WO2019009235A1 - Combustion chamber cooling mechanism - Google Patents

Abstract

This combustion chamber cooling mechanism is provided with: a bottom wall in contact with a combustion chamber; an upper wall disposed on the opposite side of the combustion chamber from the bottom wall; and a plurality of sidewalls which are in contact with the bottom wall and the upper wall, extend in a first direction extending along the bottom wall, and are arranged next to each other in a second direction perpendicular to the first direction. A flow passage having a substantially constant width is formed between the bottom wall and the upper wall and between sidewalls adjacent to each other in the second direction. A heat dispersion structure is provided in the flow passage, the heat dispersion structure allowing heat transmitted from the combustion chamber through the bottom wall to be transmitted dispersedly to a refrigerant flowing through the flow passage.

Description

Combustion chamber cooling mechanism

The present invention relates to a combustion chamber cooling mechanism.
Priority is claimed on Japanese Patent Application No. 2017-130569, filed July 3, 2017, the content of which is incorporated herein by reference.

Conventionally, in order to cool the combustion gas flowing in the combustion chamber, for example, a combustion chamber cooling mechanism as described in Patent Document 1 is used.

The cooling mechanism of the combustion chamber disclosed in Patent Document 1 includes a bottom wall contacting the combustion chamber, an upper wall, and a plurality of side walls. A flow path is formed between the bottom wall and the upper wall and between adjacent partition walls. Each flow path includes a first flow path and a second flow path extending along the first direction, and a connection flow path disposed between the first flow path and the second flow path. The second flow path is arranged to be offset in a second direction along the bottom wall and orthogonal to the first direction with respect to the first flow path.

The refrigerant flowing from the first flow path into the connection flow path is agitated by collision in the connection flow path.
The stirred refrigerant flows into the second flow path from the connection flow path.

Japanese Patent Application Laid-Open No. 2016-166595

However, in the above-described conventional combustion chamber cooling mechanism, since the first flow passage and the second flow passage are separated from each other in the second direction, the width of the flow passage becomes wider in the second direction. Therefore, there is a problem that it is difficult to arrange many flow paths per unit length in the second direction.
In addition, it is desirable to efficiently cool the combustion gas flowing in the combustion chamber.

The present invention provides a cooling mechanism of the combustion chamber which arranges more flow paths per unit length in the second direction and effectively transfers the heat from the combustion chamber to the refrigerant.

According to one aspect of the present invention, the cooling mechanism of the combustion chamber includes a bottom wall in contact with the combustion chamber, an upper wall disposed on the opposite side of the bottom wall to the combustion chamber, the bottom wall and the bottom wall. A plurality of side walls extending in a first direction along the bottom wall, the side walls being in contact with the top wall and arranged in a second direction orthogonal to the first direction; and between the bottom wall and the top wall A flow passage having a substantially constant width is formed between the side walls adjacent to each other in the second direction, and the combustion chamber is transmitted to the refrigerant flowing in the flow passage via the bottom wall. A heat dissipating structure is provided in the flow path for distributing and transferring the heat of the fluid.

Further, in the above-described combustion chamber cooling mechanism, the heat dispersion structure includes a partition member formed in a spiral wing shape which extends in the axial direction of the flow passage in the flow passage and goes around the axial line. It is also good.
Further, in the above-described combustion chamber cooling mechanism, the heat dispersion structure is disposed in the flow passage, and the guide of a shape gradually approaching the bottom wall as going from one side to the other side in the axial direction of the flow passage. A member may be provided.

Further, in the above-described combustion chamber cooling mechanism, the heat dispersion structure may have a shape in which the flow passage extends in the first direction while meandering in the second direction.
Further, in the above-described combustion chamber cooling mechanism, the heat dispersion structure may have a shape in which the width of the flow passage gradually increases from the bottom wall side toward the upper wall side.

According to the combustion chamber cooling mechanism of the present invention, since the width of the flow path is substantially constant, more flow paths can be disposed per unit length in the second direction. Furthermore, since the heat dispersion structure is provided in the flow path, the temperature of the refrigerant on the bottom wall side heated by the combustion chamber in the flow path is higher than the temperature of the other portions in the flow path The heat from the combustion chamber can be effectively transferred to the refrigerant by suppressing the increase in temperature.

