Exhaust gas cooling device

Abstract

To provide an exhaust gas cooling device 1 for a large internal combustion engine, and an internal combustion engine.SOLUTION: The exhaust gas cooling device 1 comprises a precooling jet tube 2, an outflow tube 3, and an absorber unit 4. The absorber unit 4 has a height h, a maximal width w, and a maximal length l, where the maximal length l is longer than the maximal width w. The exhaust gas cooling device 1 further comprises: an inflow deflector housing 6 tapering along the length l of the absorber unit 4, and fluidly connected with the precooling jet tube 2 and the absorber unit 4; and an outflow deflector housing 7 tapering along the length l of the absorber unit and fluidly connected with the absorber unit 4 and with the outflow tube 3.SELECTED DRAWING: Figure 2

Description

[Technical field]

[0001] The present invention relates to an exhaust gas cooling device for an internal combustion engine and to an internal combustion engine.

[0002] The invention preferably relates to an internal combustion engine, such as a large marine or ship engine or a stationary engine, with an internal cylinder diameter of at least 200 mm. The engine is preferably a two-stroke engine or a two-stroke cross-head engine. The engine may be a diesel or gas engine, a dual-fuel engine or a multi-fuel engine. In such an engine, in addition to auto-ignition or forced ignition, the combustion of liquid and / or gaseous fuels is also possible.

[0003] The internal combustion engine may be a longitudinally scavenged two-stroke engine.

[0004] The term internal combustion engine also refers to larger engines that can be operated in a diesel mode, characterized by the autoignition of one fuel, as well as in an Otto mode, characterized by the ignition of one fuel, or a mixture of both. Furthermore, the term internal combustion engine includes, among others, dual-fuel engines and larger engines in which the autoignition of one fuel is used to ignite another fuel.

[0005] Engine speeds below 800 RPM are preferred, especially for four-stroke engines, and more preferably below 200 RPM, especially for two-stroke engines, indicating a slow engine designation.

[0006] The fuel may be diesel or marine diesel, or heavy fuel oil, or an emulsion, or a slurry, or methanol, or ethanol, and a gas such as liquid natural gas (LNG), liquid petrol gas (LPG).

[0007] Further possible fuels could include, on demand, LBG (Liquefied Biogas), biofuels (e.g. oils made from algae or seaweed), ammonia, hydrogen, synthetic fuels from CO2 (e.g. produced by Power-to-Gas or Power-to-Liquid). [Background technology]

[0008] Larger ships, especially those used for carrying cargo, are usually powered by internal combustion engines, especially diesel and / or gas engines, mainly two-stroke crosshead engines.

[0009] To reduce the reactivity of the gas / air mixture and the methane slip, it is known to perform exhaust gas recirculation (EGR), in particular low pressure EGR, as shown for example in EP 3722572 A1. A part of the exhaust gases is recirculated into the cylinder, while another part of the exhaust gases is guided to the chimney and released into the environment.

[0010] While the high-pressure EGR path is generally inserted directly between the exhaust manifold and the intake manifold, the low-pressure EGR path is branched off downstream of the turbocharger turbine so that the recirculated exhaust gas can be guided through the turbocharger compressor along with the fresh air.

[0011] Typically, the low pressure EGR path includes a low pressure EGR cooling device, which may be too large in size to be mounted near the engine or on the engine itself.

[0012] If the EGR cooler is placed outside the cylinder block, there will be problems with interference with other auxiliary equipment. In addition, the support strength for the heavy load must be resolved.

[0013] EP 2853726 B1 discloses a particular engine design which allows the low pressure cooler to be miniaturised.

[0014] Japanese Patent Application Laid-Open No. 2000248936 (A2) discloses an engine having an EGR cooler that requires a small installation space. The EGR cooler is disposed near the rear end of the engine body. The EGR cooler is supported by a single mounting stay that is connected to a part of the engine body and a part of the intake pipe.

[0015] However, when the EGR cooler has a considerable volume and weight, the engine itself becomes large and cannot be compactly installed in a narrow engine room. In particular, since the low-pressure EGR cooler has low pressure and low speed, the cooling absorber that cools by dripping water has a size too large to be attached to the long side of the engine. The absorber exceeds the available space between the engine and the engine room wall.

