JP2009222250A - Radiator and cooling system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a radiator of high radiation efficiency and a cooling system comprising the same. <P>SOLUTION: A high temperature side condenser 310 as the "radiator" comprises a tube 311, a plurality of strip fins 312 arranged with prescribed clearances through which the air for cooling the tube 311 passes, and a cover section 313 for closing the clearances from a first side (arrow DR1 side) to the longitudinal direction (arrow DR0 direction) of the fins 312. The cover section 313 constitutes a "rectifying section" for making the fluid flow toward the first side (arrow DR1 side) from the second side (arrow DR2 side) opposed to the first side (arrow DR1 side) of the fin, direct to the direction from the first side (arrow DR1 side) to the second side (arrow DR2 side). <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a radiator and a cooling system, and more particularly to a radiator that promotes heat dissipation by flowing a fluid through a gap defined between a plurality of fins and a cooling system including the radiator.

  In a heat exchanger that is a mechanism for discharging heat of a refrigerant flowing in a pipe by heat exchange with an external fluid, it is effective to enlarge the heat transfer surface in order to increase the amount of heat transfer. 2. Description of the Related Art Conventionally, a heat exchanger in which fins are attached to piping is known as a heat exchanger having an enlarged heat transfer surface.

  In heat exchangers composed of finned pipes, forced cooling is generally performed by forcibly sending air with a heat radiating fan when the external fluid is a gas. FIG. 7 is a diagram showing an example of a conventional radiator. The heat exchanger shown in FIG. 7 is a cross fin type heat exchanger. Here, a large number of fins 312A are installed around a tube 311A that is a pipe-shaped flow path. In this heat exchanger, heat exchange is mainly performed between the liquid flowing in the tube 311A and the surrounding gas (arrow DR350). The reason why the fins 312A are installed on the outer surface of the tube 311A is to increase the heat transfer area for the gas and increase the efficiency. Further, the heat transfer capability from the solid surface to the gas varies depending on the gas flow state. In the example of FIG. 7, forced cooling by the fan 316 </ b> A is employed to increase the heat transfer capability. The type of heat exchanger shown in FIG. 7 is found in air conditioners, automobile radiators, and the like, and is classified as a cross flow type heat exchanger in terms of heat transfer.

  In order to install the fan 316A as shown in FIG. 7, it is necessary to secure a space for providing the fan 316A and a space through which the wind passes to form a duct, which hinders downsizing of the cooling system. In addition, there is a problem that the power consumption increases by providing the fan 316A. Further, there is a problem in that dust is clogged between the fins 312A due to the air volume by the fan 316A and the heat dissipation performance is deteriorated.

  By the way, since the upward flow by the convection has arisen in the heat exchanger vicinity higher temperature than external air, heat exchange can be performed using this upward flow. For example, in the heat exchanger shown in FIG. 8, heat dissipation performance is improved by arranging a heat exchanger including tubes 311A and fins 312A in a cylindrical duct 317A that rectifies and promotes the upward flow. ing. An example of a natural convection heat dissipation system using this so-called chimney effect is described in Japanese Patent Application Laid-Open No. 2004-37043 (Patent Document 1).

In Patent Document 1, a compressor in which heat dissipating fins are provided in a vertical direction is disposed in a wind tunnel chamber. The heat of the compressor generated during operation is discharged from the ventilation port by natural convection generated from the chimney effect in the wind tunnel chamber from the air inlet to the air outlet.
JP 2004-37043 A

  However, the conventional natural convection heat dissipation system using the chimney effect as described above still does not necessarily have sufficient heat dissipation performance.

  This invention is made | formed in view of the above problems, and the objective of this invention is providing a heat radiator with high heat dissipation efficiency and a cooling system provided with the same.

  The radiator according to the present invention includes a plurality of strip-shaped fins arranged while defining a predetermined gap through which the fluid that cools the radiator and the radiator passes, and a first side with respect to the longitudinal direction of the fins. A cover portion that closes the gap, and the cover portion directs the flow of fluid from the second side facing the first side of the fin toward the first side from the first side to the second side. Includes a rectifying section that is oriented in the direction.

  According to the above configuration, by providing the cover portion that closes the gap between the fins, a transverse component that intersects the longitudinal direction of the fin can be added to the flow of fluid that passes through the gap. Heat exchange between the fin and the fluid is promoted, and the heat dissipation performance of the heat exchanger is improved.

