Mixer and moving body

Abstract

The present invention provides a mixer and a moving body. The mixer (44) is mounted on an aircraft (10). The rear end (78) of the cylindrical portion (74) of the mixer (44) is divided into a plurality of segmented cylindrical portions (80) by guide vanes (90). In the plurality of segmented cylindrical portions (80), a notched nozzle (109) is formed on the outer wall (86) of the cylindrical portion (74). A plurality of guide holes (106) are formed from the outer wall (86) of the cylindrical portion (74) to the rear end face (94) of the guide vanes (90). Accordingly, the output efficiency of the internal combustion engine can be improved.

Description

Technical Field

[0001] This invention relates to a mixer and a moving body. Background Technology

[0002] Japanese Patent Application Publication No. 2005-507044 (PCT International Application) discloses an auxiliary power unit for an aircraft. This auxiliary power unit includes an internal combustion engine, an exhaust pipe, a gas inlet pipe, a radiator, and a mixed robe.

[0003] The exhaust pipe is connected to the internal combustion engine. A gas inlet pipe is connected to the exhaust pipe. The radiator is located on the gas inlet pipe. A mixing shroud is located at the connection between the exhaust pipe and the gas inlet pipe. When the internal combustion engine discharges exhaust gas (first exhaust gas) into the exhaust pipe, the gas inlet pipe draws in outside air as cooling gas through the pressure difference between the first exhaust gas and outside air. The radiator exchanges heat between the cooling oil and the cooling gas introduced into the gas inlet pipe. The cooling oil cools the internal combustion engine. Inside the exhaust pipe, the mixing shroud mixes the first exhaust gas with the used cooling gas (second exhaust gas) after heat exchange. The mixture of the first and second exhaust gases is discharged to the outside through the exhaust pipe. Summary of the Invention

[0004] However, in PCT international application Japanese Publication No. 2005-507044, the first and second exhaust gases are simply combined. A structure that can improve the output efficiency of an internal combustion engine is desired.

[0005] The purpose of this invention is to solve the above-mentioned technical problems.

[0006] A first aspect of the present invention is a mixer that mixes a first exhaust gas from an internal combustion engine and a second exhaust gas from a radiator. The mixer has a cylindrical portion, guide vanes, a notched nozzle, and a plurality of guide holes. The cylindrical portion introduces the first exhaust gas at its front end and discharges it from its rear end. The guide vanes have a plurality of partitions extending radially toward the outer wall of the cylindrical portion, dividing the rear end of the cylindrical portion into a plurality of segmented cylindrical portions. The notched nozzle forms the outer wall of the cylindrical portion and has a notch formed on each of the segmented cylindrical portions. The plurality of guide holes extend from the outer wall of the cylindrical portion to the rear end face of the guide vanes to discharge the second exhaust gas from the rear end face of the guide vanes.

[0007] A second aspect of the present invention is a mobile body having a mixer, an internal combustion engine, an exhaust pipe, a generator, and a radiator as in the first aspect, wherein the exhaust pipe is connected to the internal combustion engine; the generator is connected to the output shaft of the internal combustion engine; the radiator cools the cooling medium by heat exchange between the cooling medium of the generator and the second exhaust gas, and discharges the heat-exchanged second exhaust gas to the exhaust pipe; the mixer is disposed inside the exhaust pipe and mixes the first exhaust gas discharged from the internal combustion engine and the second exhaust gas discharged from the radiator.

[0008] A third aspect of the invention is a mixer that mixes a first exhaust gas from an internal combustion engine and a second exhaust gas from a radiator. The mixer has a cylindrical portion, guide vanes, and a plurality of guide holes. The cylindrical portion introduces the first exhaust gas at its front end and discharges it from its rear end. The guide vanes have a plurality of partitions extending radially toward the outer wall of the cylindrical portion, dividing the rear end of the cylindrical portion into a plurality of segmented cylindrical portions. The plurality of guide holes are formed from the outer wall of the cylindrical portion to the rear end face of the guide vanes to allow gas to pass through the guide vanes. The second exhaust gas is discharged from the rear end face of the blade. The plurality of guide holes have exhaust openings, a plurality of inlet holes, and a plurality of connecting holes. The exhaust openings are formed on the rear end face of the guide blades. The plurality of inlet holes are formed on the outer wall of the cylindrical portion. The plurality of connecting holes are formed on the plurality of partitions and connect the exhaust openings and the plurality of inlet holes. The exhaust openings formed on the rear end faces of the plurality of partitions are narrower as they are closer to the outer wall of the cylindrical portion. The plurality of inlet holes are narrower in the circumferential direction of the cylindrical portion as they are closer to the center of the cylindrical portion.

[0009] A fourth aspect of the present invention is a mobile body having a mixer, an internal combustion engine, an exhaust pipe, a generator, and a radiator as in the third aspect, wherein the exhaust pipe is connected to the internal combustion engine; the generator is connected to the output shaft of the internal combustion engine; the radiator cools the cooling medium by heat exchange between the cooling medium of the generator and the second exhaust gas, and discharges the heat-exchanged second exhaust gas to the exhaust pipe; the mixer is disposed inside the exhaust pipe and mixes the first exhaust gas discharged from the internal combustion engine and the second exhaust gas discharged from the radiator.

[0010] According to the present invention, the output efficiency of an internal combustion engine can be improved.

[0011] The above-described objectives, features, and advantages should be readily understood from the following description of embodiments with reference to the accompanying drawings. Attached Figure Description

[0012] Figure 1 It is a 3D diagram of an aircraft.

[0013] Figure 2 It is a side view showing the internal combustion engine and its surrounding structure.

[0014] Figure 3 This is a structural diagram of an aircraft's power generation system.

[0015] Figure 4 It is a three-dimensional diagram showing the internal combustion engine and its surrounding structure.

[0016] Figure 5 It is a three-dimensional diagram showing the mixer and its surrounding structure.

[0017] Figure 6 This is a rear view showing the mixer and its surrounding structure.

[0018] Figure 7 This is the front view showing the mixer and its surrounding structure.

[0019] Figure 8 This is a side view showing the mixer and its surrounding structure.

[0020] Figure 9 It is a top view showing the mixer and its surrounding structure.

[0021] Figure 10 This is a 3D diagram of a mixer.

[0022] Figure 11 This is the main view of the mixer.

[0023] Figure 12 It is along Figure 8 A cross-sectional view of line XII-XII.

[0024] Figure 13 It is along Figure 8 A cross-sectional view of line XIII-XIII.

[0025] Figure 14 It is along Figure 8 A cross-sectional view of line XIV-XIV. Detailed Implementation

[0026] Figure 1 This is a perspective view of the aircraft 10 (moving body) involved in this embodiment. The aircraft 10 is an electric vertical takeoff and landing (eVTOL) aircraft. In this embodiment, the direction of movement of the aircraft 10 when it moves (flies) in the horizontal direction is described as the forward direction (forward), and the directions of front-back, left-right, and up-down are explained.

[0027] Aircraft 10 has a fuselage 12, a canard 14, a rear wing 16, a pair of boom arms 18, eight takeoff and landing rotors 20, and two cruise rotors 22. The fuselage 12 extends in the longitudinal direction. Therefore, the central axis 24 of the fuselage 12 extends in the longitudinal direction. Aircraft 10 is symmetrical about the vertical plane including the central axis 24.

