mixing temperature at the turbine inlet, i.e. the bypass line 26 is closed at a temperature higher than that required for the SCR reactor 8, The bypass line 26 is opened at a temperature that is almost too low.

The on / off bypass will be controlled after a predetermined mixing temperature at the turbine inlet, in a manner similar to that described for load control.

Fig. 2 shows a second embodiment of a large two-stroke diesel engine 1 according to the invention. The same reference numerals refer to the same parts in FIG. The embodiment according to FIG. 2 is substantially identical to the embodiment of FIG. 1, except for the following aspects for scavenge cooler 18 in scavenging path 16.

The feed conduit 40 conveys the cold water to the scavenger cooler 18 and the return conduit 42 transports the hot water away from the scavenging cooler 18. In the second embodiment, the bypass valve 44 and the isolation valve 46 in the electronically controlled cooling medium bypass circuit 43 under the command of the controller 33 are controlled such that the supply of cold water in the supply conduit 33 Allowing it to deflect to return conduit 42 without passing through cooler 18. A recycle conduit 48 comprising a pump 50 and a heater (or heat exchanger) 52 ensures that water flows through the scavenge cooler 18 which is now switched to a heater and is effective as a heat exchanger Function. The heater 52 is provided with a warm heating medium, such as hot water from the engine cooling system, and the heater 52 heats the medium circulated through the scavenger cooler 18.

In the second embodiment, the electronic control unit 33 can deactivate the cooler 18 through the valves 44, 46 by bypassing the cooling medium. At the same time, the controller 33 will activate the pump 50 to ensure that the medium is circulated in the scavenge cooler 18. Furthermore, the control unit 33 can activate the heater 52 by transferring the heating medium to the heater 52, and by doing so, can switch the scavenge cooler 18 to the heater. The electronic control unit 33 is configured to take various measures to raise the desired temperature in connection with the need to raise the temperature of the exhaust gas entering the SCR reactor 8.

Thus, if it is sufficient to pass some scrap to the exhaust conduit 10 through the controllable bypass line 26, the electronic control unit 33 will not take any further action. However, if this first action is not sufficient, the electronic control unit 33 will deactivate the cooling function of the scavenger 18. If this second measure is not sufficient, the electronic control unit 33 will actively heat the scavenger by switching the scavenger 18 to a heater as a third measure.

Figure 2 shows an example of the temperatures of the scavenging and exhaust gases at various locations in the system. These examples are for low engine load conditions, for example below 40% of the maximum continuous rating of the associated engine. Numbers without parentheses are the temperatures of the desiccant passing through the bypass line 26 and the desire of the desiccant cooler 18. The numbers in parentheses are the temperatures when the engine is normally operated with the scavenge cooler 18 cooling the scavenge without passing through the bypass line 26. The temperature of the exhaust gas entering the SCR reactor 8 is 325 DEG C and the exhaust gas is sufficiently hot to be converted in the SCR reactor 8. [ In the absence of new measures, the temperature of the exhaust entering the SCR reactor 8 is 220 ° C and the exhaust gas is not hot enough to be converted in the SCR reactor 8.

Figure 3 shows the supply and return of the cooling medium to the scavenger cooler 18 via the cooling medium supply conduit 40 and the cooling medium return conduit 42. [

Figures 4-7 illustrate various embodiments for a controlled reduction of the cooling capacity of the scavenge cooler 18.

In Fig. 4, the engine is provided with a scavenging bypass conduit 17 for bypassing scavenger cooler 18. The scavenging bypass conduit 17 is provided with an electronically controlled valve 23 under the command of the electronic control unit 33 to open and close the scavenging bypass conduit 17. The scavenging path 16 has another valve 21 electronically controlled under the command of the electronic control unit 33 to open and close the scavenging path 16. Therefore, the electronic control unit 33 is able to control the desired flow through the scavenge bypass conduit 17 as needed to raise the desired temperature, and thus to control the flow of exhaust gas entering the SCR reactor 8 The temperature can be raised.

5, the cooling medium supply conduit 40 is provided with an electronic control separation valve 46 and a cooling medium bypass circuit 43. The cooling medium bypass circuit 43 is connected to the electronic control bypass valve 44 And directly connects the cooling medium supply conduit 40 to the cooling medium return conduit 42. The electronic control unit 33 commands the solenoid valves 44 and 46 to control the degree to which the cooling medium passes through the scavenger 18 (on / off or proportional control).