  In one aspect, in the radiator, the rectifying unit is provided between the cover member that closes the gap and the fin and the cover member, and extends in an oblique direction intersecting the longitudinal direction and the width direction of the fin. And a rectifying plate.

  In another aspect, in the radiator, the rectifying unit includes a member having a substantially arc-shaped cross section along the longitudinal direction of the fin.

  According to the said structure, in any situation, the flow component of a horizontal direction can be produced | generated efficiently and the performance of a radiator can be improved.

  Preferably, in the radiator, the fluid passes through the gap by natural convection. According to the above configuration, a fan for forming a flow of fluid flowing between the fins is unnecessary, so that power consumption can be reduced and reduction in heat dissipation efficiency due to dust clogging between the fins is suppressed. can do.

  Preferably, in the radiator, the radiator includes a tubular member through which a refrigerant flows. According to the above configuration, the heat dissipation efficiency can be further improved by the refrigerant flowing in the tubular member.

  The cooling system according to the present invention includes a Stirling engine having a high temperature part and the above-described radiator, and heat of the high temperature part of the Stirling engine is transmitted to the radiator.

  According to the said structure, it becomes possible to cool the high temperature part of a Stirling engine efficiently.

  ADVANTAGE OF THE INVENTION According to this invention, a heat radiator with high heat dissipation efficiency and a cooling system provided with the same can be provided.

  Embodiments of the present invention will be described below. Note that the same or corresponding parts are denoted by the same reference numerals, and the description thereof may not be repeated.

  Note that in the embodiments described below, when referring to the number, amount, and the like, the scope of the present invention is not necessarily limited to the number, amount, and the like unless otherwise specified. In the following embodiments, each component is not necessarily essential for the present invention unless otherwise specified. In addition, when there are a plurality of embodiments below, it is planned from the beginning to appropriately combine the configurations of the embodiments unless otherwise specified.

  FIG. 1 is a diagram showing a configuration of a Stirling cooler including a radiator according to an embodiment of the present invention. FIG. 2 is a diagram showing a state in which the Stirling refrigerator shown in FIG. 1 is viewed from the direction of arrow II. 1 and 2, a Stirling refrigerator 1 is a low-temperature side circulation which is a Stirling refrigerator 100 (Stirling engine) having a low-temperature part and a high-temperature part and a refrigerant circuit for transmitting the cold heat of the low-temperature part. The circuit 200, the high temperature side circulation circuit 300 which is a refrigerant circuit for transmitting the heat | fever of the said high temperature part, and the cabinet 400 are included.

  The low temperature side circulation circuit 200 includes a low temperature side evaporator 210, refrigerant pipes 220 and 230, and a low temperature side condenser 240 attached to a low temperature part of the Stirling refrigerator 100. The low temperature side circulation circuit 200 performs heat exchange between the air in the cabinet 400 and the low temperature part of the Stirling refrigerator 100.

  In the low temperature side circulation circuit 200, carbon dioxide, hydrocarbons and the like are sealed as a refrigerant. The refrigerant condensed in the low temperature side condenser 240 flows through the refrigerant pipe 220 (low temperature side conduit) and reaches the low temperature side evaporator 210. Heat exchange is performed by evaporating the refrigerant in the low temperature side evaporator 210. After the heat exchange, the gasified refrigerant returns to the low temperature side condenser 240 via the refrigerant pipe 230 (low temperature side return pipe). The refrigerant that has flowed into the low-temperature side condenser 240 and condensed flows into the refrigerant pipe 220.

  In the low-temperature side circulation circuit 200, the low-temperature side evaporator 200 can transmit cold heat generated in the low-temperature part of the Stirling refrigerator 100 using the natural circulation caused by the evaporation and condensation of the refrigerant. 210 is disposed below the low-temperature side condenser 240. Further, the pressure in the circulation circuit system is adjusted in order to adjust the boiling point of the refrigerant.

  The high temperature side circulation circuit 300 includes a high temperature side condenser 310, refrigerant pipes 320 and 330, and a high temperature side evaporator 340. The high temperature side circulation circuit 300 cools the high temperature part of the Stirling refrigerator 100.