[0028] The canard 14 is connected to the upper front part of the fuselage 12. The canard 14 generates lift when the aircraft 10 moves forward. A pylon 26 is installed on the upper rear part of the fuselage 12. The rear wing 16 is connected to the upper rear part of the fuselage 12 via the pylon 26. The rear wing 16 generates lift when the aircraft 10 moves forward.

[0029] Two lifting arms 18 are symmetrically arranged about a vertical plane including the central axis 24. Each lifting arm 18 is a rod-shaped component extending from front to rear. The right lifting arm 18 curves to the right (outside the width direction of the aircraft 10). The right lifting arm 18 connects to the canard wing 14 and aft wing 16 on the right side of the fuselage 12. The left lifting arm 18 curves to the left (outside the width direction of the aircraft 10). The left lifting arm 18 connects to the canard wing 14 and aft wing 16 on the left side of the fuselage 12. Alternatively, the two lifting arms 18 could be straight rod-shaped components.

[0030] Eight takeoff and landing rotors 20 are supported by two lifting arms 18. The four right-hand rotors 20 are supported on the upper part of the right-hand lifting arms 18. The four left-hand rotors 20 are supported by the left-hand lifting arms 18. Each of the eight takeoff and landing rotors 20 has multiple blades 28. Each of the eight takeoff and landing rotors 20 generates lift by rotating its multiple blades 28 around an axis 30 extending vertically. The aircraft 10 may have multiple takeoff and landing rotors 20. Each of the multiple takeoff and landing rotors 20 may have more than two blades 28.

[0031] Two cruise rotors 22 are arranged on the left and right sides at the rear end of the fuselage 12. Cylindrical ducts 32 are provided around each of the two cruise rotors 22. Each cruise rotor 22 has multiple blades 34. The two cruise rotors 22 generate thrust by rotating their multiple blades 34 around an axis extending in the longitudinal direction. The aircraft 10 may also have one cruise rotor 22. Alternatively, the aircraft 10 may have three or more cruise rotors 22.

[0032] like Figure 2As shown, multiple internal combustion engines 36 and generators 38 are housed internally at the rear of the fuselage 12. These internal combustion engines 36 and generators 38 are arranged around the perimeter of the pylon 26. The aircraft 10 has three sets of internal combustion engines 36 and generators 38. Alternatively, the aircraft 10 may have one set of internal combustion engines 36 and generators 38. Furthermore, the aircraft 10 may have two sets of internal combustion engines 36 and generators 38. Or, the aircraft 10 may have four or more sets of internal combustion engines 36 and generators 38.

[0033] The internal combustion engine 36 and the generator 38 constitute the power generation system 58 (see reference). Figure 3 It is part of the aircraft 10. The aircraft 10 has multiple power generation systems 58. The power generation systems 58 generate power to drive the takeoff and landing rotor 20 (see reference). Figure 1 The power generation systems 58 supply electricity to the rotor 22 for cruising. All of the multiple power generation systems 58 have identical structures. In the following description, only one of the multiple power generation systems 58 will be described.

[0034] The internal combustion engine 36 is, for example, a gas turbine engine. The internal combustion engine 36 enables the output shaft 40 (see reference) Figure 3 The internal combustion engine 36 is configured to face forward. A generator 38 is positioned in front of the internal combustion engine 36. The output shaft 40 of the internal combustion engine 36 is connected to the main shaft (not shown) of the generator 38.

[0035] An exhaust port 42 is provided at the rear of the internal combustion engine 36 (see reference). Figure 3 The exhaust port 42 is connected to the front end 46 of the mixer 44. The mixer 44 extends rearward from the internal combustion engine 36. The mixer 44 is connected to the exhaust pipe 48.

[0036] like Figure 2 As shown, the exhaust pipe 48 is a rearward-expanding cylindrical component. The diameter of the exhaust pipe 48 is larger than the diameter of the mixer 44. A portion of the mixer 44 is located at the front end 50 of the exhaust pipe 48. The rear end 52 of the mixer 44 is located inside the exhaust pipe 48. The exhaust pipe 48 is connected to the rear part (exhaust port 42) of the internal combustion engine 36 via the mixer 44. The exhaust pipe 48 is positioned behind the internal combustion engine 36 with a certain gap in the front-rear direction.

[0037] like Figure 4 As shown, a radiator 54 is disposed below the front end 50 of the exhaust pipe 48. The radiator 54 is located below the mixer 44. The radiator 54 has a rectangular shape. The exhaust pipe 48 and the radiator 54 are connected together by a connecting pipe 56. The connecting pipe 56 extends from the radiator 54 toward the front end 50 of the exhaust pipe 48. The connecting pipe 56 has a shape that gradually tapers at its tip as it moves from the radiator 54 toward the exhaust pipe 48. Figure 8 As shown, the length of the radiator 54 and the connecting pipe 56 in the front-to-back direction is shorter than the length of the mixer 44 in the front-to-back direction. That is, the front surface of the radiator 54 and the connecting pipe 56 is approximately coplanar with the front end face of the exhaust pipe 48, and the rear surface of the radiator 54 and the connecting pipe 56 is located in front of the rear end face of the mixer 44.

[0038] Figure 3 This is a schematic diagram of the power generation system 58. The power generation system 58 includes an internal combustion engine 36, a generator 38, an exhaust pipe 48, a radiator 54, a connecting pipe 56, and an electric pump 66. The internal combustion engine 36 has an intake port 60 and an exhaust port 42. The radiator 54 has an intake port 62 and an exhaust port 64. The exhaust port 64 of the radiator 54 is connected to the connecting pipe 56. The radiator 54 and the electric pump 66 are connected together through a first coolant passage 68. The electric pump 66 and the generator 38 are connected together through a second coolant passage 70. The generator 38 and the radiator 54 are connected together through a third coolant passage 72.

[0039] Then, while referring to Figures 4 to 14 The detailed structure of mixer 44 will be explained at the same time.

[0040] like Figure 10 As shown, the mixer 44 has a cylindrical portion 74 extending in the front-to-back direction. Figure 8 As shown, the cylindrical portion 74 is a cylindrical component with a diameter smaller than that of the exhaust pipe 48. The front end portion 76 of the cylindrical portion 74 is connected to the exhaust port 42 of the internal combustion engine 36. A portion of the cylindrical portion 74 is located inside the exhaust pipe 48. The rear end portion 78 of the cylindrical portion 74 is located inside the exhaust pipe 48. The cylindrical portion 74 has a shape that expands from the front end portion 76 to the rear end portion 78.

[0041] like Figure 10 As shown, the rear end 78 of the cylindrical portion 74 has a plurality of segmented cylindrical portions 80. The plurality of segmented cylindrical portions 80 are arranged from the middle portion of the cylindrical portion 74 to the rear end. That is, the cylindrical portion 74 is forked from the middle portion to the rear end. The cylindrical portion 74 is forked by being separated by the plurality of segmented cylindrical portions 80. The plurality of segmented cylindrical portions 80 are concentrated around the central axis of the cylindrical portion 74. In this embodiment, the case where the mixer 44 has four segmented cylindrical portions 80 will be described. The mixer 44 may also have two or three segmented cylindrical portions 80. Alternatively, the mixer 44 may also have five or more segmented cylindrical portions 80.

