JP6970070B2 - Exhaust heat recovery device - Google Patents

Description

The present disclosure relates to an exhaust heat recovery device.

Exhaust heat recovery devices that recover the heat of exhaust gas in an internal combustion engine for automobiles with cooling water are known. The exhaust heat recovery device is provided in the exhaust gas discharge flow path. The exhaust heat recovered by the cooling water in the exhaust heat recovery device is used for heating the inside of the vehicle, warming up the internal combustion engine, and the like.

It is known that such an exhaust heat recovery device is provided with a valve for adjusting the supply amount of exhaust gas to the heat exchange unit in order to adjust the recovery amount of exhaust heat (Patent Document 1). reference).

In the above document, the valve driven by the actuator is arranged on the upstream side in the flow direction of the exhaust gas with respect to the heat exchange portion.

Japanese Unexamined Patent Publication No. 2015-203400

When the valve is arranged on the upstream side with respect to the heat exchange portion as described above, the length of the exhaust heat recovery device along the flow direction of the exhaust gas becomes large. Therefore, for example, by arranging the valve at a position aligned with the heat exchange portion in the flow direction of the exhaust gas, the length of the exhaust heat recovery device can be reduced.

However, when the valve is arranged in this way, when the valve is driven so as to block the flow of the exhaust gas to the inlet of the heat exchange unit, a part of the main flow path of the exhaust gas is also blocked by the valve. As a result, the passing area of the exhaust gas becomes small and the pressure loss becomes large. On the other hand, if the diameter of the main flow path is increased in order to reduce the pressure loss, the size of the exhaust heat recovery device becomes large.

One aspect of the present disclosure is to provide an exhaust heat recovery device capable of reducing pressure loss while reducing the size.

One aspect of the present disclosure is a heat exchange unit that exchanges heat between the exhaust gas of an internal combustion engine and cooling water, an introduction port for introducing the exhaust gas, a main exhaust port for discharging the exhaust gas to the outside, and heat. A main flow path having a supply port for supplying exhaust gas to the switching section is arranged at a position where at least a part of the main flow path overlaps with the supply port in the flow direction of the exhaust gas, and from the main flow path to the heat exchange section. It is an exhaust heat recovery device including a valve for adjusting the supply amount of exhaust gas and an actuator for operating the valve.

In addition, the valve has a rod body that rotates around the axis by an actuator, a first wing that is fixed to the rod body and extends radially outward from the rod body, and can rotate around the rod body as a central axis. It has a second wing that is attached to the rod and extends radially outward from the rod. The second wing can rotate in a direction of expanding the passage area of the exhaust gas in the main flow path when limiting the supply amount of the exhaust gas to the supply port.

According to such a configuration, since the valve is arranged in the main flow path at a position overlapping with the supply port to the heat exchange portion, the exhaust heat recovery device can be miniaturized. Further, when the flow of the exhaust gas to the heat exchange portion is regulated, the second blade of the valve rotates in the direction of expanding the passing area of the exhaust gas, so that the pressure loss in the main flow path can be reduced.

In one aspect of the present disclosure, the area where the first wing receives the pressure of the exhaust gas may be equal to the area where the second wing receives the pressure of the exhaust gas. According to such a configuration, the pressure received by the first wing from the exhaust gas and the pressure received by the second wing from the exhaust gas are substantially equal to each other. Therefore, the load of the actuator that rotates the valve can be reduced.

In one aspect of the present disclosure, the second wing may be rotatable in a direction of expansion due to the pressure of the exhaust gas. According to such a configuration, the mechanism for rotating the second wing can be simplified.

In one aspect of the present disclosure, the heat exchange unit discharges the exhaust gas to the first exhaust port for discharging the exhaust gas toward the main flow path and the second exhaust gas to the exhaust recirculation flow path for supplying the exhaust gas to the internal combustion engine. It may have an exit. According to such a configuration, a part of the exhaust gas can be recirculated to the internal combustion engine by adjusting the opening degree of the valve. That is, the EGR function can be added to the exhaust heat recovery device while downsizing the exhaust heat recovery device.