Water (H ₂ O) or the like is sealed in the high temperature side circulation circuit 300 as a refrigerant. The refrigerant evaporated in the high temperature side evaporator 340 flows through the refrigerant pipe 320 (high temperature side conduit) and reaches the high temperature side condenser 310. The refrigerant is condensed by heat exchange with the outside air in the high temperature side condenser 310. The condensed refrigerant flows through the refrigerant pipe 330 (high temperature side return pipe) and returns to the high temperature side evaporator 340. In the high temperature side circulation circuit 300, the high temperature side condenser can be used to transfer the heat generated in the high temperature portion of the Stirling refrigerator 100 using the natural circulation caused by the evaporation and condensation of the refrigerant. 310 is disposed above the high-temperature side evaporator 340. Further, the pressure in the circulation circuit system is adjusted in order to adjust the boiling point of the refrigerant.

  When the Stirling refrigerator 100 is operated, the heat generated in the high temperature part of the refrigerator 100 is heat-exchanged with air via the high temperature side condenser 310. On the other hand, the cold generated in the low temperature part of the Stirling refrigerator 100 is exchanged with the air in the cabinet 400 via the low temperature side evaporator 210. The warmed airflow from the inside of the refrigerator is sent again to the vicinity of the low temperature side evaporator 210 and repeatedly cooled.

  The high temperature side condenser 310 is hotter than its surroundings. Around the high temperature side condenser 310, an upward flow resulting from this temperature difference is generated. This upward flow promotes heat exchange between the high temperature side condenser 310 and the air. Thus, the high temperature side condenser 310 in the present embodiment is a natural convection type heat exchanger that performs heat dissipation using natural convection generated due to a temperature difference from the surroundings.

Next, the structure of the high temperature side condenser 310 is demonstrated using FIG. Referring to FIG. 3, the high temperature side condenser 310 is a finned tube heat exchanger in which fins are attached to tubes, and includes header pipes 3200 and 3300 connected to conduit refrigerant pipes 320 and 330, and a header. It includes a tube 311 as a refrigerant pipe group that branches from the pipes 3200 and 3300 and runs in parallel and connects the two, and a plurality of fins 312 attached to the tube 311. The fin 312 is a strip-like fin extending in the vertical direction (arrow DR0 direction). Inside the header pipes 3200 and 3300 and the tube 311, a fluid (H ₂ O) that conducts heat from a high temperature portion (not shown in FIG. 3) of the Stirling refrigerator 100 that is a heat source is enclosed. The heat transmitted from the heat source through this refrigerant is transmitted to the fins 312 and is exhausted by heat exchange between the fins 312 and the air. A cover portion 313 is provided on one side surface (side surface on the arrow DR1 side) of the high temperature side condenser 310 that is a finned tube heat exchanger so as to close the heat radiation surface while defining a predetermined space. The cover part 313 is a trapezoidal cover member and includes inclined surfaces 3131 and 3132 and a bottom surface 3133.

  Around the high temperature side condenser 310 shown in FIG. 3, no forced cooling means such as a fan for promoting the air flow is provided. However, the inventor of the present application has confirmed that by installing the cover portion 313, heat dissipation performance exceeding the conventional chimney effect (FIG. 8) can be obtained. This is because, in the case of a fin-tube heat exchanger that is long in the vertical direction, the temperature difference between the air flow rising due to natural convection and the refrigerant becomes small at the top of the heat exchanger, so a duct is temporarily installed and the air flow is caused by the chimney effect. However, by providing the cover portion 313 as described above, one side surface (side surface in the direction of the arrow DR2) of the upright heat exchanger (high temperature side condenser 310) is provided. ) Is sucked in low-temperature air, and an arc-shaped flow (arrow DR131) is induced at the inner edge of the cover portion 313, and the high-temperature air can be discharged again on the same side, so that the horizontal direction (arrow DR1 direction and arrow DR2 This is probably because the flow component in the direction is excited and the air suction surface becomes large.

  In the example of FIG. 3, the cooling airflow flows into the high-temperature side condenser 310 along a direction obliquely intersecting with the longitudinal direction of the fins 312 (in the direction of the arrow DR <b> 0), and along the cover portion 313. After turning, it flows out of the high temperature side condenser 310 along a direction that intersects with the longitudinal direction of the fin 312 (arrow DR0 direction) in an oblique direction. In this way, the cooling airflow crosses the fin 312 diagonally. When the present inventor performs heat radiation using a heat exchanger (that is, a heat exchanger in which the cover portion 313 in FIG. 3 is omitted) including the header pipes 3200 and 3300, the tubes 311 and the fins 312 in FIG. It has been confirmed that the heat radiation efficiency can be improved by extending the fins 312 obliquely with respect to the air flow direction. In the structure of FIG. 3, similarly, since the fins 312 can be extended obliquely with respect to the direction of the arcuate air flow (the direction of the arrow DR313), high heat dissipation efficiency can be obtained.