[0042] like Figure 6 As shown, the shape of the segmented cylindrical portion 80 is roughly fan-shaped when viewed from the rear. The shape of the segmented cylindrical portion 80 can also be arbitrary. The opening area of ​​the segmented cylindrical portion 80 is smaller than the opening area of ​​the cylindrical portion 74.

[0043] The segmented cylindrical portion 80 has one outer sidewall portion 82 and two inner sidewall portions 84. For example... Figure 10 As shown, the outer sidewall portion 82 and the inner sidewall portion 84 extend in the front-rear direction. A segmented cylindrical portion 80 is formed by connecting one outer sidewall portion 82 and two inner sidewall portions 84. The outer sidewall portion 82 of the segmented cylindrical portion 80 constitutes part of the outer wall 86 of the cylindrical portion 74. Figure 6 As shown, each inner wall portion 84 extends generally radially from near the center of the cylindrical portion 74 toward the outer wall 86 of the cylindrical portion 74. The portion where one inner wall portion 84 connects to another inner wall portion 84 is located near the center of the cylindrical portion 74.

[0044] The inner wall portion 84 of one segmented cylindrical portion 80 and the inner wall portion 84 of another adjacent segmented cylindrical portion 80 face each other. The rear ends of the two facing inner wall portions 84 are closer to each other as they approach the outer wall 86 of the cylindrical portion 74. The two facing inner wall portions 84 contact each other at a contact point 87. The contact point 87 is located near the outer wall 86 of the cylindrical portion 74.

[0045] A pair of inner wall portions 84 facing each other form a partition 88. The mixer 44 has four partitioned cylindrical portions 80. Therefore, the mixer 44 has four partitions 88. The four partitions 88 divide the inner side of the rear end portion 78 of the cylindrical portion 74 into four internal spaces. The four partitions 88 extend radially from the center of the cylindrical portion 74 towards the outer wall 86 of the cylindrical portion 74. Figure 7 As shown, a pair of inner wall portions 84 facing each other (refer to) Figure 6 The front ends of the ) are connected together.

[0046] like Figure 6 As shown, a guide vane 90 is formed by a plurality of partitions 88. The guide vane 90 has a base 92 and a plurality of partitions 88, wherein the base 92 is located near the center of the cylindrical portion 74; the plurality of partitions 88 extend radially from the base 92. The guide vane 90 is positioned opposite the exhaust port 42 of the internal combustion engine 36 (see reference). Figure 8 The first exhaust gas (waste gas) discharged into the cylindrical section 74 is rectified.

[0047] A discharge opening 96 is formed on the rear end face 94 of the guide vane 90. The discharge opening 96 is formed in a generally cross shape by the inner sidewall portions 84 constituting the plurality of partition portions 88. The discharge opening 96 includes a plurality of partial openings 100. The partial openings 100 are formed on the rear end face 98 of the partition portion 88. The partial openings 100 are disposed between a pair of inner sidewall portions 84 constituting the partition portion 88. The opening width of the partial openings 100 becomes narrower as they approach the outer wall 86 of the cylindrical portion 74. That is, the cross-sectional shape of the partition portion 88 is V-shaped.

[0048] like Figure 8 and Figure 9 As shown, a plurality of inlet holes 102 are formed in the cylindrical portion 74. Specifically, the inlet holes 102 are formed by the gap between two adjacent segmented cylindrical portions 80. The inlet holes 102 are connected to the discharge opening 96 (see reference 104) through the connecting hole 104. Figure 10 The outlet opening 96, multiple inlet holes 102, and multiple connecting holes 104 constitute multiple guide holes 106. The second exhaust gas (used gas) from the radiator 54 is discharged to the exhaust pipe 48 through the multiple guide holes 106.

[0049] like Figure 12 As shown, the closer to the cylindrical part 74 (refer to...) Figure 10 The width of the circumferential inlet hole 102 of the cylindrical portion 74 is narrower at the center of the cylinder. That is, the cross-sectional shape of the pair of inner wall portions 84 is V-shaped. For example... Figure 8 and Figure 9 As shown, the width of the inlet hole 102 in the front-rear direction (axial direction) of the cylindrical portion 74 decreases as it approaches the center of the cylindrical portion 74. That is, the inlet hole 102 has a shape that tapers towards the center of the cylindrical portion 74. Figure 13 As shown, the closer to the cylindrical part 74 (refer to...) Figure 10 The width of the connecting hole 104 in the circumferential direction of the cylindrical portion 74 decreases as it approaches the center of the cylindrical portion 74. Therefore, the connecting hole 104 becomes a shape that tapers towards the center of the cylindrical portion 74. The opening area of ​​the inlet hole 102 is smaller than the opening area of ​​the outlet hole 96.

[0050] like Figure 11 As shown, the front end of the partition 88 has a curved portion 108. The curved portion 108 curves more circumferentially along the cylindrical portion 74 the closer it is to the outer wall 86 of the cylindrical portion 74. Figure 8 , Figure 9 , Figures 11-13 As shown, the curved portion 108 (refer to) Figure 11 As it approaches the front end portion 76 of the cylindrical portion 74, it bends circumferentially along the cylindrical portion 74. The closer the inlet hole 102 is to the front end portion 76 of the cylindrical portion 74, the more it bends circumferentially along the cylindrical portion 74. The portion of the connecting hole 104 that communicates with the inlet hole 102 bends circumferentially along the cylindrical portion 74 as it approaches the front end portion 76 of the cylindrical portion 74 (see reference). Figure 13 ).

[0051] Internal combustion engine 36 (reference) Figure 3The internal combustion engine 36 includes a compressor, a burner, and a turbine. The turbine is connected to the output shaft 40. In the internal combustion engine 36, air introduced through the intake port 60 is compressed by the compressor. The compressed air is introduced into the burner. The burner generates high-temperature and high-pressure gas by burning fuel in the compressed air. The turbine rotates due to the high-temperature and high-pressure gas generated in the combustion chamber. The turbine rotates the output shaft 40. The gas passing through the turbine is discharged from the exhaust port 42 as exhaust gas (first exhaust gas).

[0052] The rotation of the turbine generates a vortex in the first exhaust gas. This vortex of first exhaust gas is discharged from exhaust port 42 into cylindrical section 74. (Example:) Figure 7 As shown, the curved portion 108 can be bent by reducing the vortex flow by redirecting it. Specifically, as... Figure 7 As shown, when the vortex is clockwise during main view, the curved portion 108 can bend counterclockwise. Since the vortex and the curved portion 108 are in opposite directions, the vortex weakens.