It is a perspective view of a rocket engine in which a cooling mechanism of a 1st embodiment of the present invention is used. It is a sectional view by plane A1 which intersects perpendicularly with the axis in the burner of the rocket engine. It is the perspective view which permeate | transmitted the upper wall in FIG. It is the perspective view which permeate | transmitted the upper wall of the principal part in the same cooling mechanism. FIG. 5 is a cross-sectional view of FIG. 4 along the cutting line VV. It is a perspective view of the partition member of the same cooling mechanism. FIG. 5 is a cross-sectional view of FIG. 4 along the section line VII-VII. FIG. 5 is a cross-sectional view of FIG. 4 along the cutting line VIII-VIII. FIG. 5 is a cross-sectional view of FIG. 4 along the line IX-IX. It is the perspective view which permeate | transmitted the upper wall of the principal part in the cooling mechanism of 2nd Embodiment of this invention. It is an XI direction arrow line view in FIG. It is the perspective view which permeate | transmitted the upper wall of the principal part in the cooling mechanism of 3rd Embodiment of this invention. It is sectional drawing orthogonal to the axis line of the flow path in area | region A3 in FIG. It is the perspective view which permeate | transmitted the upper wall of the principal part in the cooling mechanism of 4th Embodiment of this invention. It is sectional drawing orthogonal to the axis line of the flow path in the flow path of the same cooling mechanism.

First Embodiment
Hereinafter, a combustion chamber cooling mechanism (hereinafter referred to as a cooling mechanism) according to a first embodiment of the present invention will be described with reference to FIGS. 1 to 9.
FIG. 1 is a perspective view of a rocket engine 1 in which the cooling mechanism of the present embodiment is used. The rocket engine 1 includes a combustor 11 and a nozzle 16. The combustor 11 has a cooling mechanism 12 formed in a cylindrical shape. A combustion chamber 13 is formed inside the cooling mechanism 12.

As shown in FIGS. 2 and 3, the cooling mechanism 12 includes a bottom wall 21, an upper wall 22, and a plurality of side walls 23. In FIG. 2, the cooling mechanism 12 is shown thick in the radial direction X of the combustor 11 in order to make the side wall 23 and the like easy to see.
The bottom wall 21 is formed in a cylindrical shape and is in contact with the combustion chamber 13.
The top wall 22 is disposed on the opposite side of the bottom wall 21 to the combustion chamber 13 so as to face the bottom wall 21. The upper wall 22 is formed in a cylindrical shape, and surrounds the bottom wall 21 from the outer side in the radial direction X and is arranged coaxially with the bottom wall 21.

The side wall 23 extends in the first direction Z along the bottom wall 21. In the present embodiment, the first direction Z is a direction along the central axis of the combustor 11. The side wall 23 is in contact with the bottom wall 21 and the top wall 22 respectively. The plurality of side walls 23 are arranged side by side in a second direction Y orthogonal to the first direction Z. In the present embodiment, the second direction Y is the circumferential direction of the combustor 11. In addition, since the radial direction X and the second direction Y which is the circumferential direction change depending on the position in the circumferential direction, the radial direction X, the first direction Z and the second direction Y are shown in FIG. 2 and FIG. Show.
The plurality of side walls 23 are integrally formed with the bottom wall 21.
A channel C1 is formed between the bottom wall 21 and the top wall 22 and between the side walls 23 adjacent in the second direction Y. In FIG. 3 and FIGS. 4, 10, 12 and 14 described later, the upper wall 22 is shown transparent. Moreover, in FIG. 3, the number of the plurality of flow paths C1 is reduced and shown.
Below, several flow paths C1 among a plurality of flow paths C1 which constitute cooling mechanism 12, and bottom wall 21, top wall 22, and side wall 23 which constitute these flow paths C1 are explained.

FIG. 4 is a perspective view of three flow paths C1 of the cooling mechanism 12. In the present embodiment, the side wall 23 linearly extends along the first direction Z. The axis of the flow path C1 extends along the first direction Z. The channel C1 has a substantially constant width regardless of the position in the first direction Z. Here, that the width of the flow channel C1 is substantially constant regardless of the position in the first direction Z is, for example, the ratio of the maximum width of the flow channel C1 to the minimum width of the flow channel C1 according to the position in the first direction Z Means that it is within 140%. More preferably, this ratio is within 120%.
As shown in FIG. 5, for example, the cross-sectional shape of the flow path C1 by a plane orthogonal to the first direction Z is a rectangular shape that is long in the radial direction X. The cross-sectional shape of the side wall 23 by a plane orthogonal to the first direction Z is a rectangular shape elongated in the radial direction X.