[0016] US Pat. No. 10,100,787 B2 and DE 10 2014 115 453 A1 disclose an EGR cooler having parallel arranged channels which act as a heat exchanger and through which the EGR gases are guided. [Prior art documents] [Patent documents]

[0017] [Patent Document 1] European Patent Application Publication No. 3722572(A1) [Patent Document 2] European Patent No. 2853726(B1) [Patent Document 3] Japanese Patent Application Publication No. 2000248936(A2) [Patent Document 4] U.S. Patent No. 10,100,787(B2) [Patent Document 5] German Patent Application Publication No. 102014115453(A1) Summary of the Invention [Problem to be solved by the invention]

[0018] The present invention is based on the task of providing an exhaust gas cooling device and an internal combustion engine which avoid the known disadvantages, and in particular proposes an EGR cooling device which is easy to rearrange in order to provide an engine with an engine-mounted EGR cooling device. [Means for solving the problem]

[0019] This object is achieved by means of the features of the independent claims.

[0020] SUMMARY OF THE PRESENT EMBODIMENT In accordance with the present invention, an exhaust gas cooling system for a large internal combustion engine includes a pre-cooling injection tube, an outflow tube, and an absorber unit.

[0021] The pre-cooled injection tube has an exhaust gas inlet and the outlet tube has an exhaust gas outlet. An absorber unit is fluidly disposed between the pre-cooled injection tube and the outlet tube.

[0022] A standard tube type cooling absorber has a diameter of 1-6m. The absorber unit has a height, a maximum width and a maximum length, the maximum length being greater than the maximum width. The maximum width is preferably less than 50% of the diameter of a comparable standard tube type absorber. The maximum width is preferably less than 3m.

[0023] The flow area is the cross-sectional area perpendicular to the main exhaust gas flow direction. The flow area of ​​an absorber unit or single absorber is parallel to a plane spanning the width and length of the absorber unit or single absorber, and the flow direction through the absorber unit is parallel to the height direction.

[0024] The exhaust gas cooling system further includes an inlet deflector housing tapered along a length of the absorber unit, the inlet deflector housing fluidly connected with the pre-cooling jet tube and the absorber unit.

[0025] A tapered configuration of the inlet deflector housing may be provided to change the main flow direction of the gas from a first main flow direction within the inlet deflector housing to a second main flow direction within the absorber unit, the second main flow direction being preferably perpendicular to the first main flow direction.

[0026] The flow area of ​​the inlet deflector housing may be reduced in a mainstream direction through the inlet deflector housing over the length of the absorber unit.

[0027] The exhaust gas cooling system further includes an outlet deflector housing tapered along a length of the absorber unit, the outlet deflector housing fluidly connected to the absorber unit and the outlet tube.

[0028] A tapered configuration of the outlet deflector housing can be provided to change the main flow direction of the gas from a second main flow direction in the absorber unit to a third main flow direction in the outlet deflector housing, the second main flow direction being preferably perpendicular to the third main flow direction.

[0029] A flow area of ​​the outlet deflector housing may extend in a mainstream direction through the outlet deflector housing over a length of the absorber unit. The inlet deflector housing and the outlet deflector housing are each disposed adjacent the absorber unit.

[0030] The tapered form of the inlet deflector housing allows for a homogenous flow of exhaust gas into the flow area of ​​the absorber unit, while the tapered form of the outlet deflector housing allows for a homogenous flow of exhaust gas from the flow area of ​​the absorber unit. This also applies when the exhaust gas pressure is low, e.g. in low pressure exhaust gas recirculation systems.

[0031] Thus, the exhaust gas pressure can be evenly distributed even for absorber units with asymmetric flow fields, which in this context means flow fields that do not have circular or quadratic symmetry because the maximum width is less than the maximum length of the flow field.

[0032] Absorber units with asymmetric flow areas offer more versatility for the placement of the coolers: the flow area required for cooling can be realized in a narrow enough width to fit into the available space around the engine and / or between the engine and the engine room walls.

[0033] The pre-cooling injection tube, the outflow tube, the absorber unit, the inflow deflector housing and the outflow deflector housing are preferably separate structural parts, and each of these structural parts can be combined in a selectable orientation relative to each other, as long as the exhaust gas flows first through the pre-cooling injection tube, then through the inflow deflector housing, through the absorber unit, through the outflow deflector housing and finally through the outflow tube. Thus, the exhaust gas cooling device can be adapted to specific space conditions.

[0034] The precooling jet tubes, inlet deflector housing, outlet deflector housing, absorber unit walls, and outlet tubes may be made from stainless steel or galvanized steel to withstand acidic cooling water. Wall thickness may be 3-8mm.