[0053] like Figure 10 As shown, the rear end portion of the outer wall 86 of the cylindrical portion 74 forms a notch nozzle 109. The notch nozzle 109 has multiple notches 110. The notches 110 are provided on the segmented cylindrical portion 80. Two notches 110 are provided on the segmented cylindrical portion 80. The two notches 110 are formed on the outer wall portion 82 of the segmented cylindrical portion 80. The two notches 110 are arranged side by side in the circumferential direction of the cylindrical portion 74. The notches 110 are inclined toward the rear end of the cylindrical portion 74. The notches 110 are recessed in such a way that they become deeper the closer they are to the rear end of the cylindrical portion 74. In addition, only one notch 110 may be formed on the segmented cylindrical portion 80. Alternatively, three or more notches 110 may be formed on the segmented cylindrical portion 80. Furthermore, the size of the multiple notches 110 may vary depending on the distance from the heat sink 54.

[0054] Next, for aircraft 10 (refer to...) Figure 1 The action of the air intake 60 to the internal combustion engine 36 (refer to...) will be explained. Figure 3 Air is introduced. The compressor of the internal combustion engine 36 compresses the air introduced from the intake port 60. The compressed air is introduced into the combustor. The combustor generates high-temperature and high-pressure gas by burning fuel in the compressed air. The turbine rotates due to the high-temperature and high-pressure gas generated in the combustion chamber. The turbine rotates the output shaft 40. With the rotation of the turbine, the high-temperature and high-pressure gas is discharged from the exhaust port 42 to the mixer 44 as the first exhaust gas forming a vortex.

[0055] The generator 38 generates electricity in conjunction with the rotation of the output shaft 40. The generator 38 supplies power to the motor drive circuit (not shown). The motor drive circuit powers the eight takeoff and landing rotors 20 (see reference). Figure 1 ) and at least one of the two cruise rotors 22 rotates.

[0056] Generator 38 also supplies power to electric pump 66. Electric pump 66 circulates the cooling medium in the order of first coolant passage 68, second coolant passage 70, and third coolant passage 72. Generator 38 is cooled by the circulating cooling medium. Radiator 54 cools the cooling medium (heat exchange) through air entering from inlet 62. The air heated by radiator 54 is discharged as second exhaust gas (used gas) from exhaust port 64 through connecting pipe 56 to exhaust pipe 48.

[0057] The first exhaust gas from the internal combustion engine 36 flows into the cylindrical section 74 (refer to...) Figure 8 The first exhaust gas flows into the cylindrical section 74, forming a vortex. The vortex passes through the bent section 108.

[0058] (Refer to Figure 7 The vortex weakens as it turns. The first exhaust gas, weakened by the vortex, passes through the split cylinder 80.

[0059] (Refer to Figure 6 The dividing cylinder 80 rectifies the first exhaust gas through the dividing section 88, thereby redirecting the direction of the first exhaust gas's movement towards the axial direction of the exhaust pipe 48 (the axial direction of the cylindrical section 74). The dividing cylinder 80 directs the first exhaust gas, whose axial component is dominant, towards the exhaust pipe 48 (see reference 74). Figure 4 )discharge.

[0060] The mixer 44 expands from the front end 76 to the rear end 78. The mixer 44 expands taking into account the flow rate of the second exhaust gas through the guide hole 106 and the volume of the mixer 44 itself. Specifically, the mixer 44 expands to keep the cross-sectional area of ​​the flow path of the first exhaust gas along the axial direction of the mixer 44 constant. By expanding the mixer 44, the pressure loss of the first exhaust gas can be reduced. Furthermore, the stagnation pressure generated inside the mixer 44 by the first exhaust gas can be reduced. By reducing pressure loss and stagnation pressure, the first and second exhaust gases can be easily discharged from the mixer 44. Additionally, the impact on the output of the internal combustion engine 36 can be suppressed.

[0061] From radiator 54 (reference) Figure 4 The second exhaust gas flows through exhaust pipe 48.

[0062] (Refer to Figure 5The gap between the inner wall of the cylindrical part 74 and the outer wall 86 of the cylindrical part 74. A portion of the second discharged gas flows into the inlet hole 102 (see reference). Figure 8 The inlet hole 102 has a shape that tapers towards the center of the cylindrical portion 74. Accordingly, the flow direction of the second discharged gas inside the inlet hole 106 is redirected toward the center of the discharge opening 96.

[0063] Furthermore, the closer the discharge opening 96 is to the center of the cylindrical portion 74, the wider it becomes. Accordingly, the cross-sectional area of ​​the flow path for the second discharged gas flowing into the inlet hole 102 and towards the center of the cylindrical portion 74 is limited. As a result, the pressure rise of the second discharged gas near the center of the cylindrical portion 74 can be suppressed.

[0064] As described above, the first exhaust gas flows in a swirling stream up to the tip of the guide vane 90. Therefore, up to the tip of the guide vane 90, the pressure of the first exhaust gas decreases near the center of the cylindrical portion 74 due to the negative pressure generated by the vortex core. Furthermore, the first exhaust gas is axially diverted towards the exhaust pipe 48 through the multiple partitions 88 of the guide vane 90. Consequently, the diverted first exhaust gas is dominated by this axial component. As a result, the pressure near the center of the cylindrical portion 74 of the diverted first exhaust gas increases. Therefore, the diverted first exhaust gas does not easily flow near the center of the cylindrical portion 74. In this embodiment, by forming the exhaust opening 96 in the above shape, the pressure rise of the second exhaust gas near the center of the cylindrical portion 74 can be suppressed. Therefore, the pressure gradient between the partitioned cylindrical portion 80 and the center of the exhaust opening 96 can be suppressed. As a result, the first exhaust gas easily flows near the center of the cylindrical portion 74 in the partitioned cylindrical portion 80. By allowing the first exhaust gas to flow in this way, the mixing of the first and second exhaust gases inside the exhaust pipe 48 can be promoted. By promoting the mixing of the first and second exhaust gases, the exhaust pipe 48 can function effectively.

[0065] like Figure 5 As shown, another portion of the second exhaust gas is discharged towards the rear of the mixer 44 through the gap between the notch 110 and the exhaust pipe 48. The notch 110 becomes more recessed closer to the rear end of the cylindrical portion 74. Accordingly, the second exhaust gas is discharged towards the central portion inside the exhaust pipe 48. In addition, the opening area of ​​the gap between the notch 110 and the exhaust pipe 48 is larger closer to the rear end of the cylindrical portion 74. Accordingly, the contact area between the first and second exhaust gases behind the mixer 44 is increased. By increasing this contact area, the mixing of the first and second exhaust gases can be promoted. As a result, since the relatively high-speed first exhaust gas diffuses to the vicinity of the inner wall of the exhaust pipe 48, the exhaust pipe 48 is more easily activated.

[0066] That is, as described above, by discharging the second exhaust gas, the first exhaust gas is discharged from the dividing cylinder 80 in a manner surrounded by the second exhaust gas. Accordingly, the contact area between the first and second exhaust gases is increased. As a result, the first and second exhaust gases can be well mixed behind the mixer 44. By mixing the first and second exhaust gases, the distribution of the amount of mixed gas movement inside the exhaust pipe 48 is made more uniform. Therefore, the function of the exhaust pipe 48 is more easily realized. The mixed gas is discharged to the outside from the rear end of the exhaust pipe 48.