FIG. 1 is a schematic perspective view of the exhaust heat recovery device of the embodiment. FIG. 2 is a schematic cross-sectional view taken along the line II-II of FIG. 3A is a schematic front view of the valve in the exhaust heat recovery device of FIG. 1, FIG. 3B is a schematic rear view of the valve of FIG. 3A, and FIG. 3C is a schematic view of the valve of FIG. 3A. It is a plan view. 4A is a schematic cross-sectional view showing the non-recovery mode in the exhaust heat recovery device of FIG. 1, and FIG. 4B is a schematic cross-sectional view showing the EGR mode in the exhaust heat recovery device of FIG. 5A is a schematic front view of the valve in an embodiment different from FIG. 3A, FIG. 5B is a schematic front view of the exhaust heat recovery device in an embodiment different from FIG. 1, and FIG. 5C is a schematic front view. , Is a schematic plan view of the exhaust heat recovery device of FIG. 5B.

Hereinafter, embodiments to which the present disclosure has been applied will be described with reference to the drawings.
[1. First Embodiment]
[1-1. composition]
The exhaust heat recovery device 1 shown in FIG. 1 is provided in the exhaust gas flow path of the internal combustion engine, and recovers the heat of the exhaust gas G to the cooling water. Examples of the internal combustion engine provided with the exhaust heat recovery device 1 include a gasoline engine or a diesel engine used in an automobile.

The exhaust heat recovery device 1 includes a main flow path 2, a heat exchange unit 3, a valve 4, and an actuator 5. The exhaust heat recovery device 1 can be switched between a recovery mode in which exhaust heat recovery is performed, a non-recovery mode in which exhaust heat recovery is not performed, and an EGR mode in which exhaust gas recirculation is performed.

<Main flow path>
The main flow path 2 has an introduction port 21, a main discharge port 22, a supply port 23, and a return port 24 (see FIG. 2).

The introduction port 21 introduces the exhaust gas G into the exhaust heat recovery device 1. The main exhaust port 22 discharges the exhaust gas G to the outside of the exhaust heat recovery device 1. The supply port 23 supplies the exhaust gas G to the heat exchange unit 3. The return port 24 is an opening through which the exhaust gas G that has passed through the heat exchange unit 3 returns to the main flow path 2.

A valve 4 is arranged in the main flow path 2. Further, in the present embodiment, the introduction port 21 and the main discharge port 22 are arranged so as to face each other. That is, the flow direction of the exhaust gas G at the introduction port 21 is parallel to the flow direction of the exhaust gas G at the main discharge port 22. Further, the center of the introduction port 21 overlaps with the main exhaust port 22 when viewed from the flow direction of the exhaust gas G in the introduction port 21. A part of the main flow path 2 may be curved.

<Heat exchange section>
The heat exchange unit 3 is a portion that exchanges heat between the exhaust gas G of the internal combustion engine and the cooling water. The heat exchange unit 3 is arranged side by side with respect to the main flow path 2 on the second direction D2 side perpendicular to the first direction D1 through which the exhaust gas G flows in the main flow path 2.

As shown in FIG. 2, the heat exchange unit 3 has a heat transfer member 31, an intake port 32, and a first discharge port 33. Further, as shown in FIG. 1, the heat exchange unit 3 further has a second discharge port 34, a first water flow port 35, and a second water flow port 36.

The heat exchange unit 3 exchanges heat between the exhaust gas flowing outside the heat transfer member 31 and the cooling water flowing inside the heat transfer member 31 via the heat transfer member 31. As a result, the heat exchange unit 3 gives the heat of the exhaust gas to the cooling water. As the heat transfer member 31, a tube having a plurality of fins attached to the outer surface, a plurality of plates, and the like can be used.

As shown in FIG. 2, the intake port 32 is connected to the supply port 23 of the main flow path 2. The first discharge port 33 is connected to the return port 24 of the main flow path 2. The exhaust gas G introduced into the main flow path 2 enters the inside of the heat exchange unit 3 from the supply port 23 and the intake port 32, exchanges heat with the heat transfer member 31, and then returns the return port 24 and the first. It is discharged from the discharge port 33 into the main flow path 2.

The cooling water for cooling the exhaust gas G is supplied into the heat exchange unit 3 from one of the first water passage port 35 and the second water passage port 36, passes through the heat transfer member 31, and then passes through the first water passage port 35 and the second water passage port 35 and the second. It is discharged from the other side of the water passage 36.

The heat transfer member 31 is in the first portion 31A in which the exhaust gas G flows in the third direction D3 orthogonal to the first direction D1 and the second direction D2, and in the fourth direction D4 opposite to the third direction D3, respectively. It has a second part 31B through which the exhaust gas G flows.