[0035] Alternatively, the walls can also be made of synthetic materials that can withstand temperatures up to 100°C.

[0036] The absorber unit may comprise at least one unitary absorber, and preferably comprises at least two unitary absorbers arranged in parallel along the length of the absorber unit.

[0037] The total flow area of ​​an absorber unit is determined by the flow area of ​​a single absorber.

[0038] A unitary absorber typically has a closed wall.

[0039] Several single absorbers in parallel may be of the same functional type and / or of the same shape, preferably cylindrical, each with the same flow area and the same height.

[0040] The height can range from 0.5 to 5 m, the length from 2 to 10 m, and the diameter from 0.5 to 3 m.

[0041] In the case of several elementary absorbers arranged in parallel, the width of the absorber unit is typically given by the width of an elementary absorber, and the length of the absorber unit is given by the sum of the lengths of the several elementary absorbers and the distance between the elementary absorbers.

[0042] The unitary absorber may have a cylindrical shape with a rectangular flow area.

[0043] Several unitary absorbers arranged in parallel may each have a cylindrical shape with a circular or rectangular flow area.

[0044] The unitary absorber may have any flow field shape, for example an ellipse, so long as the width of the absorber unit is less than the length of the absorber unit.

[0045] A rectangular flow area can provide a larger flow area in the absorber unit, whereas a circular or elliptical flow area can improve the pressure resistance, which may be necessary if a misfire occurs in the cylinder and the pressure in the cooler rises to 0.5 bar.

[0046] The absorber unit, and in particular each individual absorber, may comprise a cooling layer, which may comprise a rolled sheet or strip of stainless steel provided as a bulk material, stainless steel typically being resistant to any corrosive pollutants that may be contained in the exhaust gases.

[0047] The exhaust gases are able to flow through the bulk material and give up their heat to the rolled sheet.

[0048] At least one water nozzle is disposed in the pre-cooled injection tube. The nozzle is preferably disposed to spray an inner wall of the pre-cooled injection tube. Thus, exhaust gases flowing through the tube give up heat to the tube, which is cooled by the water.

[0049] The exhaust gas can preferably be cooled from a temperature of about 230° C.-280° C. to a temperature of about 80° C.-90° C. along the pre-cooling injection tube, the length of which depends on the cooling capacity and is preferably equal to or greater than the height of the absorber unit.

[0050] The pre-cooling injection tubes preferably have a J-shape to direct the exhaust gases and channel the cooling water. The pre-cooling injection tubes and the outlet tube typically have a circular cross section.

[0051] Its diameter is preferably equal to the width of the absorber unit.

[0052] The opening diameter of the tapered inlet deflector housing decreases along the exhaust gas flow path so that the pressure remains approximately constant along the length of the absorber unit while more exhaust preferably exits the inlet deflector housing into the absorber unit.

[0053] A similar amount of exhaust gas may be directed to each of the parallel single absorbers.

[0054] The opening diameter of the tapered outlet deflector housing preferably decreases in the opposite direction of the exhaust gas flow path, i.e. increases along the exhaust gas flow path, so that the pressure remains approximately constant along the length of the absorber unit while more exhaust is applied from the absorber unit to the outlet deflector housing.

[0055] Preferably, the inlet deflector housing is arranged below the absorber unit and / or the outlet deflector housing is arranged above the absorber unit, so that the exhaust gas flows through the absorber unit from bottom to top. This is particularly advantageous if cooling water is provided in the absorber unit.

[0056] The absorber unit may comprise at least one water spray nozzle. Preferably, the absorber unit comprises several individual absorbers arranged in parallel and at least one water spray nozzle for each individual absorber.

[0057] The spray nozzles are preferably arranged above the cooling layer and directed towards it. The cooling layer, which absorbs heat from the exhaust gases, is thus cooled by water. The temperature of the cooling water allows the exhaust gases to be sufficiently cooled. In particular, the spray nozzles are arranged not directed towards the walls of the absorber unit, since in this case the cooling water flows away from the walls. The exhaust gases can be cooled in the absorber unit from a temperature of 80-90°C to a temperature of 30-35°C.

[0058] The spray nozzle preferably produces a rain-like water shower with droplets of 1-2 mm in diameter.

[0059] The multiple spray nozzles may be connected by a common rail, which may branch off from a water supply pipe that also supplies cooling water to the pre-cooling injection tubes.