[0067] However, without the mixer 44, the first and second exhaust gases flow along the inner wall of the exhaust pipe 48. The first and second exhaust gases are not adequately mixed. The mixture of the first and second exhaust gases does not flow uniformly inside the exhaust pipe 48. Because the mixture does not flow uniformly, the gas flow near the inner wall of the exhaust pipe 48 separates from the inner wall. Consequently, a sufficient pressure gradient cannot be ensured inside the exhaust pipe 48. As a result, there is a pressure rise at the exhaust port 42 of the internal combustion engine 36, affecting the output efficiency of the internal combustion engine 36. Furthermore, the first exhaust gas becomes a vortex and is discharged from the exhaust port 42 of the internal combustion engine 36 into the exhaust pipe 48. Being discharged through the vortex generates a pressure loss caused by the vortex. Due to the pressure loss generated inside the exhaust pipe 48, the output efficiency of the internal combustion engine 36 is sometimes affected.

[0068] In contrast, in this embodiment, due to the mixer 44 having the above-described structure, the first exhaust gas and the second exhaust gas, which are axially diverted towards the exhaust pipe 48, can be well mixed inside the exhaust pipe 48. Inside the exhaust pipe 48, the mixed gas of the first and second exhaust gases can flow uniformly. Accordingly, the mixed gas is discharged from the exhaust pipe 48 when the internal pressure of the exhaust pipe 48 is sufficiently restored. As a result, the output efficiency of the internal combustion engine 36 can be improved.

[0069] The invention described below is an invention that can be mastered based on the above-described embodiments.

[0070] The first aspect of the invention is a mixer (44) that mixes a first exhaust gas discharged from an internal combustion engine (36) and a second exhaust gas discharged from a radiator (54). The mixer has a cylindrical portion (74), guide vanes (90), a notched nozzle (109), and a plurality of guide holes (106). The cylindrical portion (74) introduces the first exhaust gas at its front end (76) and discharges the first exhaust gas from its rear end (78). The guide vanes (90) have an outer wall facing the cylindrical portion. (86) A plurality of radially extending partitions (88) divide the rear end of the cylindrical portion into a plurality of segmented cylindrical portions (80) through the plurality of partitions; the notched nozzle (109) forms the outer wall of the cylindrical portion and has a notch (110) formed on each of the plurality of segmented cylindrical portions; the plurality of guide holes (106) are formed from the outer wall of the cylindrical portion to the rear end face of the guide vane to discharge the second exhaust gas from the rear end face (94) of the guide vane.

[0071] According to the present invention, the output efficiency of an internal combustion engine can be improved.

[0072] That is, the first exhaust gas is introduced from the internal combustion engine through the cylindrical section into the split cylinder section. The first exhaust gas introduced into the split cylinder section is rectified by the partition section. The rectified first exhaust gas is discharged from the split cylinder section to the exhaust pipe. A portion of the second exhaust gas is discharged from the radiator through the guide hole from the rear end face of the guide vane towards the exhaust pipe. A portion of the second exhaust gas is discharged to the vicinity of the center inside the exhaust pipe. Another portion of the second exhaust gas is discharged from the radiator through the notch towards the exhaust pipe. The first exhaust gas is discharged from the split cylinder section surrounded by the second exhaust gas discharged from the rear end face of the guide vane and the second exhaust gas discharged from the notch. Accordingly, since the contact area of ​​the first and second exhaust gases is increased, the first and second exhaust gases can be fully mixed inside the exhaust pipe. Furthermore, since a portion of the second exhaust gas is discharged to the vicinity of the center inside the exhaust pipe, the first and second exhaust gases can be mixed near the center inside the exhaust pipe. Therefore, in this invention, the pressure recovery function of the exhaust pipe can be improved. Furthermore, the pressure drop at the engine outlet caused by the pressure difference inside the exhaust pipe reduces pressure loss within the exhaust pipe. By reducing pressure loss, the engine's output efficiency can be improved.

[0073] In the first aspect of the present invention, the plurality of guide holes may have discharge openings (96), a plurality of inlet holes (102) and a plurality of connecting holes (104), wherein the discharge openings (96) are formed on the rear end face of the guide vane; the plurality of inlet holes (102) are formed on the outer wall of the cylindrical portion; and the plurality of connecting holes (104) are formed on the plurality of partition portions and connect the discharge openings and the plurality of inlet holes.

[0074] Accordingly, the second exhaust gas can be introduced through the inlet hole and discharged through the outlet hole via the connecting hole.

[0075] In the first aspect of the present invention, the opening (100) formed on the rear end face (98) of the plurality of partitions in the discharge opening may be narrower as it is closer to the outer wall of the cylindrical portion.

[0076] Accordingly, the flow direction of the second discharged gas is redirected towards the center of the discharge opening. Furthermore, the discharge opening becomes wider the closer it is to the center of the cylindrical section. This restricts the cross-sectional area of ​​the flow path of the second discharged gas entering from the inlet and moving towards the center of the cylindrical section. As a result, the pressure rise of the second discharged gas near the center of the cylindrical section can be suppressed.

[0077] As described above, the first exhaust gas flows in a swirling stream up to the tip of the guide vane. Therefore, up to the tip of the guide vane, the pressure of the first exhaust gas decreases near the center of the cylindrical section due to the negative pressure generated by the vortex core. Furthermore, the first exhaust gas is axially diverted through multiple partitions of the guide vane towards the exhaust pipe. Consequently, the diverted first exhaust gas becomes dominated by this axial component. As a result, the pressure near the center of the cylindrical section of the diverted first exhaust gas increases. Therefore, the diverted first exhaust gas does not flow easily near the center of the cylindrical section.

[0078] In this invention, by forming the discharge opening into the shape described above, the pressure rise of the second discharged gas near the center of the cylindrical portion can be suppressed. Accordingly, the pressure gradient between the split cylindrical portion and the center of the discharge opening can be suppressed. As a result, the first discharged gas easily flows near the center of the cylindrical portion within the split cylindrical portion. By allowing the first discharged gas to flow in this way, the mixing of the first and second discharged gases inside the exhaust pipe can be promoted. By promoting the mixing of the first and second discharged gases, the exhaust pipe can function effectively.

[0079] In the first aspect of the present invention, the closer the plurality of inlet holes are to the center of the cylindrical portion, the narrower the circumferential width of the cylindrical portion.

[0080] Accordingly, the inlet hole becomes a shape that tapers towards the center of the cylindrical section. In this case, the flow direction of the second exhaust gas introduced into the inlet hole is redirected towards the center of the exhaust opening. Furthermore, the cross-sectional area of ​​the flow path of the second exhaust gas entering from the inlet hole and moving towards the center of the cylindrical section is restricted. Therefore, it is possible to suppress the pressure rise of the second exhaust gas near the center of the cylindrical section.

[0081] In the first aspect of the present invention, the closer the plurality of inlet holes are to the center of the cylindrical portion, the narrower the axial width of the cylindrical portion.

[0082] In this case, the inlet hole also becomes a shape that tapers towards the center of the cylindrical section. Accordingly, the flow direction of the second exhaust gas introduced into the inlet hole is redirected towards the center of the exhaust opening. Furthermore, the cross-sectional area of ​​the flow path of the second exhaust gas entering from the inlet hole and moving towards the center of the cylindrical section is restricted. Therefore, it is possible to suppress the pressure rise of the second exhaust gas near the center of the cylindrical section.