  FIG. 4 is a view showing a modification of the high temperature side condenser 310. A feature of the modification shown in FIG. 4 is that a cover member 3141 having a rectifying plate 3142 disposed therein is installed as the cover portion 314. That is, the cover portion 314 is provided between the cover member 3141 that closes the gap between the fins 312 and between the fin 312 and the cover member 3141, and the longitudinal direction (arrow DR0 direction) and the width direction (arrow DR1 direction) of the fin 312. And a current plate 3142 extending in an oblique direction intersecting with the arrow DR2 direction. In the modification shown in FIG. 4, since the internal air flow (arrow DR 314) is adjusted as compared with the trapezoidal cover portion 313, the outer shape is substantially a rectangular parallelepiped shape, but is equivalent to the case of the trapezoidal cover (FIG. 3). Indicates heat dissipation performance.

  FIG. 5 is a view showing another modification of the high temperature side condenser 310. The feature of the modified example shown in FIG. 5 is that the cover portion 315 is an arc-shaped cover member having a columnar shape having an arc-shaped concave surface formed in a deep concave shape toward the center with respect to the side surface of the high-temperature side condenser 310. Is the point where is placed. That is, cover portion 315 includes a member whose cross section along the longitudinal direction (arrow DR0 direction) of fin 312 has a substantially arc shape. In the modification shown in FIG. 5, since the air flow (arrow DR315) inside the cover is stabilized, the heat dissipation performance is higher than that of the above-described radiator (FIGS. 3 and 4).

  Next, the performance of the radiator shown in FIGS. 3 to 5 will be described using Table 1.

Table 1 shows the result of measuring the average temperature of the surface of the radiator after stabilization by applying a predetermined power (200 W) to the heater for heating the refrigerant inside the radiator. In Table 1, “free” indicates that the heat exchange cover portion 313 shown in FIG. 3 is omitted, and “chimney effect” is provided with a cylindrical member that provides a chimney effect instead of the cover portion 313 shown in FIG. In this case, “trapezoidal cover” means the example shown in FIG. 3, “rectifier plate cover” means the example shown in FIG. 4, and “arc-shaped cover” means the example shown in FIG. In Table 1, “temperature difference [K]” means the average temperature of the radiator surface−environment temperature (30 ° C.), and “air side heat resistance value [K / W]” is the heat dissipation performance. It is used as an index, and means a value obtained by subtracting the contact heat resistance value between the heater and the evaporator and the evaporation heat resistance value of the refrigerant from the total heat resistance value. The size of the radiator was 60 cm in length, 60 cm in width, 2 cm in depth, and the heat transfer area was about 2 m ² .

  In Table 1, the higher the heat dissipation efficiency, the smaller the “temperature difference” and “thermal resistance value”. As shown in Table 1, rather than natural convection heat dissipation using the “chimney effect”, the natural convection radiator (FIGS. 3, 4, and 5) according to the present embodiment in which the cover portions 313, 314, and 315 are arranged is used. Heat dissipation has higher heat dissipation efficiency.

  Next, an example of the structure of the Stirling refrigerator 100 and its operation will be described with reference to FIG.

  As shown in FIG. 6, the Stirling refrigerator 100 of the present embodiment is a free piston type Stirling engine, and includes a casing 110 as an “outer shell” including a high temperature portion 111 and a low temperature portion 112, and the casing 110, a piston 130 and a displacer 140 that reciprocate in the cylinder 120, a displacer rod 140A, a working space 150 including a compression space 151 and an expansion space 152, a regenerator 160, and a back. The pressure space 170, a linear motor 180 as a piston driving means, and a spring 190 including a piston spring 191 and a displacer spring 192 are configured.

  The casing 110 defines a back pressure space 170. Various parts including a cylinder 120, a linear motor 180, a piston spring 191 and a displacer spring 192 are assembled to the casing 110. The casing 110 is filled with a working medium such as helium gas, hydrogen gas, or nitrogen gas.