The second part 31B is located downstream of the first part 31A in the flow direction of the exhaust gas, and is arranged on the first direction D1 side of the first part 31A. The exhaust gas G that has passed through the first part 31A flows into the first direction D1 and then enters the second part 31B. The exhaust gas G that has passed through the second part 31B flows toward the first discharge port 33 in the fifth direction D5 opposite to the second direction D2.

The second exhaust port 34 shown in FIG. 1 is an opening for discharging the exhaust gas G into an exhaust gas recirculation flow path (not shown) that supplies the exhaust gas G to the internal combustion engine. That is, the exhaust gas recirculation path 100 is connected to the second exhaust port 34.

The second exhaust port 34 is provided in the middle of the flow path of the exhaust gas G in the heat exchange unit 3. In the present embodiment, the second exhaust port 34 is provided between the first part 31A and the second part 31B of the heat transfer member 31 in the flow of the exhaust gas G. The second discharge port 34 is arranged on the upstream side of the heat transfer member 31.

Therefore, in the EGR mode in which the exhaust gas recirculation is performed, a part of the exhaust gas supplied to the heat exchange unit 3 is discharged from the second exhaust port 34 toward the internal combustion engine.

<Valve>
The valve 4 adjusts the supply amount of the exhaust gas G from the main flow path 2 to the heat exchange unit 3. The opening degree of the valve 4 changes according to the mode of the exhaust heat recovery device 1.

As shown in FIG. 2, the valve 4 is a butterfly valve arranged at a position in the main flow path 2 where at least a part thereof overlaps with the supply port 23 in the flow direction of the exhaust gas G.

The valve 4 is displaceable between the recovery mode, the non-recovery mode, and the EGR mode. However, the valve 4 may be displaceable in other modes (that is, any valve opening).

The valve 4 is opened and closed by an actuator 5 described later. As shown in FIGS. 3A, 3B, and 3C, the valve 4 has a rod body 41, a first wing 42, a second wing 43, and a spring 44.

(Stick body)
The rod body 41 is a rod-shaped member (that is, a stem) connected to the actuator 5. The rod body 41 rotates about its axis by driving the actuator 5. The first wing 42 and the second wing 43 are displaced by the axial rotation of the rod body 41. In the present embodiment, as shown in FIG. 2, the rod body 41 is arranged so as to pass through the radial center of the main flow path 2.

(1st feather)
The first wing 42 is a disc that is fixed to the rod body 41 and extends radially outward from the rod body 41. Specifically, as shown in FIG. 3A, the first wing 42 has a first pressure receiving portion 42A and two mounting portions 42B and 42C.

The first pressure receiving portion 42A is a portion for blocking a part of the main flow path 2 in the recovery mode or the non-recovery mode, and changes the direction of the flow of the exhaust gas G by the collision with the exhaust gas G. The outer shape of the first pressure receiving portion 42A is designed according to the cross-sectional shape of the main flow path 2.

The two mounting portions 42B and 42C are portions extending in the radial direction of the rod body 41 from the first pressure receiving portion 42A, and overlap with the outer peripheral surface of the rod body 41. The two mounting portions 42B and 42C are fixed to the rod body 41 at positions separated from each other in the axial direction of the rod body 41. Further, the two mounting portions 42B and 42C extend to a position farther than the rod body 41 (that is, to a position beyond the rod body 41) with respect to the first pressure receiving portion 42A.

(2nd feather)
The second wing 43 is a disc that is attached to the rod body 41 so as to be rotatable around the rod body 41 and extends radially outward from the rod body 41. Specifically, as shown in FIG. 3B, the second wing 43 has a second pressure receiving portion 43A, a locking portion 43B, and two regulating portions 43C and 43D.

The second pressure receiving portion 43A is a portion for blocking a part of the main flow path 2 in cooperation with the first pressure receiving portion 42A of the first blade 42. The second pressure receiving unit 43A changes the direction of the flow of the exhaust gas G mainly due to the collision with the exhaust gas G in the recovery mode.

The second pressure receiving portion 43A has the same shape as the first pressure receiving portion 42A. That is, the area where the first wing 42 receives the pressure of the exhaust gas G in the direction of rotating the rod 41 in the first rotation direction C1 (that is, the area of the first pressure receiving portion 42A) is such that the second wing 43 has the rod 41. Is equal to the area that receives the pressure of the exhaust gas G in the direction of rotating in the second rotation direction C2 (that is, the area of the second pressure receiving portion 43A).