[0083] In the first aspect of the present invention, the closer the plurality of connecting holes are to the center of the cylindrical portion, the narrower the circumferential width of the cylindrical portion.

[0084] Accordingly, the multiple connecting holes become tapered towards the center of the cylindrical section. In this case, the flow direction of the second discharged gas is also diverted towards the center of the discharge opening. Furthermore, since the cross-sectional area of ​​the flow path of the second discharged gas toward the center of the cylindrical section is restricted, the pressure rise of the second discharged gas near the center of the cylindrical section can be suppressed.

[0085] In a first aspect of the invention, the guide vane may have a base (92) and a plurality of partitions extending radially from the base, the plurality of partitions extending into the cylindrical portion.

[0086] Therefore, it is possible to efficiently rectify the first exhaust gas that becomes a vortex.

[0087] In the first aspect of the present invention, each of the plurality of partitions may have a curved portion (108) at its front end, which bends circumferentially along the cylindrical portion as it approaches the outer wall of the cylindrical portion.

[0088] Accordingly, when the first exhaust gas, which forms a vortex, flows into the cylindrical section, it is deflected by the bend, thereby weakening the vortex. The weakened vortex of the first exhaust gas is then redirected axially towards the mixer by the partition. As a result, the first exhaust gas, with its axial component being dominant, can be discharged from the partitioned cylinder section.

[0089] In a first aspect of the invention, the plurality of the curved portions may be bent circumferentially as they approach the front end of the cylindrical portion.

[0090] In this case, when the first exhaust gas, which forms a vortex, flows into the cylindrical section, the first exhaust gas is deflected by the bend, thereby weakening the vortex. The weakened vortex of the first exhaust gas is then redirected axially towards the mixer by the partition. As a result, the first exhaust gas, with its axial component being dominant, can be reliably discharged from the partitioned cylinder section.

[0091] In the first aspect of the present invention, the notch may be formed in a plurality of the outer walls of the rear ends of each of the plurality of segmented cylindrical portions.

[0092] Therefore, the second exhaust gas flowing through the notch and the first exhaust gas discharged from the dividing cylinder can be well mixed.

[0093] In the first aspect of the present invention, the depth of the notch may be greater as it approaches the rear end of the cylindrical portion.

[0094] Accordingly, the second exhaust gas flowing through the notch flows toward the first exhaust gas exiting from the dividing cylinder. As a result, the first and second exhaust gases can be mixed more effectively.

[0095] The second aspect of the present invention is a mobile body having a mixer, an internal combustion engine, an exhaust pipe (48), a generator (38), and a radiator as in the first aspect, wherein the exhaust pipe (48) is connected to the internal combustion engine; the generator (38) is connected to the output shaft (40) of the internal combustion engine; the radiator cools the cooling medium by heat exchange between the cooling medium of the generator and the second exhaust gas, and discharges the heat-exchanged second exhaust gas to the exhaust pipe; the mixer is disposed inside the exhaust pipe and mixes the first exhaust gas discharged from the internal combustion engine and the second exhaust gas discharged from the radiator.

[0096] Therefore, the effects of the first method can be easily obtained. In addition, it is possible to construct a moving body while maintaining the output efficiency of the internal combustion engine.

[0097] A third aspect of the invention is a mixer (44) that mixes a first exhaust gas discharged from an internal combustion engine (36) and a second exhaust gas discharged from a radiator (54). The mixer has a cylindrical portion (74), guide vanes (90), and a plurality of guide holes (106). The cylindrical portion (74) introduces the first exhaust gas at its front end (76) and discharges it from its rear end (78). The guide vanes (90) have a plurality of partitions (88) extending radially toward the outer wall (86) of the cylindrical portion, dividing the rear end of the cylindrical portion into a plurality of partitioned cylindrical portions (80). The plurality of guide holes (106) are formed from the outer wall of the cylindrical portion to the guide vanes. The rear end face of the guide vane is used to discharge the second exhaust gas from the rear end face (94) of the guide vane. The plurality of guide holes have an exhaust opening (96), a plurality of inlet holes (102) and a plurality of connecting holes (104), wherein the exhaust opening (96) is formed on the rear end face of the guide vane; the plurality of inlet holes (102) are formed on the outer wall of the cylindrical portion; the plurality of connecting holes (104) are formed on the plurality of partitions and connect the exhaust opening and the plurality of inlet holes. The closer the exhaust opening (100) is to the rear end face of the plurality of partitions, the narrower its width. The closer the plurality of inlet holes are to the center of the cylindrical portion, the narrower their width in the circumferential direction of the cylindrical portion.

[0098] According to the present invention, the output efficiency of an internal combustion engine can be improved.

[0099] That is, the first exhaust gas is introduced from the internal combustion engine through the cylindrical section into the split cylinder section. The first exhaust gas introduced into the split cylinder section is rectified by the partition section. The rectified first exhaust gas is discharged from the split cylinder section to the exhaust pipe. A portion of the second exhaust gas is discharged from the radiator through the guide hole from the rear end face of the guide vane towards the exhaust pipe. A portion of the second exhaust gas is discharged to the vicinity of the center inside the exhaust pipe. Another portion of the second exhaust gas is discharged from the radiator through the notch towards the exhaust pipe. The first exhaust gas is discharged from the split cylinder section surrounded by the second exhaust gas discharged from the rear end face of the guide vane and the second exhaust gas discharged from the notch. Accordingly, since the contact area of ​​the first and second exhaust gases is increased, the first and second exhaust gases can be fully mixed inside the exhaust pipe. Furthermore, since a portion of the second exhaust gas is discharged to the vicinity of the center inside the exhaust pipe, the first and second exhaust gases can be mixed near the center inside the exhaust pipe. Therefore, in this invention, the pressure recovery function of the exhaust pipe can be improved. Furthermore, the pressure drop at the engine outlet caused by the pressure difference inside the exhaust pipe reduces pressure loss within the exhaust pipe. By reducing pressure loss, the engine's output efficiency can be improved.

[0100] In addition, according to the present invention, the second exhaust gas can be introduced from the inlet hole and discharged from the outlet through the connecting hole.

[0101] Furthermore, according to the present invention, the flow direction of the second discharged gas is redirected towards the center of the discharge opening. Additionally, the discharge opening becomes wider the closer it is to the center of the cylindrical portion. Accordingly, the cross-sectional area of ​​the flow path of the second discharged gas entering from the inlet and moving towards the center of the cylindrical portion is limited. As a result, the pressure rise of the second discharged gas near the center of the cylindrical portion can be suppressed.

[0102] As described above, the first exhaust gas flows in a swirling stream up to the tip of the guide vane. Therefore, up to the tip of the guide vane, the pressure of the first exhaust gas decreases near the center of the cylindrical section due to the negative pressure generated by the vortex core. Furthermore, the first exhaust gas is axially diverted through multiple partitions of the guide vane towards the exhaust pipe. Consequently, the diverted first exhaust gas becomes dominated by this axial component. As a result, the pressure near the center of the cylindrical section of the diverted first exhaust gas increases. Therefore, the diverted first exhaust gas does not flow easily near the center of the cylindrical section.