As shown in FIG. 4 to FIG. 6, a partition member (heat dispersion structure) 26 is disposed in the flow path C1. The partition member 26 is formed in a spiral wing shape extending in the first direction Z in the flow path C1 and rotating around the axis of the flow path C1. In other words, the partition member 26 passes through the axis of the flow path C1 at each position in the axial direction of the flow path C1, and both ends respectively contact at least one of the bottom wall 21, the upper wall 22 and the side wall 23 ing. The partition member 26 circulates around the axis of the channel C1 as it goes from the first end to the second end of the channel C1, whereby the channel C1 is divided into a first divided channel C2 and a second divided flow. It divides into road C3.
As shown in FIG. 5, the cross-sectional shape orthogonal to the axis of the flow path C1 of the partition member 26 is a rectangular shape. Hereinafter, in the rectangular cross-sectional shape of the partition member 26, the dimension with the longer length is referred to as the width, and the dimension with the shorter length is referred to as the thickness.
The refrigerant R1 flows in the divided flow paths C2 and C3. The type of the refrigerant R1 is not particularly limited. For example, the refrigerant R1 is liquid hydrogen. For example, as shown in FIG. 4, the refrigerant R1 flows in the direction of the arrow F1 from one side to the other side along the first direction Z.

As shown in FIGS. 4 and 6, the partition member 26 makes one rotation around the axis of the flow path C1 for each reference length L1 in the first direction Z. More specifically, FIG. 5 is a cross-sectional view of the cooling mechanism 12 along the cutting line VV in FIG. In FIG. 5, the partition member 26 extends along the second direction Y and is in contact with the pair of side walls 23. In the present embodiment, the thickness of the partition member 26 is constant regardless of the position in the first direction Z.
FIG. 7 is a cross-sectional view of the cooling mechanism 12 taken along the line VII-VII in FIG. The partition member 26 is inclined so as to gradually approach the bottom wall 21 as it goes from one side (left side in the drawing) to the other side (right side in the drawing) of the second direction Y. The partition members 26 are in contact with the pair of side walls 23 respectively.

FIG. 8 is a cross-sectional view of the cooling mechanism 12 taken along line VIII-VIII in FIG. The partition member 26 extends in the radial direction X and is in contact with the bottom wall 21 and the top wall 22 respectively.
FIG. 9 is a cross-sectional view of the cooling mechanism 12 taken along the line IX-IX in FIG. The partition member 26 is inclined so as to gradually approach the upper wall 22 as it goes from one side to the other side in the second direction Y. The partition members 26 are in contact with the pair of side walls 23 respectively.

As shown in FIG. 9, as the refrigerant R1 flows in the direction of the arrow F1, the first divided flow passage C2 disposed at the position on the bottom wall 21 side of the flow passage C1 in FIG. Placed in the position of. Similarly, as shown in FIG. 9, the second divided flow passage C3 disposed at the upper wall 22 side of the flow passage C1 in FIG. 5 is the bottom of the flow passage C1 as shown in FIG. 9 as the refrigerant R1 flows in the direction of arrow F1. It is disposed at a position on the wall 21 side. Of the divided channels C 2 and C 3, the channel disposed at the position on the bottom wall 21 side is easily heated by the combustion chamber 13, and the channel disposed at the position on the upper wall 22 side is heated by the combustion chamber 13. It is hard to be done.
That is, as the refrigerant R1 flows in the direction of the arrow F1, the position of the first divided channel C2 alternates with the position on the bottom wall 21, the position on the upper wall 22, the position on the bottom wall 21,. Corresponding to this, the position of the second divided flow passage C3 is alternately switched to the position on the upper wall 22 side, the position on the bottom wall 21 side, the position on the upper wall 22 side,.

By the division channels C2 and C3 arranged at the position on the bottom wall 21 side being interchanged according to the position in the first direction Z, the refrigerant R1 flowing in the division channels C2 and C3 is transmitted via the bottom wall 21. The heat from the combustion chamber 13 is dispersed and transmitted.
By changing the distance from the combustion chamber 13 of the refrigerant R1 flowing in the divided flow paths C2 and C3 in the first direction Z, only a part of the refrigerant R1 flowing in the divided flow paths C2 and C3 is changed by the combustion chamber 13 Overheating is prevented.

In the present embodiment, since the thickness of the partition member 26 is constant, when the partition member 26 extends along the radial direction X and the width of the partition member 26 is relatively long as shown in FIG. The cross-sectional area orthogonal to the axis of the paths C2 and C3 is narrowed.
On the other hand, as shown in FIG. 5, when the partition member 26 extends in the second direction Y and the width of the partition member 26 is relatively short, the cross-sectional area orthogonal to the axis of the divided channels C2 and C3 becomes wide. .