The locking portion 43B is a portion extending in the radial direction of the rod body 41 from the second pressure receiving portion 43A, and overlaps with the outer peripheral surface of the rod body 41. The locking portion 43B is arranged between the two mounting portions 42B and 42C of the first blade 42. The locking portion 43B is curved along the outer peripheral surface of the rod body 41, and covers a part of the outer peripheral surface of the rod body 41 in the circumferential direction. The locking portion 43B abuts on the rod 41, but is not fixed to the rod 41.

The two regulating portions 43C and 43D each extend from the second pressure receiving portion 43A along the outer peripheral surface of the rod 41 in the first rotation direction C1 (see FIG. 3C). The two regulating portions 43C and 43D are arranged so as to sandwich the locking portion 43B.

As shown in FIG. 3C, one regulating portion 43C comes into contact with one mounting portion 42B of the first wing 42 in a state where the first pressure receiving portion 42A and the second pressure receiving portion 43A are arranged in parallel. The same applies to the relationship between the other regulating portion 43D and the other mounting portion 42C.

The locking portion 43B allows the second wing 43 to rotate in any direction (that is, the first rotation direction C1 and the second rotation direction C2) with the rod body 41 as the central axis. Further, the two regulating portions 43C and 43D regulate that the first pressure receiving portion 42A and the second pressure receiving portion 43A rotate in the second rotation direction C2 from the parallel state. That is, in the state of FIG. 3C, the second wing 43 can rotate only in the first rotation direction C1.

(Spring)
The spring 44 is an elastic body that urges the second wing 43 in the second rotation direction C2 around the rod 41. Specifically, the spring 44 is a torsion spring wound around the outer peripheral surface of the rod body 41. The axis of the spring 44 and the axis of the rod 41 are arranged in parallel.

The spring 44 has a central portion 44A and two end portions 44B, 44C, as shown in FIG. 3B. The central portion 44A is a portion that protrudes in the radial direction between the two end portions 44B and 44C of the spring 44, and abuts on the surface of the second wing 43 on the first rotation direction C1 side of the second pressure receiving portion 43A. There is. The two end portions 44B and 44C each project to the side opposite to the central portion 44A and abut on the surface of the first blade 42 on the second rotation direction C2 side of the first pressure receiving portion 42A.

When no external force is applied to the second wing 43, the second pressure receiving portion 43A is held at a position parallel to the first pressure receiving portion 42A by the spring 44 and the two regulating portions 43C and 43D. When a force of a certain magnitude in the first rotation direction C1 is applied to the second wing 43, the second wing 43 rotates in the first rotation direction C1 while elastically deforming the spring 44.

(Valve mode)
In the recovery mode shown in FIG. 2, the first pressure receiving portion 42A of the first wing 42 and the second pressure receiving portion 43A of the second wing 43 are arranged in parallel with each other. The radial end of the first wing 42 abuts on the inner surface of the main flow path 2 opposite to the supply port 23.

Further, the radial end portion of the second wing 43 abuts on the downstream side of the supply port 23 on the inner surface of the main flow path 2. Exhaust gas G collides with the second wing 43 on the surface on the first rotation direction C1 side. Therefore, the second wing 43 receives the gas pressure in the second rotation direction C2, but the rotation is restricted by the two regulating portions 43C and 43D. Therefore, the second wing 43 does not rotate with respect to the rod body 41.

In the recovery mode, the first wing 42 and the second wing 43 block the flow path to the main flow path 2 on the downstream side of the supply port 23. Therefore, the entire amount of the exhaust gas G is guided to the supply port 23 and supplied to the heat exchange unit 3.

In the non-recovery mode shown in FIG. 4A, the first wing 42 is arranged at a position rotated by 180 ° about the rod 41 from the recovery mode. The radial end of the first wing 42 abuts on the upstream side of the supply port 23 on the inner surface of the main flow path 2.

The second wing 43 is further first from the position rotated 90 ° around the rod 41 from the recovery mode due to the collision of the exhaust gas G with the surface on the second rotation direction C2 side (that is, the pressure of the exhaust gas G). It rotates in the rotation direction C1. That is, the second wing 43 can rotate in the direction of expanding the passage area of the exhaust gas G in the main flow path 2 when limiting the supply amount of the exhaust gas G to the supply port 23 (that is, in the non-recovery mode). be.