[0103] In this invention, by forming the discharge opening into the shape described above, the pressure rise of the second discharged gas near the center of the cylindrical portion can be suppressed. Accordingly, the pressure gradient between the split cylindrical portion and the center of the discharge opening can be suppressed. As a result, the first discharged gas easily flows near the center of the cylindrical portion within the split cylindrical portion. By allowing the first discharged gas to flow in this way, the mixing of the first and second discharged gases inside the exhaust pipe can be promoted. By promoting the mixing of the first and second discharged gases, the exhaust pipe can function effectively.

[0104] In a third aspect of the present invention, the closer the plurality of inlet holes are to the center of the cylindrical portion, the narrower their width in the axial direction of the cylindrical portion.

[0105] In this case, the inlet hole also becomes a shape that tapers towards the center of the cylindrical section. Accordingly, the flow direction of the second exhaust gas introduced into the inlet hole is redirected towards the center of the exhaust opening. Furthermore, the cross-sectional area of ​​the flow path of the second exhaust gas entering from the inlet hole and moving towards the center of the cylindrical section is restricted. Therefore, it is possible to suppress the pressure rise of the second exhaust gas near the center of the cylindrical section.

[0106] In a third aspect of the invention, the width of the plurality of connecting holes in the circumferential direction may be narrower as they are closer to the center of the cylindrical portion.

[0107] Accordingly, the multiple connecting holes become tapered towards the center of the cylindrical section. In this case, the flow direction of the second discharged gas is also diverted towards the center of the discharge opening. Furthermore, since the cross-sectional area of ​​the flow path of the second discharged gas toward the center of the cylindrical section is restricted, the pressure rise of the second discharged gas near the center of the cylindrical section can be suppressed.

[0108] In a third aspect of the invention, the guide vane may have a base (92) and a plurality of partitions extending radially from the base, the plurality of partitions extending into the cylindrical portion.

[0109] Therefore, it is possible to efficiently rectify the first exhaust gas that becomes a vortex.

[0110] In a third aspect of the invention, each of the plurality of partitions may have a curved portion (108) at its front end, which bends circumferentially along the cylindrical portion as it approaches the outer wall of the cylindrical portion.

[0111] Accordingly, when the first exhaust gas, which forms a vortex, flows into the cylindrical section, it is deflected by the bend, thereby weakening the vortex. The weakened vortex of the first exhaust gas is then redirected axially towards the mixer by the partition. As a result, the first exhaust gas, with its axial component being dominant, can be discharged from the partitioned cylinder section.

[0112] In a third aspect of the invention, the plurality of the curved portions may be bent circumferentially as they approach the front end of the cylindrical portion.

[0113] In this case, when the first exhaust gas, which forms a vortex, flows into the cylindrical section, the first exhaust gas is deflected by the bend, thereby weakening the vortex. The weakened vortex of the first exhaust gas is then redirected axially towards the mixer by the partition. As a result, the first exhaust gas, with its axial component being dominant, can be reliably discharged from the partitioned cylinder section.

[0114] The fourth aspect of the present invention is a mobile body having a mixer, an internal combustion engine, an exhaust pipe (48), a generator (38), and a radiator as in the third aspect, wherein the exhaust pipe (48) is connected to the internal combustion engine; the generator (38) is connected to the output shaft (40) of the internal combustion engine; the radiator cools the cooling medium by heat exchange between the cooling medium of the generator and the second exhaust gas, and discharges the heat-exchanged second exhaust gas to the exhaust pipe; the mixer is disposed inside the exhaust pipe and mixes the first exhaust gas discharged from the internal combustion engine and the second exhaust gas discharged from the radiator.

[0115] Therefore, the effects of the third method can be easily obtained. In addition, it is possible to construct a moving body while maintaining the output efficiency of the internal combustion engine.

[0116] Furthermore, the present invention is not limited to the above-described embodiments, and various structures can be adopted without departing from the spirit of the present invention.

Claims

1. A mixer (44) for mixing a first exhaust gas from an internal combustion engine (36) and a second exhaust gas from a radiator (54), characterized in that, It has a cylindrical section (74), guide vanes (90), a notched nozzle (109), and multiple guide holes (106), wherein, The cylindrical portion (74) introduces the first exhaust gas at the front end (76) and exhausts the first exhaust gas from the rear end (78); The guide vane (90) has a plurality of partitions (88) extending radially toward the outer wall (86) of the cylindrical portion, and the rear end of the cylindrical portion is divided into a plurality of partitioned cylindrical portions (80) by the plurality of partitions. The notched nozzle (109) forms the outer wall of the cylindrical portion and has a notch (110) formed on each of the plurality of segmented cylindrical portions; A plurality of the guide holes (106) are formed from the outer wall of the cylindrical portion to the rear end face of the guide vane to discharge the second discharge gas from the rear end face (94) of the guide vane. The plurality of the segmented cylindrical sections are arranged circumferentially along the cylindrical section. The multiple segmented cylindrical portions each have an outer side wall portion and two inner side wall portions, wherein the outer side wall portion forms the notch, and the two inner side wall portions are respectively connected to the two ends of the outer side wall portion located in the circumferential direction of the cylindrical portion. The segmented cylindrical portion is formed into a cylindrical shape by the two inner side wall portions connected to each other by the outer side wall portion and the inner end.

2. A mixer that mixes a first exhaust gas from an internal combustion engine and a second exhaust gas from a radiator, characterized in that, It has a cylindrical section, guide vanes, a notched nozzle, and multiple guide holes, among which, The cylindrical portion introduces the first exhaust gas at its front end and discharges the first exhaust gas from its rear end; The guide vane has a plurality of partitions extending radially toward the outer wall of the cylindrical portion, which divide the rear end of the cylindrical portion into a plurality of partitioned cylindrical portions. The recessed nozzle forms the outer wall of the cylindrical portion and has a recess formed on each of the plurality of segmented cylindrical portions; A plurality of the guide holes are formed from the outer wall of the cylindrical portion to the rear end face of the guide vane to discharge the second exhaust gas from the rear end face of the guide vane. The plurality of the segmented cylindrical sections are arranged circumferentially along the cylindrical section. Each of the multiple segmented cylindrical sections has an outer sidewall and two inner sidewalls. The outer sidewalls have a notch, and the two inner sidewalls are respectively connected to the two circumferential ends of the outer sidewalls. The segmented cylindrical sections are formed into a cylindrical shape by the outer sidewalls and the two inner sidewalls connected to each other at their inner ends. Partial openings are formed between the opposing inner wall portions of the segmented cylindrical portions that are adjacent to each other in the circumferential direction of the cylindrical portion. The plurality of guide holes have a discharge opening formed on the rear end face of the guide vane. One of the discharge openings is composed of a plurality of the partial openings connected to each other at their inner ends.

3. The mixer according to claim 2, characterized in that, The plurality of guide holes have a plurality of inlet holes (102) and a plurality of connecting holes (104), wherein, Multiple inlet holes (102) are formed on the outer wall of the cylindrical portion; Multiple connecting holes (104) are formed in multiple partitions and connect the discharge opening and multiple inlet holes.