[0060] The outflow tube may include a demister which reduces the size of water droplets contained in the exhaust gases, preferably to a diameter of less than 40 microns.

[0061] The cooling water return line may be connected to the inflow deflector housing, preferably at its lowest point. A tapered configuration of the inflow deflector housing may guide the water into the cooling water return line.

[0062] The cooling water from the pre-cooling jet tubes and absorber unit can be collected in the inflow deflector housing and can be guided to the cooling water return line.

[0063] The cooling water return line may be fluidly connected to a circulating water tank. The circulating water may be brought to a suitable temperature, in particular cooled, and / or cleaned, and may be used again as cooling water for the pre-cooling jet tubes and / or the absorber unit.

[0064] According to the invention, the internal combustion engine, i.e. marine or stationary engine, is preferably a two-stroke engine or a two-stroke cross-head engine. The internal combustion engine comprises at least one cylinder having an inner diameter of at least 200 mm.

[0065] The present internal combustion engine is equipped with the above-mentioned exhaust gas cooling device.

[0066] The internal combustion engine preferably comprises at least one turbocharger, the turbocharger comprising a turbine and a compressor.

[0067] The internal combustion engine may further include a system for exhaust gas recirculation having at least a low pressure EGR path fluidly disposed between an exhaust outlet and an air inlet of the cylinder. The low pressure EGR path may allow exhaust gases to be guided through a turbine of the turbocharger. At least a portion of the exhaust gases may be guided through a compressor of the turbocharger to the air inlet of the cylinder. The exhaust gas cooling device may be disposed in the low pressure EGR path between the turbine and the compressor.

[0068] The exhaust gas cooling device may be mounted on the cylinder jacket and / or on the engine frame and / or on the engine platform.

[0069] The cylinder jacket is the retaining structure for the cylinder. The engine platform is connected to the cylinder jacket. The cylinder jacket, engine frame, and engine platform are usually made from cast iron to give stability.

[0070] Thus, the exhaust gas cooling system may be mounted "on the engine itself" rather than being part of the ship or engine house.

[0071] Further advantageous aspects of the invention are explained below by means of exemplary embodiments and figures, in which: The figures are shown diagrammatically. [Brief description of the drawings]

[0072] [Figure 1] 1 is a schematic diagram of an internal combustion engine. [Diagram 2] FIG. 2 is a first schematic side view of a first example of an exhaust gas cooling device; [Diagram 3] FIG. 2 is a second schematic side view of the first example of an exhaust gas cooling device. [Figure 4] FIG. 1 is a schematic perspective view of a first example of an exhaust gas cooling device; [Diagram 5] FIG. 2 is a schematic perspective view of a second example of an exhaust gas cooling device; [Figure 6] FIG. 13 is a schematic perspective view of a third example of an exhaust gas cooling device. [Figure 7] FIG. 13 is a schematic perspective view of a fourth example of an exhaust gas cooling device. [Figure 8] FIG. 2 is a first schematic perspective view of a first example of an internal combustion engine having a second example of an exhaust gas cooling device; [Figure 9] FIG. 2 is a second schematic perspective view of the first example of an internal combustion engine. [Figure 10] FIG. 2 is a first schematic perspective view of a second example of an internal combustion engine having a second example of an exhaust gas cooling device; [Figure 11] FIG. 2 is a second schematic perspective view of a second example of an internal combustion engine. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0073] FIG. 1 is a schematic diagram of an internal combustion engine 100 .

[0074] The internal combustion engine 100 comprises at least one cylinder 101 having an inner diameter 102 of at least 200 mm.

[0075] The internal combustion engine 100 comprises a turbocharger 103 having a turbine 104 and a compressor 105. The internal combustion engine 100 further comprises a system 106 for exhaust gas recirculation (EGR) having a low pressure EGR path 107 fluidly arranged between an exhaust outlet 108 and an air inlet 109 of the cylinder 101. The exhaust gases are guided via the turbine 104 of the turbocharger 103. A part of the exhaust gases is guided to the air inlet 109 of the cylinder 101 through a compressor 105 of the turbocharger 103, which also draws in fresh air FA.

[0076] Fresh air or a mixture of fresh air and recirculated exhaust gas is directed to the scavenge air receiver 110. When the reciprocating piston is in the low position, fresh air or a mixture of fresh air and recirculated exhaust gas can enter the cylinder 101.

