Cooling device for internal combustion engine

Abstract

To provide a cooling device for an internal combustion engine capable of actively cooling an exhaust member by using travel wind passing through a fan shroud to lower a surface temperature of the exhaust member and of extending a thermal fatigue life of the exhaust member.SOLUTION: A radiator 12 includes: a radiator fan 14 provided on a front side of an engine 3 having an exhaust member 8 in which exhaust gas flows; and a cylindrical fan shroud 16 that surrounds the radiator fan 14. The fan shroud 16 has a plurality of opening parts 17 through which travel wind passes, and the opening parts 17 are partitioned by a plurality of support columns 16C extending in a radial direction of a cylindrical part 16A. A guide member 18 is provided in one of the plurality of the opening parts 17. The guide member 18 guides the travel wind to upstream sides of upstream side piping 9 located in an upstream part of the exhaust member 8 and a catalyst case 10.SELECTED DRAWING: Figure 2

Description

[Technical field]

[0001] The present invention relates to a cooling device for an internal combustion engine. [Background technology]

[0002] 2. Description of the Related Art Conventionally, there is known a radiator fan shroud in which an exhaust manifold is disposed on the vehicle rear side of the fan shroud attached to the rear of the radiator (see Patent Document 1).

[0003] In order to protect the fan shroud of the radiator described in Patent Document 1 from heat damage from the exhaust manifold (exhaust member), a heat shield plate is attached to the back side of the fan shroud and includes a base portion that partially covers the air flow window of the fan shroud and a heat shield portion that is formed integrally with the base portion, protrudes radially outward from the air flow window, and covers the front side of the exhaust manifold.The heat shield plate has an air guide port that deflects the passing air blowing against the base portion at approximately a right angle by the air flow window and leads it to the alternator. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Patent No. 4064685 Summary of the Invention [Problem to be solved by the invention]

[0005] However, the fan shroud of a conventional radiator is designed to protect the fan shroud from the exhaust members, and is not designed to actively cool the exhaust members by utilizing the fan shroud.

[0006] The surface of the exhaust manifold becomes very hot because hot exhaust gas flows through it immediately after combustion in the engine. Therefore, it is desirable to actively cool the exhaust manifold to lower the surface temperature of the exhaust manifold and improve the thermal fatigue life of the exhaust manifold.

[0007] The present invention has been made in response to the above-mentioned problems, and aims to provide a cooling device for an internal combustion engine that can actively cool the exhaust members using the running wind passing through the fan shroud, thereby lowering the surface temperature of the exhaust members and extending the thermal fatigue life of the exhaust members. [Means for solving the problem]

[0008] The present invention is a cooling device for an internal combustion engine comprising a radiator fan provided in front of an internal combustion engine having an exhaust member through which exhaust gas flows, and a fan shroud having a cylindrical portion surrounding the radiator fan, the fan shroud having a plurality of openings through which air flows when the engine is traveling, the openings being separated by a plurality of struts extending radially of the cylindrical portion, and a guide member is provided in at least one of the plurality of openings, and the guide member guides the air flows toward an upstream portion of the exhaust member in the flow direction of the exhaust gas. Effect of the Invention

[0009] As described above, according to the present invention, the exhaust member can be actively cooled by the traveling wind passing through the fan shroud, thereby lowering the surface temperature of the exhaust member, and the thermal fatigue life of the exhaust member can be extended. [Brief description of the drawings]

[0010] [Figure 1] FIG. 1 is a plan view of an engine room of a vehicle according to an embodiment of the present invention. [Diagram 2] FIG. 2 is a front view of an internal combustion engine and a cooling device according to one embodiment of the present invention. [Diagram 3] FIG. 3 is a rear view of the radiator and exhaust member according to one embodiment of the present invention. [Figure 4] FIG. 4 is an enlarged view of a guide member and a radiator portion in the vicinity thereof according to an embodiment of the present invention. [Diagram 5]FIG. 5 is an enlarged rear view of a guide member according to an embodiment of the present invention. [Figure 6] FIG. 6 is a plan view of an internal combustion engine and a cooling device for comparison with an internal combustion engine and a cooling device according to an embodiment of the present invention, showing an example in which the inclined wall is extended. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0011] A cooling device for an internal combustion engine in one embodiment of the present invention comprises a radiator fan provided in front of an internal combustion engine having an exhaust member through which exhaust gas flows, and a fan shroud having a cylindrical portion surrounding the radiator fan, the fan shroud having a plurality of openings through which air flows while the engine is traveling, the openings being separated by a plurality of struts extending radially of the cylindrical portion, and a guide member is provided in at least one of the plurality of openings, and the guide member guides the air flows toward an upstream portion of the exhaust member in the flow direction of the exhaust gas.