4. A mixer that mixes a first exhaust gas from an internal combustion engine and a second exhaust gas from a radiator, characterized in that, It has a cylindrical section, guide vanes, a notched nozzle, and multiple guide holes, among which, The cylindrical portion introduces the first exhaust gas at its front end and discharges the first exhaust gas from its rear end; The guide vane has a plurality of partitions extending radially toward the outer wall of the cylindrical portion, which divide the rear end of the cylindrical portion into a plurality of partitioned cylindrical portions. The recessed nozzle forms the outer wall of the cylindrical portion and has a recess formed on each of the plurality of segmented cylindrical portions; A plurality of the guide holes are formed from the outer wall of the cylindrical portion to the rear end face of the guide vane to discharge the second exhaust gas from the rear end face of the guide vane. The plurality of guide holes have discharge openings, plurality of inlet holes, and plurality of connecting holes, wherein, The discharge opening is formed on the rear end face of the guide vane; Multiple inlet holes are formed on the outer wall of the cylindrical portion; Multiple connecting holes are formed in multiple partitions and connect the discharge opening and multiple inlet holes. The opening (100) formed on the rear end face (98) of the plurality of partitions in the discharge opening is narrower the closer it is to the outer wall of the cylindrical portion.

5. The mixer according to claim 4, characterized in that, The closer the multiple inlet holes are to the center of the cylindrical portion, the narrower their width in the circumferential direction of the cylindrical portion.

6. The mixer according to claim 4 or 5, characterized in that, The closer the multiple inlet holes are to the center of the cylindrical portion, the narrower their width in the axial direction of the cylindrical portion.

7. The mixer according to claim 4 or 5, characterized in that, The closer the multiple connecting holes are to the center of the cylindrical portion, the narrower their width in the circumferential direction of the cylindrical portion.

8. A mixer that mixes a first exhaust gas from an internal combustion engine and a second exhaust gas from a radiator, characterized in that, It has a cylindrical section, guide vanes, a notched nozzle, and multiple guide holes, among which, The cylindrical portion introduces the first exhaust gas at its front end and discharges the first exhaust gas from its rear end; The guide vane has a plurality of partitions extending radially toward the outer wall of the cylindrical portion, which divide the rear end of the cylindrical portion into a plurality of partitioned cylindrical portions. The recessed nozzle forms the outer wall of the cylindrical portion and has a recess formed on each of the plurality of segmented cylindrical portions; A plurality of the guide holes are formed from the outer wall of the cylindrical portion to the rear end face of the guide vane to discharge the second exhaust gas from the rear end face of the guide vane. The guide vane has a base (92) and a plurality of partitions extending radially from the base. The plurality of the partitions extend into the cylindrical portion. Each of the plurality of partitions has a curved portion at its front end, which bends circumferentially along the outer wall of the cylindrical portion as it approaches the outer wall of the cylindrical portion. The plurality of the curved portions bend circumferentially along the cylindrical portion as they approach the front end of the cylindrical portion.

9. A mixer for mixing a first exhaust gas from an internal combustion engine and a second exhaust gas from a radiator, characterized in that, It has a cylindrical section, guide vanes, a notched nozzle, and multiple guide holes, among which, The cylindrical portion introduces the first exhaust gas at its front end and discharges the first exhaust gas from its rear end; The guide vane has a plurality of partitions extending radially toward the outer wall of the cylindrical portion, which divide the rear end of the cylindrical portion into a plurality of partitioned cylindrical portions. The recessed nozzle forms the outer wall of the cylindrical portion and has a recess formed on each of the plurality of segmented cylindrical portions; A plurality of the guide holes are formed from the outer wall of the cylindrical portion to the rear end face of the guide vane to discharge the second exhaust gas from the rear end face of the guide vane. The notches are formed on the outer wall of the rear end of each of the multiple segmented cylindrical portions.

10. The mixer according to any one of claims 1 to 5, 8, and 9, characterized in that, The depth of the notch increases as it approaches the rear end of the cylindrical section.

11. A mobile body, characterized in that, The mixture, internal combustion engine, exhaust pipe (48), generator (38), and radiator as described in any one of claims 1 to 10, wherein, The exhaust pipe (48) is connected to the internal combustion engine; The generator (38) is connected to the output shaft (40) of the internal combustion engine; The radiator cools the cooling medium by exchanging heat between the generator's cooling medium and the second exhaust gas, and then discharges the heat-exchanged second exhaust gas into the exhaust pipe. The mixer is disposed inside the exhaust pipe and mixes the first exhaust gas discharged from the internal combustion engine and the second exhaust gas discharged from the radiator.

12. A mixer (44) for mixing a first exhaust gas from an internal combustion engine (36) and a second exhaust gas from a radiator (54), characterized in that, It has a cylindrical section (74), guide vanes (90), and multiple guide holes (106), wherein, The cylindrical portion (74) introduces the first exhaust gas at the front end (76) and exhausts the first exhaust gas from the rear end (78); The guide vane (90) has a plurality of partitions (88) extending radially toward the outer wall (86) of the cylindrical portion, and the rear end of the cylindrical portion is divided into a plurality of partitioned cylindrical portions (80) by the plurality of partitions. The plurality of guide holes (106) are formed from the outer wall of the cylindrical portion to the rear end face of the guide vane to discharge the second discharge gas from the rear end face (94) of the guide vane. The plurality of guide holes have discharge openings (96), multiple inlet holes (102), and multiple connecting holes (104), wherein, The discharge opening (96) is formed on the rear end face of the guide vane; Multiple inlet holes (102) are formed on the outer wall of the cylindrical portion; Multiple connecting holes (104) are formed in multiple partitions and connect the discharge opening and multiple inlet holes. The closer the discharge opening (100) is to the outer wall of the cylindrical portion, the narrower its width. The closer the multiple inlet holes are to the center of the cylindrical portion, the narrower their width in the circumferential direction of the cylindrical portion.

13. The mixer according to claim 12, characterized in that, The closer the multiple inlet holes are to the center of the cylindrical portion, the narrower their width in the axial direction of the cylindrical portion.

14. The mixer according to claim 12, characterized in that, The closer the multiple connecting holes are to the center of the cylindrical portion, the narrower their width in the circumferential direction of the cylindrical portion.

15. The mixer according to claim 12, characterized in that, The guide vane has a base (92) and a plurality of partitions extending radially from the base. The plurality of the partitions extend into the cylindrical portion.

16. The mixer according to claim 15, characterized in that, Each of the plurality of partitions has a curved portion (108) at its front end, which bends circumferentially along the cylindrical portion as it approaches the outer wall of the cylindrical portion.

17. The mixer according to claim 16, characterized in that, The plurality of the curved portions bend circumferentially along the cylindrical portion as they approach the front end of the cylindrical portion.

18. A mobile body, characterized in that, The mixture, internal combustion engine, exhaust pipe (48), generator (38), and radiator as described in any one of claims 12 to 17, wherein, The exhaust pipe (48) is connected to the internal combustion engine; The generator (38) is connected to the output shaft (40) of the internal combustion engine; The radiator cools the cooling medium by exchanging heat between the generator's cooling medium and the second exhaust gas, and then discharges the heat-exchanged second exhaust gas into the exhaust pipe. The mixer is disposed inside the exhaust pipe and mixes the first exhaust gas discharged from the internal combustion engine and the second exhaust gas discharged from the radiator.

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