Due to the rotation of the second wing 43, in the non-recovery mode, the first pressure receiving portion 42A of the first wing 42 and the second pressure receiving portion 43A of the second wing 43 are arranged so as to intersect each other. The exhaust gas G is bypassed by the supply port 23 and flows through the main flow path 2 toward the main discharge port 22 by the first blade 42 and the second blade 43. As a result, the supply of the exhaust gas G to the heat exchange unit 3 is restricted.

In the EGR mode shown in FIG. 4B, the first wing 42 and the second wing 43 are arranged so that their respective pressure receiving portions are parallel to the flow direction of the exhaust gas G. The second pressure receiving portion 43A of the second wing 43 receives almost no pressure from the exhaust gas G, or the pressure is smaller than the elastic force of the spring 44, so that the second pressure receiving portion 43A is maintained in a state parallel to the first pressure receiving portion 42A.

In the EGR mode, a part of the exhaust gas G is supplied to the heat exchange unit 3 through the supply port 23, and is supplied to the exhaust gas recirculation path 100 from the second exhaust port 34 of the heat exchange unit 3. The remaining exhaust gas G bypasses the heat exchange unit 3 and is discharged from the main exhaust port 22.

In any mode, the second pressure receiving portion 43A of the second wing 43 is on the downstream side of the flow of the exhaust gas G in the main flow path 2 (that is, the first direction D1) than the first pressure receiving portion 42A of the first wing 42. Located on the side).

<Actuator>
The actuator 5 operates the valve 4. Specifically, the actuator 5 displaces the valve 4 to at least one of the recovery mode, the non-recovery mode, and the EGR mode by rotating the rod 41 around the axis.

As the actuator 5, a motor driven by power such as electric power, pneumatic pressure, and hydraulic pressure, a thermoactuator using a thermal expansion body that expands and contracts in response to the temperature of cooling water, and the like can be used.

[1-2. effect]
According to the embodiment described in detail above, the following effects can be obtained.
(1a) Since the valve 4 is arranged in the main flow path 2 at a position overlapping the supply port 23 to the heat exchange unit 3, the exhaust heat recovery device 1 can be miniaturized. Further, when the flow of the exhaust gas G to the heat exchange unit 3 is regulated, the second wing 43 of the valve 4 rotates in the direction of expanding the passing area of the exhaust gas G, thereby reducing the pressure loss in the main flow path 2. can.

(1b) The area where the first wing 42 receives the pressure of the exhaust gas G and the area where the second wing 43 receives the pressure of the exhaust gas G are equal, so that the pressure received by the first wing 42 from the exhaust gas G and the second wing 42 are equal. The pressure received by the wing 43 from the exhaust gas G is substantially equal to that of the wing 43. Therefore, the load of the actuator 5 that rotates the valve 4 can be reduced.

(1c) Since the second wing 43 can rotate in the direction of expanding the passing area of the exhaust gas G by the pressure of the exhaust gas G, the mechanism for rotating the second wing 43 can be simplified.

(1d) Since the heat exchange unit 3 has the second exhaust port 34, a part of the exhaust gas G can be recirculated to the internal combustion engine by adjusting the opening degree of the valve 4. That is, the EGR function can be added to the exhaust heat recovery device 1 while downsizing the exhaust heat recovery device 1.

[2. Other embodiments]
Although the embodiments of the present disclosure have been described above, it is needless to say that the present disclosure is not limited to the above-described embodiments and can take various forms.

(2a) In the exhaust heat recovery device 1 of the above embodiment, the area where the first wing 42 receives the pressure of the exhaust gas G may be different from the area where the second wing 43 receives the pressure of the exhaust gas G. Further, the rod body 41 does not necessarily have to be arranged at a position passing through the radial center of the main flow path 2.

(2b) In the exhaust heat recovery device 1 of the above embodiment, the configuration of the valve 4 is an example, and if the second wing 43 can rotate in the direction of expanding the passage area of the exhaust gas G of the main flow path 2, the above Not limited to the configuration.