6, a recirculation conduit 48 having a recirculation pump 50 (under the control of an electronic control unit 33) is added to the embodiment of FIG. 5 to enable it to circulate the cooling medium in the scavenge cooler 18 do.

In Fig. 7, the engine is provided with an additional (second) scavenger cooler 19. The electronic control unit 33 is configured to control the cooling capacity of the at least one scavenge cooler 18, 19 as described above.

Figures 8-12 illustrate various embodiments for applying heat in a controlled manner.

In FIG. 8, the engine is provided with a steam injection conduit 50 connected to the scavenging path 16. Steam injection conduit 90 has an electronically controlled steam injection control valve 92 under the command of an electronic control unit 33. Thus, the desired temperature and thus the temperature of the exhaust gas entering the SCR reactor 8 can be increased as desired by controllably injecting the vapor without any drop in scavenging pressure.

In Fig. 9, the engine is provided with an exhaust gas injection conduit 60 connected to the scavenging path 16. As shown in Fig. The exhaust gas injection conduit 60 is provided with an electronically controlled exhaust gas injection control valve 62 under the command of an electronic control unit 33. Thus, the desired temperature and thus the temperature of the exhaust gas entering the SCR reactor 8 can be increased as desired by controllably injecting the exhaust gas without a drop in the desired pressure.

In Fig. 10, the engine is provided with a heater unit 27 in the scavenging passage 16. In Fig. The heater unit 27 is supplied with a heating medium (such as hot water or hot air) through a heating medium supply conduit 70, and the return heating medium is transferred to be separated by the heating medium return conduit 72. The heating medium supply conduit 70 and the heating medium return conduit 72 are provided with electronically controlled valves under the command of the electronic control unit 33. Thus, the desired temperature and thereby the temperature of the exhaust gas entering the SCR reactor 8 can be raised as desired without a drop in the scavenging pressure.

The embodiment of FIG. 11 is substantially the same as the embodiment of FIG. 6, but further includes a heat exchanger 52 for adding heat to the medium circulated through the scavenging cooler 18.

In the embodiment of Figure 12, the engine is provided with a heat exchanger 80 in a cooling medium supply conduit 40 for supplying heat to the medium flowing through the cooling medium supply conduit 40.

Although the teachings of the present invention have been described in detail for purposes of illustration, it is to be understood that such detail is solely for that purpose and that modifications may be made by those skilled in the art without departing from the scope of the present invention.

The embodiments described above can be combined in all possible ways to enhance the functionality of the engine.

It should also be noted that there are several alternative ways to implement the device according to the teachings of the present invention.

The term " comprising "in the claims does not exclude other elements or steps. The definite articles and the indefinite articles set forth in the claims do not exclude a plurality of articles. A single processor or other unit may perform the functions of several means described in the claims.

1. Engine 6. Exhaust gas receiving portion
8. SCR reactor 10. Exhaust conduit
12. Turbine 14. Compressor
18. Cooler 20. Auxiliary blower

Claims (22)