[0012] As a result, the cooling device for an internal combustion engine according to one embodiment of the present invention can actively cool the exhaust members using the running wind passing through the fan shroud, thereby lowering the surface temperature of the exhaust members and extending the thermal fatigue life of the exhaust members. EXAMPLES

[0013] DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, an embodiment of a cooling device for an internal combustion engine according to the present invention will be described with reference to the drawings. 1 to 6 are diagrams showing a cooling device for an internal combustion engine according to one embodiment of the present invention.

[0014] 1 to 6, the up / down, front / rear, left / right directions are defined as the front / rear direction of the vehicle based on the engine disposed in the vehicle, with the side where the radiator is disposed being the front and the side where the engine is disposed being the rear.

[0015] The left-right direction of the vehicle (vehicle width direction) is defined as the left-right direction, with the radiator side defined as the left and the engine side defined as the right. The height direction of the engine is defined as the up-down direction, with the cylinder head side defined as the top and the oil pan side defined as the bottom.

[0016] First, the configuration will be described. As shown in FIG. 1, an engine room 2 is provided in the front part of a vehicle 1, and an engine 3 serving as an internal combustion engine is provided in the engine room 2.

[0017] In FIG. 2, the engine 3 includes a cylinder block 4, a cylinder head 5, a cylinder head cover 6, and an oil pan .

[0018] The cylinder block 4 is provided with a plurality of cylinders (not shown), and the cylinders are arranged in a row in the front-to-rear direction of the engine 3. Each cylinder houses a piston (not shown), and the pistons are connected to a crankshaft (not shown) via a connecting rod (not shown).

[0019] The piston reciprocates within the cylinder, thereby rotating the crankshaft via the connecting rod.

[0020] The cylinder head 5 is attached to the upper part of the cylinder block 4, and is formed with a plurality of intake ports (not shown) and a plurality of exhaust ports (not shown).

[0021] The intake port and exhaust port are connected to the cylinders. The intake port introduces intake air into the cylinder, and the exhaust port discharges exhaust gas from the cylinder.

[0022] An exhaust member 8 is connected to the front side of the cylinder head 5. The exhaust member 8 has an upstream piping 9 whose upstream end is connected to the cylinder head 5, a catalyst case 10 connected to the downstream end of the upstream piping 9, and a downstream piping 11 connected to the downstream end of the catalyst case 10.

[0023] Here, upstream and downstream refer to the upstream and downstream in the direction in which exhaust gas flows. For example, the upstream pipe 9 is located upstream of the catalyst case 10, and the catalyst case 10 is located downstream of the upstream pipe 9.

[0024] An exhaust manifold (not shown) is formed inside the cylinder head 5 at the front of the cylinder head 5, and exhaust gas discharged from the exhaust ports is collected by the exhaust manifold and then discharged to the upstream piping 9.

[0025] A three-way catalyst is provided inside the catalyst case 10. The three-way catalyst purifies the exhaust gas by oxidizing carbon monoxide and unburned hydrocarbons contained in the exhaust gas and converting them into carbon dioxide (CO2) and water vapor (H2O), and by reducing nitrogen oxides and converting them into nitrogen (N2).

[0026] Exhaust gas purified in the catalyst case 10 is discharged to the downstream pipe 11. An exhaust pipe (not shown) is connected to the downstream end of the downstream pipe 11, and the exhaust gas discharged from the downstream pipe 11 to the exhaust pipe is discharged to the atmosphere by the exhaust pipe.

[0027] As shown in Fig. 1, a radiator 12 is disposed on the left front side of the engine 3. As shown in Fig. 3, the radiator 12 includes a radiator body 13, a radiator fan 14, a fan motor 15, and a fan shroud 16. The radiator 12 in this embodiment constitutes a cooling device.

[0028] The radiator body 13 has an upper tank 13A provided at the top, a lower tank 13B provided at the bottom, and a radiator core 13C (the radiator core is arranged in front of the fan shroud 16) provided between the upper tank 13A and the lower tank 13B in the vertical direction.