The bottom wall 21, the top wall 22, the plurality of side walls 23, and the partition member 26 are formed of metal such as copper. In addition, in order to manufacture the cooling mechanism 12, a known three-dimensional printer or the like capable of printing a three-dimensional shape can be used.

Next, the operation of the rocket engine 1 configured as described above will be described focusing on the cooling mechanism 12.
When fuel is burned in the combustion chamber 13, combustion gas of several thousand degrees C. flows in the combustion chamber 13. The combustion gas flows in the direction opposite to the direction of the arrow F1. The refrigerant R1 flows in the direction of the arrow F1 in each of the divided flow paths C2 and C3 by transport means such as a turbo pump (not shown). Since the partition member 26 is disposed in the channel C1 and the divided channels C2 and C3 are formed, the refrigerant R1 disposed at the position on the combustion chamber 13 side in the first direction Z, and the combustion chamber 13 The refrigerant R1 disposed at a position away from R.sub.1 is alternately switched. When the relatively low temperature refrigerant R1 is periodically disposed near the combustion chamber 13, the temperature gradient per unit length of the combustion gas and the refrigerant R1 increases, and the combustion gas is efficiently cooled.

As described above, according to the cooling mechanism 12 of the present embodiment, since the width of the channel C1 is substantially constant, more channels C1 can be disposed per unit length in the second direction Y. . Furthermore, since the partition member 26 is disposed in the flow passage C1, the temperature of the refrigerant R1 in the portion on the side of the bottom wall 21 heated by the combustion chamber 13 in the flow passage C1 is the other temperature in the flow passage C1. The heat from the combustion chamber 13 can be effectively dispersed and transmitted to the refrigerant R1 while suppressing the temperature from becoming excessively higher than the temperature of the Therefore, the cooling mechanism 12 can be effectively cooled by the refrigerant R1.

Since the heat dispersion structure includes the partition member 26, as the refrigerant R1 flows in the direction of the arrow F1 in the first direction Z, the divided channels C2 and C3 disposed at the position on the bottom wall 21 side are alternately switched. As a result, the temperatures of the refrigerant R1 flowing in the divided flow paths C2 and C3 become equal to each other, and the heat from the combustion chamber 13 can be effectively transferred to the refrigerant R1.

In the present embodiment, regardless of the position in the first direction Z, the cross-sectional area orthogonal to the axis of the first divided flow channel C2 is constant, and the second divided flow is not dependent on the position in the first direction Z. The thickness of the partition member 26 may be adjusted so that the cross-sectional area orthogonal to the axis of the passage C3 is constant. Specifically, the product of the width of the partition member 26 and the thickness of the partition member 26 is adjusted to be constant.
With this configuration, the cross-sectional areas of the divided channels C2 and C3 become constant regardless of the position in the first direction Z, and the pressure loss of the refrigerant R1 flowing in the divided channels C2 and C3 is reduced. be able to.

Second Embodiment
Next, a second embodiment of the present invention will be described with reference to FIGS. 10 and 11. FIG. In the present embodiment, the same parts as those of the above-described embodiment are denoted by the same reference numerals, and the description thereof is omitted. Only different points will be described.
As shown in FIG. 10, the cooling mechanism 32 of the present embodiment includes a guide member (heat distribution structure) 33 disposed in the flow path C1 instead of the partition member 26 of the cooling mechanism 12 of the first embodiment. ing. The guide member 33 is formed to gradually approach the bottom wall 21 as it goes from one side to the other side in the first direction Z. The refrigerant R1 flows in the flow path C1 in the direction of the arrow F1 from one side to the other side in the first direction Z.

As shown in FIGS. 10 and 11, in the present embodiment, the guide member 33 has a wing shape. For example, the guide member 33 is a wing shape such as NACA 6415. The outer surface of the guide member 33 preferably has a smooth shape without corners. The smooth shape of the guide member 33 can suppress pressure loss from occurring in the refrigerant R1.
The elevation angle of the guide member 33 with respect to the first direction Z is, for example, 15 °. As shown in FIG. 11, it is preferable that the distance L3 between the guide member 33 and the bottom wall 21 and the distance L4 between the guide member 33 and the upper wall 22 be equal to each other.
As shown in FIG. 10, a plurality of guide members 33 may be arranged at intervals in the first direction Z.