In the crosshead type large turbocharged two-stroke combustion engine 1,
A plurality of cylinders respectively connected to the exhaust gas receiving portion 6;
A selective catalytic reduction reactor (8) having an inlet connected to the outlet of the exhaust gas receiver (6);
An exhaust conduit 10 connecting the outlet of the selective catalytic reduction reactor 8 to the turbine 12 of the turbocharger;
A compressor 14 of a turbocharger driven by a turbine 12 is driven by a scavenge air receiver 22 through a scavenge path 16 including a scavenge air cooler 18, a compressor 14 for delivering air;
An auxiliary blower (20) in the scavenging path (16) for assisting the compressor (14) under low load conditions;
A scavenging receiver (22) connected to each of the plurality of cylinders;
From a position in the desired path 16 to a position in the exhaust conduit 10 between the outlet of the selective catalytic reduction reactor 8 and the inlet of the turbine 12 from the scavenging receiver 22 to the downstream side of the auxiliary blower, An extended, controllable bypass line 26; And
An electronic control unit (33) operatively connected to the bypass line (26), wherein the engine load is below a predetermined threshold or the temperature of the exhaust entering the selective catalytic reduction reactor (8) is below a given threshold A large turbocharger of the crosshead type including an electronically controlled unit 33 configured to allow a desired flow from the scavenging receiver 22 to the exhaust conduit 10 via the controllable bypass line 26 when the engine is low, 2-stroke combustion engine. The method according to claim 1,
The exhaust conduit (10) has a three port mixing point (30) for mixing the bypassed scavenger with the exhaust gas, a large turbocharged two stroke combustion engine of the crosshead type. The method according to claim 1,
The bypass line (26) has a valve (28) for controlling the desired flow through the bypass line (26). The method of claim 3,
The valve 28 is an on-off type valve electronically controlled in an open loop by an electronic control unit 33. The valve 28 is a crosshead type large turbocharged two- . The method of claim 3,
Wherein the valve (28) is a proportional control type valve electronically controlled in a closed loop by an electronic control unit (33). The method according to claim 1,
Further comprising a temperature sensor (35) near the inlet of the selective catalytic reduction reactor (8). The method according to claim 1,
The scavenging cooler (18) can be deactivated by an electronic control unit (33), a large turbocharged two-stroke combustion engine of the crosshead type. 8. The method of claim 7,
The electronic control unit 33 is configured to open the bypass line 26 as a first action and deactivate the scavenge cooler 18 as a second action, . 8. The method of claim 7,
A large turbocharged two-stroke combustion engine of the crosshead type wherein the scavenging cooler (18) can be switched to a heater by an electronic control unit (33). 9. The method of claim 8,
The electronic control unit (33) is configured to convert the scavenge cooler (18) to a heater as a third action. In the crosshead type large turbocharged two-stroke combustion engine 1,
A plurality of cylinders respectively connected to the exhaust gas receiving portion 6;
A selective catalytic reduction reactor (8) having an inlet connected to the outlet of the exhaust gas receiver (6);
An exhaust conduit 10 connecting the outlet of the selective catalytic reduction reactor 8 to the turbine 12 of the turbocharger;
A compressor (14) of a turbocharger driven by a turbine (12), the compressor (14) delivering the scoop to the scoop receiver (22) via scavenging path (16) including scoop cooler (18);
An auxiliary blower (20) in the scavenging path (16) for assisting the compressor (14) under low load conditions;
A scavenging receiver (22) connected to each of the plurality of cylinders; And
An electronic control unit (ECU) configured to reduce or deactivate the cooling function of the scavenger cooler 18 when the engine load is below a predetermined threshold or when the temperature of the exhaust gas entering the selective catalytic reduction reactor 8 is below a given threshold (33), a crosshead type large turbocharged two-stroke combustion engine. 12. The method of claim 11,
Further comprising a scavenge bypass conduit (17) for bypassing the scavenge cooler (18). 13. The method of claim 12,
A large turbocharged two-stroke type of crosshead type, further comprising one or more electronically controlled valves under command of an electronic control unit (33) for controlling the desired flow through the scavenge bypass conduit (17) Combustion engine. 12. The method of claim 11,
A cooling medium bypass conduit 43 having an electronically controlled isolation valve 46 with a cooling medium supply conduit 40, a cooling medium return conduit 42 and an electronically controlled bypass valve 44 A large turbocharged 2-stroke combustion engine of the crosshead type, including. 15. The method of claim 14,
A large turbocharged two-stroke combustion engine of the crosshead type, further comprising a recirculation conduit (48) and a recirculation pump (50). 16. The method of claim 15,
Further comprising a heat exchanger (52) within the recirculation conduit for heating the medium flowing through the recirculation conduit (48). 15. The method of claim 14,
Further comprising a second scavenger cooler (19), said electronic control unit (33) being adapted to control the cooling capacity of at least one scavenging cooler (18, 19) engine. 12. The method of claim 11,
Further comprising a steam injection conduit (90) connected to the desired path (16), said steam injection conduit (50) having an electronically controlled steam injection control valve (92) under command of an electronic control unit (33) Crosshead type large turbocharged 2-stroke combustion engine. 12. The method of claim 11,
Further comprising an exhaust gas injection conduit (60) connected to the scavenge path (16), the exhaust gas injection conduit (60) comprising an electronically controlled exhaust gas injection control valve (62) under command of an electronic control unit A large turbocharged two stroke combustion engine of the crosshead type. 12. The method of claim 11,
A large turbocharged two-stroke combustion engine of the crosshead type, further comprising a heater unit (27) in an evacuation path. 21. The method of claim 20,
The heater unit (27) is operated by hot air as a heating medium, a large turbocharged two-stroke combustion engine of the crosshead type. 15. The method of claim 14,
A large turbocharged two-stroke combustion engine of the crosshead type, further comprising a heat exchanger (80) in a cooling medium supply conduit (40) for supplying heat to the medium flowing through the cooling medium supply conduit (40).

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