  The cylinder 120 has a substantially cylindrical shape, and receives a piston 130 and a displacer 140 as a free piston in a reciprocating manner. In the cylinder 120, the piston 130 and the displacer 140 are arranged coaxially with a space therebetween, and the piston 130 and the displacer 140 divide the working space 150 into a compression space 151 and an expansion space 152. More specifically, the working space 150 is a space located closer to the displacer 140 than the end face of the piston 130 on the displacer 140 side. A compression space 151 is formed between the piston 130 and the displacer 140, and the displacer 140 and the low temperature portion An expansion space 152 is formed between the two and 112. The compression space 151 is mainly surrounded by the high temperature part 111, and the expansion space 152 is mainly surrounded by the low temperature part 112.

  Between the compression space 151 and the expansion space 152, a regenerator 160 in which a film is wound with a predetermined gap is disposed, and the compression space 151 and the expansion space are interposed via the regenerator 160. 152 communicates. Thereby, a closed circuit is configured in the Stirling refrigerator 100. The working medium sealed in the closed circuit flows in accordance with the operations of the piston 130 and the displacer 140, whereby a reverse Stirling cycle is realized.

  A back pressure space 170 surrounded by the casing 110 is disposed on the opposite side of the piston 130 from the displacer 140. There is also a working medium in the back pressure space 170.

  A linear motor 180 is disposed in a portion of the back pressure space 170 located outside the cylinder 120. The linear motor 180 includes an inner yoke 181, an outer yoke 182, a coil 183, and a movable magnet 184. The linear motor 180 drives the piston 130 in the axial direction of the cylinder 120 (arrow DR0 direction).

  One end of the piston 130 is connected to a piston spring 191 composed of a leaf spring or the like. The piston spring 191 functions as “elastic force applying means” for applying an elastic force to the piston 130. By applying an elastic force by the piston spring 191, the piston 130 can be reciprocated in the cylinder 120 more stably and periodically. One end of the displacer 140 is connected to a displacer spring 192 via a displacer rod 140A. The displacer rod 140A is disposed through the piston 130, and the displacer spring 192 is configured by a leaf spring or the like.

Next, the operation of the Stirling refrigerator 100 will be described.
This refrigerator obtains a refrigeration effect using a so-called reverse Stirling cycle. The piston 130 is driven by a linear motor 180 to move sinusoidally. Due to the movement of the piston 130, the working medium in the compression space 151 exhibits a sinusoidal pressure change. The compressed working medium releases compression heat at the high temperature portion 111, is precooled when passing through the regenerator 160 provided outside the cylinder 120, and flows into the expansion space 152.

  The displacer 140 sine-moves with a constant phase difference in the same period as the piston 130 during steady operation, and the phase difference and amplitude are the spring constant of the displacer spring 192, the compression space 151 and the expansion space 152 that change from moment to moment. It is determined by the pressure difference, the mass of the displacer 140, the operating frequency, and the like. About this phase difference, it is generally said that the optimum condition is about 90 degrees.

  The working medium that has flowed into the expansion space 152 expands due to the sinusoidal movement of the displacer 140, whereby the temperature in the expansion space 152 is significantly reduced. By transmitting the extremely low temperature (for example, about −50 ° C.) generated at this time into the refrigerator through the low temperature portion 112, a desired cooling effect can be obtained.

  According to the present embodiment, as described above, by providing the cover portions 313 (FIG. 3), 314 (FIG. 4), and 315 (FIG. 5) that close the gap between the fins 312, the gap passes through the gap. Since a component in the transverse direction that intersects the longitudinal direction of the fin 312 (arrow DR0 direction) can be added to the air flow, heat exchange between the fin 312 and the air is promoted, and the heat dissipation performance of the heat exchanger is improved. Can be improved.

  Further, since air is caused to flow by natural convection due to the temperature difference between the high-temperature side condenser 310 and its surroundings, a fan for forming a flow of air flowing between the fins 312 becomes unnecessary, so that power consumption can be reduced. In addition to being able to reduce, it is possible to suppress a decrease in heat radiation efficiency due to dust clogging between the fins 312.

  Moreover, the high temperature part 111 of the Stirling refrigerator 100 can be efficiently cooled by flowing the refrigerant into the tube 311 as the “tubular member” to dissipate heat.

  The above contents are summarized as follows. That is, the high temperature side condenser 310 as the “heat radiator” according to the present embodiment defines a predetermined gap through which the tube 311 as the “heat radiator” and the air as the “fluid” that cools the tube 311 pass. And a plurality of strip-shaped fins 312 and cover portions 313, 314, and 315 that close the gap from the first side (arrow DR1 side) with respect to the longitudinal direction (arrow DR0 direction) of the fin 312. . The cover portions 313, 314, and 315 are configured to cause a fluid flow from the second side (arrow DR2 side) facing the first side (arrow DR1 side) of the fin to the first side (arrow DR1 side). A “rectifying unit” is configured to face in a direction from the first side (arrow DR1 side) to the second side (arrow DR2 side).