Next, the operation of the cooling mechanism 32 configured as described above will be described.
As shown in FIG. 11, of the refrigerant R1 flowing toward the other side along the first direction Z indicated by the arrow F1, a location relatively away from the bottom wall 21 in the flow path C1 as indicated by the arrow F3 The refrigerant R1 having a relatively low temperature flows. The refrigerant R1 is guided by the guide member 33 as it travels to the other side in the first direction Z, and flows relatively near the bottom wall 21 as indicated by an arrow F4.
Heat from the combustion chamber 13 is effectively transferred to the relatively low temperature refrigerant R1 by flowing the relatively low temperature refrigerant R1 at a position relatively close to the bottom wall 21.

As described above, according to the cooling mechanism 32 of the present embodiment, more flow channels C1 can be disposed per unit length in the second direction Y.
Furthermore, since the cooling mechanism 32 includes the guide member 33, the heat from the combustion chamber 13 is dispersed not only to the refrigerant R1 having a relatively high temperature but also to the refrigerant R1 having a relatively low temperature guided by the guide member 33. It can be transmitted. Therefore, the heat from the combustion chamber 13 can be effectively transferred to the refrigerant R1 having a relatively low temperature.

In the present embodiment, the guide member 33 has a wing shape, but the shape of the guide member is not limited to this. The guide member may be flat or the like.

Third Embodiment
Next, a third embodiment of the present invention will be described with reference to FIG. 12 and FIG. In the present embodiment, the same parts as those of the above-described embodiment are denoted by the same reference numerals, and the description thereof is omitted. Only different points will be described.
As shown in FIG. 12, in the cooling mechanism 37 of the present embodiment, the flow path C5 meanders in the second direction Y in the first direction Z, instead of the partition member 26 of the cooling mechanism 12 of the first embodiment. The heat dissipating structure 38 has an extended shape.
Even when the channel C5 meanders, the channel C5 has a substantially constant width regardless of the position in the first direction Z. For this reason, even if the plurality of flow paths C5 are arranged in the second direction Y, the flow paths C5 adjacent in the second direction Y do not interfere with each other, and more flow paths per unit length in the second direction Y C5 can be placed.

Next, the operation of the cooling mechanism 37 configured as described above will be described.
For example, the flow of the refrigerant R1 in the region A3 in the flow passage C5, which is curved so as to protrude toward one side in the second direction Y (the lower left side in FIG. 12) will be described. In the cross section perpendicular to the axis of the flow path C5 in the region A3, as shown in FIG. 13, the centrifugal force acting on the refrigerant R1 and the temperature difference between the bottom wall 21 and the top wall 22 The secondary flow shown occurs. That is, the refrigerant R1 flows to one side in the second direction Y (left side in the drawing of FIG. 13) by the centrifugal force. The relatively high temperature refrigerant R1 disposed on the bottom wall 21 side has a low density and flows outward in the radial direction X, and the relatively low temperature refrigerant R1 disposed on the top wall 22 side has a low density Flow radially inward.
The flow velocity of the secondary flow of the refrigerant R1 is slower than the flow velocity of the refrigerant R1 in the first direction Z. Due to the secondary flow of the refrigerant R1, the refrigerant R1 flows not only in the direction along the second direction Y but also in the radial direction X in this cross section.

As described above, according to the cooling mechanism 37 of the present embodiment, it is possible to arrange more channels C5 per unit length in the second direction Y.
Furthermore, since the refrigerant R1 flows also in the radial direction X in the flow path C5 by the secondary flow of the refrigerant R1, the heat from the combustion chamber 13 transmitted through the bottom wall 21 is the refrigerant R1 in the flow path C5. Can be distributed to effectively transmit.

Fourth Embodiment
Next, a fourth embodiment of the present invention will be described with reference to FIG. 14 and FIG. In the present embodiment, the same parts as those of the above-described embodiment are denoted by the same reference numerals, and the description thereof is omitted. Only different points will be described.
As shown in FIGS. 14 and 15, in the cooling mechanism 42 of this embodiment, the width of the channel C7 is changed from the bottom wall 21 side to the top wall 22 instead of the partition member 26 of the cooling mechanism 12 of the first embodiment. The heat dissipating structure 43 has a shape that gradually widens toward the side.
In the present embodiment, the channel C7 has a triangular shape whose width narrows inward in the radial direction X when viewed in the first direction Z. The axis of the flow path C7 extends along the first direction Z. The channel C7 is formed between the side walls 44 adjacent in the second direction Y. The cross-sectional shape of the side wall 44 in a plane orthogonal to the first direction Z is an equal leg trapezoidal shape in which the lower base on the bottom wall 21 side is long. That is, the width of the side wall 44 gradually narrows from the bottom wall 21 side toward the top wall 22 side.
One side wall 44 is shared by a pair of flow paths C7 sandwiching the side wall 44 in the second direction Y.