[0029] Radiator core 13C is configured by alternately stacking flat water tubes (not shown). Radiator core 13C cools the coolant by exchanging heat between the coolant flowing from upper tank 13A through the water tubes and the outside air, and introduces the cooled coolant into lower tank 13B.

[0030] The fan shroud 16 is attached to the rear of the radiator body 13. The fan shroud 16 has a cylindrical portion 16A that surrounds the radiator fan 14, and a fan motor 15 that drives the radiator fan 14 to rotate.

[0031] The fan shroud 16 draws air generated by traveling from the front of the vehicle 1 into the radiator core 13C by the rotating radiator fan 14. The air that has exchanged heat with the cooling water flowing through the radiator core 13C is exhausted rearward by the radiator fan 14.

[0032] As shown in Figures 2 and 3, the fan shroud 16 has an annular motor mounting portion 16B on which the fan motor 15 is mounted, and a plurality of pillars 16C extending radially from the motor mounting portion 16B in the radial direction of the fan shroud 16 and having their radial outer ends connected to the cylindrical portion 16A.

[0033] A radially inner end of the support column 16C is connected to the motor attachment portion 16B, and the fan motor 15 is supported by the support column 16C via the motor attachment portion 16B.

[0034] Openings 17 are formed between adjacent supports 16C in the circumferential direction of cylindrical portion 16A. In other words, openings 17 are partitioned by supports 16C. Since supports 16C extend radially, openings 17 have a gradually increasing circumferential opening area from the inner end side toward the outer end side in the radial direction of cylindrical portion 16A.

[0035] Further, the radiator fan 14 is formed such that the blade area increases in the circumferential direction from the inner end side to the outer end side in the radial direction of the cylindrical portion 16A.

[0036] Here, the radially inner end of the cylindrical portion 16A is the rotation center 14a of the radiator fan 14, and the radially outer end of the cylindrical portion 16A is the cylindrical portion 16A.

[0037] The fan shroud 16 is provided with a guide member 18. The guide member 18 is provided in one of the plurality of openings 17.

[0038] 2, the guide member 18 is disposed along the radial direction of the opening 17 (the radial direction of the cylindrical portion 16A) when viewed from the front of the vehicle 1. In other words, the guide member 18 covers a part of the opening 17 in the radial direction of the cylindrical portion 16A.

[0039] 1 and 2, the guide member 18 has an inclined wall 18A, an upper side wall 18B, and a lower side wall 18C. In this embodiment, the inclined wall 18A constitutes an inclined portion, and the upper side wall 18B and the lower side wall 18C constitute a pair of side wall portions.

[0040] The inclined wall 18A is inclined so as to move away from the support pillar 16C from the rotation center 14a side of the radiator fan 14 toward the cylindrical portion 16A side. In other words, the inner end 18b of the inclined wall 18A is located closer to the support pillar 16C than the outer end 18a, and the outer end 18a of the inclined wall 18A is located farther from the support pillar 16C than the inner end 18b.

[0041] The upper side wall 18B connects the support pillar 16C to the upper end of the inclined wall 18A, and the lower side wall 18C connects the support pillar 16C to the lower end of the inclined wall 18A. In other words, the upper side wall 18B and the lower side wall 18C connect the adjacent support pillar 16C to the inclined wall 18A.

[0042] As shown in FIG. 1, the exhaust member 8 is located on an extension surface 30 of the inclined wall 18A, and as shown in FIG. 2, the extension surface 30 passes through the upstream pipe 9 and the upstream side of the catalyst case 10.

[0043] That is, the upstream pipe 9 located on the upstream side of the exhaust member 8 and the upstream side of the catalyst case 10 are located on the extension surface 30 of the inclined wall 18A.

[0044] As a result, a portion of the traveling wind passing through the opening 17 is guided by the guide member 18 to the upstream pipe 9 and the upstream side of the catalyst case 10 .

[0045] An outer end 18a of the inclined wall 18A is located closer to the rotation center 14a of the radiator fan 14 than the cylindrical portion 16A.

[0046] The opening 17 has an outer opening 17A located closer to the cylindrical portion 16A than the outer end 18a of the inclined wall 18A, and an inner opening 17B located closer to the rotation center 14a of the radiator fan 14 than the inner end 18b of the inclined wall 18A.

[0047] The outer opening 17A has a larger opening area than the inner opening 17B, and the inclined wall 18A gradually expands in diameter in the circumferential direction of the cylindrical portion 16A from the side of the rotation center 14a of the radiator fan 14 toward the cylindrical portion 16A.