  In the present embodiment, the high temperature part 111 and the low temperature part 112 in the Stirling refrigerator 100 are arranged in the vertical direction (arrow DR0 direction) (more specifically, the high temperature part 111 of the Stirling refrigerator 100 is connected to the Stirling refrigerator). The Stirling refrigerator 100 is installed (so that it is located above the low temperature portion 112 of the machine 100), but the Stirling refrigerator 100 so that the high temperature portion 111 and the low temperature portion 112 in the Stirling refrigerator 100 are aligned in the horizontal direction. May be installed.

  In the specification of the present application, the “refrigerator” is a concept including all of the “refrigerator” having a refrigerator compartment, the “freezer” having a freezer compartment, and the “refrigerator refrigerator” having both the freezer compartment and the refrigerator compartment.

  In the present embodiment, the Stirling refrigerator / freezer (Stirling Refrigerator / Freezer) as a Stirling engine-equipped device including the Stirling refrigerator 100 has been described. However, the radiator according to the present invention is applied only to the Stirling refrigerator 1. Is not to be done. The Stirling engine-equipped device may be, for example, one that uses the Stirling engine as a generator.

  Although the embodiments of the present invention have been described above, the embodiments disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is defined by the terms of the claims, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

It is a figure which shows the structure of the Stirling cooler containing the heat radiator which concerns on one embodiment of this invention. It is a figure which shows the state which looked at the Stirling refrigerator shown by FIG. 1 from the direction of arrow II. It is a disassembled perspective view which shows the heat radiator which concerns on one embodiment of this invention. It is a figure which shows typically the modification of the heat radiator which concerns on one embodiment of this invention. It is a figure which shows typically the other modification of the heat radiator which concerns on one embodiment of this invention. It is sectional drawing which showed the Stirling refrigerator in the Stirling refrigerator shown by FIG. 1, FIG. It is the figure which showed an example of the conventional heat radiator. It is the figure which showed the other example of the conventional heat radiator.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 Stirling refrigerator, 100 Stirling refrigerator, 110 casing, 111 high temperature part, 112 low temperature part, 120 cylinder, 130 piston, 140 displacer, 140A displacer rod, 150 working space, 151 compression space, 152 expansion space, 160 regenerator, 170 Back pressure space, 180 Linear motor, 181 Inner yoke, 182 Outer yoke, 183 Coil, 184 Movable magnet, 190 Spring, 191 Piston spring, 192 Displacer spring, 200 Low temperature side circulation circuit, 210 Low temperature side evaporator, 220, 230 Refrigerant piping, 240 Low temperature side condenser, 300 High temperature side circulation circuit, 310 High temperature side condenser, 311, 311A tube, 312, 312A Fin, 313, 314 15 cover portion, 316A fan, 317A duct, 320,330 refrigerant pipe, 340 high-temperature side evaporator, 400 cabinets, 3131,3132 inclined surface 3133 bottom 3141 covering member, 3142 current plate.

Claims (6)

A radiator,
A plurality of strip-shaped fins arranged while defining a predetermined gap through which a fluid for cooling the heat radiator passes,
A cover portion that closes the gap from the first side with respect to the longitudinal direction of the fin,
The cover portion directs the flow of the fluid from the second side facing the first side of the fin toward the first side in a direction from the first side toward the second side. A radiator including a rectifier. The rectifying unit includes a cover member that closes the gap,
2. The radiator according to claim 1, further comprising a current plate provided between the fin and the cover member and extending in an oblique direction intersecting with a longitudinal direction and a width direction of the fin.   The radiator according to claim 1 or 2, wherein the rectifying unit includes a member having a substantially arc-shaped cross section along the longitudinal direction of the fin.   The radiator according to any one of claims 1 to 3, wherein the fluid passes through the gap by natural convection.   The radiator according to any one of claims 1 to 4, wherein the radiator includes a tubular member through which a refrigerant flows. A Stirling engine having a high temperature section;
A radiator according to any one of claims 1 to 5,
The cooling system in which the heat of the high temperature part of the Stirling engine is transmitted to the radiator.

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