[0077] An EGR valve 112 is disposed in the EGR path 107. The pressure within the EGR path 107 may be regulated by a backpressure valve 113.

[0078] The exhaust gas cooling device 1 is disposed in the low pressure EGR path 107, downstream of the EGR valve 112 in this example.

[0079] FIG. 2 shows a first schematic side view of a first example of an exhaust gas cooling device 1 .

[0080] The exhaust gas cooling device 1 comprises a J-shaped pre-cooling injection tube 2. Two water nozzles 8 are arranged in the pre-cooling injection tube 2. The exhaust gas cooling device 1 comprises an outflow tube 3 having a demister 12. The exhaust gas cooling device 1 further comprises an absorber unit 4.

[0081] Exhaust gas enters the pre-cooling injection tube 2 of the exhaust gas cooler 1 , passes through an absorber unit 4 and exits the exhaust gas cooler 1 after passing through an outlet tube 3 .

[0082] The absorber unit 4 has a height h, a maximum width w (see FIG. 6) and a maximum length l, the maximum length l being greater than the maximum width w.

[0083] The exhaust gas cooling system 1 comprises a tapered inlet deflector housing 6 along the length l of the absorber unit 4, the inlet deflector housing 6 being fluidly connected to the pre-cooling injection tubes 2 and the absorber unit 4. The tapered inlet deflector housing 6 has a vertical opening diameter 14 which decreases along the exhaust gas flow path.

[0084] In this example, the outlet end 16 of the pre-cooling injection tube 2 is widened to connect to the absorber unit 4. The lowest point of the system is connected to the cooling water return system.

[0085] The exhaust gas cooling device 1 includes a tapered outlet deflector housing 7 along the length l of the absorber unit 4. The outlet deflector housing 7 is fluidly connected to the absorber unit 4 and the outlet tube 3. The tapered outlet deflector housing 7 has a vertical opening diameter 15 that decreases in the direction opposite the exhaust gas flow path. The opening diameter 15 increases along the exhaust gas flow path.

[0086] An inlet deflector housing 6 is disposed below the absorber unit 4 and an outlet deflector housing 7 is disposed above the absorber unit 4 .

[0087] The absorber unit 4 comprises four individual absorbers 5 arranged in parallel along the length l of the absorber unit 4 .

[0088] Each single absorber 5 is provided with a cooling layer 9. For each single absorber 5, a water spray nozzle 10 is arranged for spraying water into the cooling layer 9. The water spray nozzles 10 are connected by a common rail 11.

[0089] A cooling water return line 13 for collecting the cooling water of the absorber unit 4 and the pre-cooling injection tubes 2 is connected to the inlet deflector housing 6 at its lowest point.

[0090] 3 is a second schematic side view of the first example of the exhaust gas cooling device 1. The exhaust gas cooling device 1 is of slender design with several single absorbers having a narrow width 2 so that the exhaust gas cooling device 1 can be placed between the internal combustion engine 100 and the wall of the engine room (not shown).

[0091] 4 is a schematic perspective view of a part of a first example of an exhaust gas cooling device 1. The exhaust gas cooling device 1 comprises four unitary absorbers 5 with circular flow areas.

[0092] The tapered inlet deflector housing 6 and the tapered outlet deflector housing 7 are oriented such that the pre-cool injection tube 2 and the outlet tube 3 are positioned adjacent to one another.

[0093] 5 is a schematic perspective view of a second example of an exhaust gas cooling device 1. The tapered inlet deflector housing 6 and the tapered outlet deflector housing 7 are oriented such that the pre-cooling injection tubes 2 and the outlet tubes 3 are located on opposite sides of the absorber unit 4.

[0094] 6 is a schematic perspective view of a third example of an exhaust gas cooling device 1. The absorber unit 4, having a height h, a length l and a width w, comprises only one single absorber 5 with a rectangular flow area.

[0095] 7 is a schematic perspective view of a fourth example of an exhaust gas cooling device 1. The absorber unit 4 comprises two individual absorbers 5 arranged in parallel, each with a rectangular flow area.

[0096] FIG. 8 is a first schematic perspective view of a part of a first example of an internal combustion engine 100 having a second example of an exhaust gas cooling device 1 .

[0097] Figure 9 is a second schematic perspective view of a part of a first example of an internal combustion engine 100. The exhaust gas cooling device 1 is fixed at the free or driving end of the engine to the engine platform or by a support to the engine housing, the length l of the absorber unit 4 (see Figure 8) being oriented transverse to the direction 17 of the crankshaft of the engine.