[0048] 4, the upper side wall 18B includes an extension wall portion 18c, and the lower side wall 18C includes an extension wall portion 18d. The extension walls 18c and 18d in this embodiment form extensions.

[0049] Specifically, when an imaginary straight line 31 is set that is perpendicular to the extension direction of the support 16C and passes through the outer end 18a of the inclined wall 18A and the connecting portion 18m of the upper side wall 18B, and an imaginary straight line 31 that is perpendicular to the extension direction of the support 16C and passes through the outer end 18a of the inclined wall 18A and the connecting portion 18n of the lower side wall 18C, the extended wall portions 18c, 18d extend from the imaginary straight line 31 toward the cylindrical portion 16A.

[0050] Next, the effects of the radiator 12 of this embodiment will be described. The radiator 12 of this embodiment includes a radiator fan 14 provided in front of the engine 3 which includes an exhaust member 8 through which exhaust gas flows, and a fan shroud 16 having a cylindrical portion 16A which surrounds the radiator fan 14.

[0051] As a result, the fan shroud 16 draws in a traveling wind W (see FIG. 1) from the front of the vehicle 1 into the radiator core 13C by the rotating radiator fan 14. The air that has exchanged heat with the cooling water flowing through the radiator core 13C is exhausted rearward by the radiator fan 14.

[0052] The fan shroud 16 has a plurality of openings 17 through which the wind generated during running passes, and the openings 17 are partitioned by a plurality of struts 16C extending in the radial direction of the cylindrical portion 16A.

[0053] A guide member 18 is provided at one of the openings 17, and guides the traveling wind W1 (see FIG. 1) to the upstream pipe 9 located upstream of the exhaust member 8 and to the upstream side of the catalyst case 10.

[0054] This makes it possible to actively cool exhaust member 8 and reduce the surface temperature of exhaust member 8. As a result, the thermal fatigue life of exhaust member 8 can be extended.

[0055] In addition, since the wind generated by running is guided to the upstream piping 9 of the exhaust member 8 through which high-temperature exhaust gas flows immediately after combustion in the engine 3, the upstream piping 9, which is the hottest part of the exhaust member 8, can be actively cooled, and the surface temperature of the exhaust member 8 can be more effectively reduced. As a result, the thermal fatigue life of the exhaust member 8 can be more effectively extended.

[0056] Furthermore, according to the radiator 12 of this embodiment, when viewed from the front of the vehicle 1, the guide member 18 is disposed along the radial direction of the cylindrical portion 16A.

[0057] The guide member 18 has an inclined wall 18A that inclines away from the support 16C as it moves from the side of the center of rotation 14a of the radiator fan 14 (the radial inner end side of the cylindrical portion 16A) to the side of the cylindrical portion 16A (the radial outer end side of the cylindrical portion 16A), and an upper side wall 18B and a lower side wall 18C that connect the adjacent support 16C and the inclined wall 18A, and the upstream piping 9 and catalyst case 10 are located on the extension surface 30 of the inclined wall 18A.

[0058] This allows the traveling wind passing through opening 17 to be more effectively guided to upstream piping 9 by inclined wall 18A, and more effectively cools exhaust member 8. As a result, the surface temperature of exhaust member 8 can be more effectively reduced, and the thermal fatigue life of exhaust member 8 can be more effectively extended.

[0059] Here, when the vehicle 1 is running normally, the swirling flow of the radiator fan 14 causes the running wind passing through the opening 17 to flow so as to spread outward in the radial direction of the cylindrical portion 16A.

[0060] In addition, since the blade area of ​​the radiator fan 14 is increased in the circumferential direction from the rotation center 14a side of the radiator fan 14 toward the cylindrical portion 16A side, the circumferential speed of the radiator fan 14 on the cylindrical portion 16A side is greater than the circumferential speed on the rotation center 14a side.

[0061] As a result, the amount of air generated by the rotation of the radiator fan 14 increases from the rotation center 14a toward the cylindrical portion 16A.

[0062] According to the radiator 12 of this embodiment, when viewed from the front of the vehicle 1, the inclined wall 18A covers a part of the opening 17 in the radial direction of the cylindrical portion 16A.

[0063] Therefore, as shown in Figure 6, if the inclined wall 18A is extended to the cylindrical portion 16A, the running wind passing through the opening 17 will collide with the extended portion of the inclined wall 18A and diffuse, as shown by the running wind W2, making it difficult to efficiently guide it to the upstream piping 9.