Here, as shown in FIG. 15, the description will be given focusing on one flow path C7A among the plurality of flow paths C7. A pair of side walls 44 sandwiching the flow path C7A is bisected in the second direction Y by an imaginary line L11 extending along the radial direction X. Of the side wall 44 divided into two equal parts, the portion on the flow path C7A side is a first partial wall 44a, and the portion on the opposite side to the flow path C7A is a second partial wall 44b.
The width of the first partial wall 44 a gradually narrows from the bottom wall 21 side toward the top wall 22 side.

In general, the thermal conductivity of the side wall is larger than the thermal conductivity of the refrigerant. The width of the first partial wall 44 a is wider at the bottom wall 21 than at the top wall 22. For this reason, heat is easily conducted to a portion on the bottom wall 21 side of the first partial wall 44a. The heat from the combustion chamber 13 passes through the portion on the bottom wall 21 side of the first partial wall 44a, as indicated by the arrow F8, and not only on the portion on the bottom wall 21 side in the channel C7A, but also on the top in the channel C7A. The part to the wall 22 side is effectively distributed and transmitted.

In the refrigerant R1 in the flow path C7 adjacent to the flow path C7A in the second direction Y, the flow path C7A and the second partial wall 44b of the side wall 44 sandwiching the flow path C7A in the second direction Y Heat is also effectively transferred.

As described above, according to the cooling mechanism 42 of the present embodiment, it is possible to dispose more channels C7 per unit length in the second direction Y.
Furthermore, through the side wall 44 on the side of the wide bottom wall 21 having a large thermal conductivity, heat from the combustion chamber 13 is not only the portion on the bottom wall 21 side in the flow path C7 but also the top wall 22 in the flow path C7. It can also be distributed and transmitted to the side part. Therefore, the heat from the combustion chamber 13 can be effectively transferred to the refrigerant R1.

Although the first to fourth embodiments of the present invention have been described in detail with reference to the drawings, the specific configuration is not limited to this embodiment, and a configuration without departing from the scope of the present invention Changes, combinations, deletions etc. are also included. Furthermore, it goes without saying that each of the configurations shown in each embodiment can be used in combination as appropriate.
For example, in the first to fourth embodiments, the bottom wall and the top wall may be formed in a flat plate shape instead of a cylindrical shape.

The cooling mechanism of the present embodiment can be suitably used, for example, to cool the combustion gas flowing in the combustion chamber.

12, 32, 37, 42 Cooling mechanism (Cooling chamber cooling mechanism)
13 combustion chamber 21 bottom wall 22 top wall 23, 44 side wall 26 partition member (heat distribution structure)
33 Guide member (heat distribution structure)
38, 43 heat dispersion structure C1, C5, C7 flow path Y second direction Z first direction

Claims (5)

1. A bottom wall in contact with the combustion chamber,
   An upper wall disposed opposite to the combustion chamber with respect to the bottom wall;
   A plurality of side walls that are in contact with the bottom wall and the top wall, extend in a first direction along the bottom wall, and are arranged in a second direction perpendicular to the first direction;
   Equipped with
   A flow path having a substantially constant width is formed between the bottom wall and the top wall and between the side walls adjacent in the second direction,
   A heat dispersion structure is provided in the flow passage for dispersing and transferring the heat from the combustion chamber transmitted through the bottom wall to the refrigerant flowing in the flow passage.
   Combustion chamber cooling mechanism.
2. The heat dispersion structure includes a partition member formed in a spiral wing shape, which extends in the axial direction of the flow channel in the flow channel, and which revolves around the axial line.
   The cooling mechanism of the combustion chamber according to claim 1.
3. The heat dispersion structure includes a guide member which is disposed in the flow passage and has a shape gradually approaching the bottom wall from one side to the other side in the axial direction of the flow passage.
   The cooling mechanism of the combustion chamber according to claim 1.
4. The heat distribution structure has a shape in which the flow path extends in the first direction while meandering in the second direction.
   The cooling mechanism of the combustion chamber according to claim 1.
5. The heat dissipating structure has a shape in which the width of the flow path gradually increases from the bottom wall side toward the upper wall side.
   The cooling mechanism of the combustion chamber according to claim 1.

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