[0098] FIG. 10 is a first schematic perspective view of a part of a second example of an internal combustion engine 100 having a second example of an exhaust gas cooling device 1 .

[0099] Figure 11 is a second schematic perspective view of a part of a second example of an internal combustion engine 100. The second example of the exhaust gas cooling device 1 is arranged on the long side of the engine 1 near the turbocharger unit, with the length l of the absorber unit 4 oriented along the crankshaft direction 17 (see Figure 10). The exhaust gas cooling device 1 may be mounted on a platform 111 or by supports (not explicitly shown) of the engine housing.

Claims

1. Pre-cooling injection tube (2), Outlet tube (3), An absorber unit (4) having a height (h), a maximum width (w), and a maximum length (l), wherein the maximum length (l) is longer than the maximum width (w), The inlet deflector housing (6) is tapered along the length (l) of the absorber unit (4) and is fluidly connected to the precooling injection tube (2) and the absorber unit (4), The outlet deflector housing (7) is tapered along the length (l) of the absorber unit (4) and is fluidly connected to the absorber unit (4) and the outlet tube (3). An exhaust gas cooling system (1) for a large internal combustion engine (100) equipped with the following.

2. The exhaust gas cooling device (1) according to claim 1, wherein the absorber unit comprises at least one standalone absorber (5).

3. The exhaust gas cooling device (1) according to claim 2, wherein the absorber unit comprises at least two individual absorbers (5) arranged in parallel along the length (l) of the absorber unit.

4. The exhaust gas cooling device (1) according to claim 2, wherein one of the absorbers (5) has a rectangular flow region, or several individual absorbers (5) arranged in parallel have a circular flow region.

5. The exhaust gas cooling device (1) according to claim 1, wherein at least one water nozzle (8) is arranged in the precooling injection tube (2).

6. The exhaust gas cooling device (1) according to claim 1, wherein the precooling injection tube (2) is J-shaped.

7. The exhaust gas cooling device (1) according to claim 1, wherein the opening diameter (14) of the tapered inlet deflector housing (6) decreases along the flow path of the exhaust gas.

8. The exhaust gas cooling device (1) according to claim 1, wherein the opening diameter (15) of the tapered outlet deflector housing (7) is smaller in the direction opposite to the flow path of the exhaust gas.

9. The exhaust gas cooling device (1) according to claim 1, wherein the inlet deflector housing (6) is positioned below the absorber unit (4), and / or the outlet deflector housing (7) is positioned above the absorber unit (4).

10. The exhaust gas cooling device (1) according to claim 1, wherein the absorber unit (4) comprises a cooling layer (9).

11. The exhaust gas cooling device (1) according to claim 1, wherein the absorber unit (4) comprises at least one water spray nozzle (10).

12. The exhaust gas cooling device (1) according to claim 11, wherein the water spray nozzle (10) is connected by a common rail (11).

13. The exhaust gas cooling device (1) according to claim 11, wherein the absorber unit (4) comprises several individual absorbers and at least one water spray nozzle for each individual absorber.

14. The exhaust gas cooling device (1) according to claim 1, wherein the outlet tube (3) is equipped with a demister (12).

15. The exhaust gas cooling device (1) according to claim 1, wherein the cooling water return line (13) is connected to the inlet deflector housing (6).

16. An internal combustion engine (100), i.e., a large marine engine or a stationary engine, comprising at least one cylinder (101) having an inner diameter (102) of at least 200 mm, and equipped with the exhaust gas cooling device (1) described in claim 1.

17. The internal combustion engine (100) according to claim 16, wherein the internal combustion engine (100) comprises at least one turbocharger (102), the turbocharger (103) comprises a turbine (104) and a compressor (105), the internal combustion engine (100) further comprises an exhaust gas recirculation system (106) having at least a low-pressure EGR path (107) fluidly arranged between the exhaust outlet (108) and the air inlet (109) of the cylinder (101), the exhaust gas being guided through the turbine (104) of the turbocharger (103), at least a portion of the exhaust gas being guided through the compressor (105) of the turbocharger (103) to the air inlet (109) of the cylinder (101), and the exhaust gas cooling device (1) being arranged in the low-pressure EGR path (107).

18. The internal combustion engine (100) according to claim 17, wherein the exhaust gas cooling device (1) is attached to at least one of the cylinder jacket, engine frame, and engine platform.

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