[0064] According to the radiator 12 of this embodiment, the outer end 18a of the inclined wall 18A is located closer to the center of rotation 14a of the radiator fan 14 than the cylindrical portion 16A, and the opening 17 has an outer opening 17A closer to the cylindrical portion 16A than the outer end 18a of the inclined wall 18A.

[0065] This prevents the wind generated by radiator fan 14 from being obstructed by inclined wall 18A, and prevents the wind from being diffused by inclined wall 18A.

[0066] In addition, the traveling wind flowing through the outer opening 17A can be merged with the traveling wind directed toward the upstream piping 9 along the inclined wall 18A (see traveling wind W1 in Figure 1), so that more traveling wind W1 can be guided to the upstream piping 9.

[0067] As a result, the surface temperature of exhaust member 8 can be reduced more effectively, and the thermal fatigue life of exhaust member 8 can be extended more effectively.

[0068] In addition, when viewed from the front of the vehicle 1, the inclined wall 18A covers a portion of the opening 17 in the radial direction of the cylindrical portion 16A, so that the traveling wind passing through the opening 17 collides with the inclined wall 18A, thereby obstructing the flow of the traveling wind passing through the opening 17.

[0069] Therefore, the inclined wall 18A acts as an air resistance to the radiator fan 14, and the amount of airflow drawn by the radiator fan 14 during running is reduced.

[0070] In other words, the larger the installation range of inclined wall 18A relative to opening 17, the greater the air resistance of radiator fan 14, reducing the amount of airflow drawn by radiator fan 14 and deteriorating the cooling performance of radiator 12.

[0071] In addition, the volume of airflow generated by the vehicle during running increases from the center of rotation 14a of the radiator fan 14 toward the cylindrical portion 16A, so the volume of air flowing on the side of the center of rotation 14a of the radiator fan 14 is smaller than the volume of air flowing on the side of the cylindrical portion 16A.

[0072] For these reasons, even if the inner end 18b of the inclined wall 18A is extended to the rotation center 14a of the radiator fan 14, it is not possible to expect an increase in the volume of airflow guided to the exhaust member 8 by the guide member 18. Instead, there is a risk that the volume of air drawn in by the radiator fan 14 will be reduced, thereby degrading the cooling performance of the radiator 12.

[0073] According to the radiator 12 of this embodiment, the opening 17 has an inner opening 17B closer to the rotation center 14a of the radiator fan 14 than the inner end 18b of the inclined wall 18A, so that the radiator fan 14 can direct the wind generated by running through the inner opening 17B.

[0074] Therefore, the air resistance of the radiator fan 14 can be reduced, and the cooling performance of the radiator 12 can be prevented from decreasing.

[0075] In addition, by reducing the air resistance of the radiator fan 14, it is possible to suppress a reduction in the amount of air drawn in by the radiator fan 14, and it is possible to prevent a reduction in the amount of airflow of the traveling wind guided from the outer opening 17A along the inclined wall 18A to the upstream piping 9.

[0076] Therefore, the surface temperature of exhaust member 8 can be reduced more effectively, and the thermal fatigue life of exhaust member 8 can be extended more effectively.

[0077] Furthermore, according to the radiator 12 of this embodiment, the outer opening 17A has a larger opening area than the inner opening 17B, so that more of the running wind can be guided from the cylindrical portion 16A side of the radiator fan 14, where the air volume increases, to the exhaust member 8 through the outer opening 17A having a larger opening area.

[0078] As a result, the surface temperature of exhaust member 8 can be reduced more effectively, and the thermal fatigue life of exhaust member 8 can be extended more effectively.

[0079] In addition, according to the radiator 12 of this embodiment, when an imaginary straight line 31 is set that is perpendicular to the extension direction of the support 16C and passes through the connecting portions 18m, 18n between the outer end of the inclined wall 18A and the side wall portions, the upper side wall 18B and the lower side wall 18C have extended wall portions 18c, 18d that extend from the imaginary straight line 31 toward the cylindrical portion 16A of the fan shroud 16.

[0080] This makes it possible to prevent the traveling wind that has passed through the outer opening 17A from being diffused in the circumferential direction of the cylindrical portion 16A.

[0081] Specifically, if the upper side wall 18B and the lower side wall 18C do not have the extended wall portions 18c, 18d extending from the imaginary straight line 31 toward the cylindrical portion 16A of the fan shroud 16, the outer ends of the upper side wall 18B and the lower side wall 18C will be collinear with the imaginary straight line 31.