For example, as shown in FIG. 5A, two springs 45A and 45B may be provided in the valve 4 instead of the spring 44. The two springs 45A and 45B are leaf springs arranged so as to straddle the first pressure receiving portion 42A of the first wing 42 and the second pressure receiving portion 43A of the second wing 43, respectively. The second pressure receiving portion 43A is urged in the rotational direction about the rod 41 by the two springs 45A and 45B.

Further, the second wing 43 may be rotated by power instead of the pressure of the exhaust gas G. For example, the second wing 43 may be configured to rotate with respect to the rod 41 by an actuator.

(2c) In the exhaust heat recovery device 1 of the above embodiment, the heat exchange unit 3 does not necessarily have to have the second exhaust port 34. That is, the exhaust heat recovery device 1 does not necessarily have to have an EGR function.

(2d) In the exhaust heat recovery device 1 of the above embodiment, the shape of the heat exchange unit 3 is an example. For example, the exhaust heat recovery device 11 shown in FIGS. 5B and 5C includes a coaxial type heat exchange unit 13 arranged in an annular shape on the outer periphery of the main flow path 2. The heat exchange unit 13 takes in the exhaust gas G from the supply port 23 of the main flow path 2. The valve 4 is arranged at a position overlapping the supply port 23.

(2e) The functions of one component in the above embodiment may be dispersed as a plurality of components, or the functions of the plurality of components may be integrated into one component. Further, a part of the configuration of the above embodiment may be omitted. Further, at least a part of the configuration of the above embodiment may be added or substituted with respect to the other configurations of the above embodiment. It should be noted that all aspects included in the technical idea specified from the wording described in the claims are embodiments of the present disclosure.

1,11 ... Exhaust heat recovery device, 2 ... Main flow path, 3,13 ... Heat exchange section, 4 ... Valve,
5 ... Actuator, 21 ... Introduction port, 22 ... Main discharge port, 23 ... Supply port, 24 ... Return port,
31 ... Heat transfer member, 31A ... Part 1, 31B ... Part 2, 32 ... Intake port,
33 ... 1st outlet, 34 ... 2nd outlet, 35 ... 1st outlet, 36 ... 2nd outlet,
41 ... rod body, 42 ... first wing, 42A ... first pressure receiving part, 42B, 42C ... mounting part,
43 ... 2nd wing, 43A ... 2nd pressure receiving part, 43B ... locking part,
43C, 43D ... Regulatory part, 44 ... Spring, 44A ... Central part, 44B, 44C ... End part,
45A, 45B ... Spring, 100 ... Exhaust gas recirculation path.

Claims (5)

A heat exchange unit that exchanges heat between the exhaust gas of the internal combustion engine and the cooling water,
A main flow path having an introduction port for introducing the exhaust gas, a main exhaust port for discharging the exhaust gas to the outside, and a supply port for supplying the exhaust gas to the heat exchange unit.
A valve that is arranged at a position where at least a part of the main flow path overlaps the supply port in the flow direction of the exhaust gas and that adjusts the amount of the exhaust gas supplied from the main flow path to the heat exchange unit.
The actuator that operates the valve and
Equipped with
The valve is
A rod body that rotates around the axis by the actuator,
The first wing, which is fixed to the rod and extends radially outward from the rod,
A second wing that is attached to the rod so as to be rotatable about the rod as a central axis and extends radially outward from the rod.
Have,
Said second wings, at the time of limiting the supply amount of the exhaust gas to the supply port, Ri rotatable der in the direction of enlarging the passage area of the exhaust gas in the main passage,
The rod body is an exhaust heat recovery device whose axis can be rotated so that the main flow path is blocked by the first blade and the second blade. The exhaust heat recovery device according to claim 1.
An exhaust heat recovery device in which the area where the first wing receives the pressure of the exhaust gas is equal to the area where the second wing receives the pressure of the exhaust gas. The exhaust heat recovery device according to claim 1 or 2.
The second wing is an exhaust heat recovery device that can rotate in the expanding direction by the pressure of the exhaust gas. The exhaust heat recovery device according to any one of claims 1 to 3.
The heat exchange unit is
A first exhaust port for discharging the exhaust gas toward the main flow path,
A second exhaust port for discharging the exhaust gas to the exhaust gas recirculation flow path for supplying the exhaust gas to the internal combustion engine, and
Has an exhaust heat recovery device. The exhaust heat recovery device according to any one of claims 1 to 4.
The rod body is an exhaust heat recovery device arranged inside the main flow path.

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