[0082] In this case, there is a risk that the wind passing through the outer opening 17A will be diffused in the circumferential direction of the cylindrical portion 16A from the outer ends of the upper side wall 18B and the lower side wall 18C that are on the same line as the imaginary straight line 31.

[0083] According to the radiator 12 of this embodiment, the upper side wall 18B and the lower side wall 18C have extension wall portions 18c, 18d that extend from the imaginary straight line 31 toward the cylindrical portion 16A.

[0084] As a result, as shown in FIG. 5, it is possible to prevent the traveling wind W1 that has passed through the outer opening 17A from colliding with the extension wall portions 18c, 18d and diffusing in the circumferential direction of the fan shroud 16, and it is possible to guide a larger amount of the traveling wind along the upper side wall 18B and the lower side wall 18C to the exhaust member 8.

[0085] As a result, the surface temperature of exhaust member 8 can be reduced more effectively, and the thermal fatigue life of exhaust member 8 can be extended more effectively.

[0086] Although the guide member 18 in this embodiment is provided at one opening 17 of the fan shroud 16, the number is not limited to one.

[0087] Although an embodiment of the invention has been disclosed, it will be apparent to one skilled in the art that modifications may be made without departing from the spirit and scope of the invention, and all such modifications and equivalents are intended to be encompassed by the following claims. [Explanation of symbols]

[0088] 3...engine (internal combustion engine), 8...exhaust member, 12...radiator (cooling device), 14...radiator fan, 16...fan shroud, 16A...cylindrical portion, 16C...support, 17...opening, 17A...outer opening, 17B...inner opening, 18...guide member, 18A...inclined wall (inclined portion), 18a...outer end (outer end of inclined portion), 18B...upper side wall (side wall portion), 18b...inner end (inner end of inclined portion), 18C...lower side wall (side wall portion), 18c, 18d...extension wall portion (extension portion), 18m, 18n...connection portion, 30...extension surface, 31...imaginary straight line

Claims

1. The present invention relates to an internal combustion engine having an exhaust member through which exhaust gas flows, and a radiator fan provided in front of the internal combustion engine, and a fan shroud having a cylindrical portion surrounding the radiator fan. The fan shroud has a plurality of openings through which a running wind passes, and the openings are partitioned by a plurality of struts extending in a radial direction of the cylindrical portion, A guide member is provided in at least one of the plurality of openings, The guide member guides airflow from the exhaust member to an upstream portion of the exhaust gas flow direction.

2. When viewed from the front of the vehicle, the guide member is disposed along a radial direction of the opening, The guide member is an inclined portion inclined away from the support column from a radially inner end side to a radially outer end side of the cylindrical portion; a pair of side walls connecting the adjacent support columns and the inclined portions; 2. The cooling device for an internal combustion engine according to claim 1, wherein an upstream portion of said exhaust member is located on an extension surface of said inclined portion.

3. When viewed from the front of the vehicle, the inclined portion covers a part of the opening in a radial direction of the cylindrical portion, a radial outer end of the inclined portion is located closer to an inner end of the cylindrical portion in the radial direction than an outer end of the cylindrical portion in the radial direction, 3. The cooling device for an internal combustion engine according to claim 2, wherein the opening portion has an outer opening portion on a radially outer end side of the cylindrical portion relative to an outer end of the inclined portion.

4. When viewed from the front of the vehicle, the inclined portion covers a part of the opening in a radial direction of the cylindrical portion, 3. The cooling device for an internal combustion engine according to claim 2, wherein the opening has an inner opening located radially inner than a radial inner end of the inclined portion.

5. When viewed from the front of the vehicle, the inclined portion covers a part of the opening in a radial direction of the cylindrical portion, 4. The cooling device for an internal combustion engine according to claim 3, wherein the opening has an inner opening located radially inner than a radial inner end of the inclined portion.

6. 6. The cooling device for an internal combustion engine according to claim 5, wherein the outer opening has an opening area larger than that of the inner opening.

7. When a virtual straight line is set that is perpendicular to the extending direction of the support and passes through each connecting portion between the outer end of the inclined portion and each connecting portion between the pair of side wall portions, 7. The cooling device for an internal combustion engine according to claim 2, wherein the pair of side wall portions have an extension portion that extends from the imaginary straight line toward an outer end side in a radial direction of the cylindrical portion.

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