JP6213050B2 - Cooling device for temperature difference power generation - Google Patents

Description

  The present application relates to a cooling device for temperature difference power generation using thermal energy.

  Conventionally, when air-cooling a heating element or the like using cooling air, heat radiation from the heating element is increased by bringing an air-cooling fin made of metal into contact with the heating element and hitting the cooling air against the air-cooling fin. A method of suppressing fever is taken. Various shapes are known for the structure of the air-cooling fin. For example, a shape in which a large number of thin metal plates are projected vertically on a plate-like base metal is common. As the metal used for the air-cooled fin, a metal having high thermal conductivity is used, and copper, aluminum, an alloy thereof, or the like is used. Alloys based on aluminum are most commonly used because of their light weight and low cost.

  In normal air-cooling fins, it is assumed that the flow of cooling air (airflow) directed in a specific direction is used. For example, in the case of forced air cooling, a large number of airflows generated by the operation of the fan are likely to flow. The metal plate is arranged substantially parallel to the airflow. In the case of air cooling using natural convection, air cooling fins are arranged in consideration of the direction of convection in consideration of gravity. However, for example, when the direction of airflow changes with time, or the entire device including the element of the heat source may move or rotate, the direction of airflow as viewed from the device is not necessarily constant. There is a case.

  For such a problem, for example, Patent Document 1 and Patent Document 2 provide a mechanism for rotating the entire air-cooled fin. The heat sink mounting structure disclosed in Patent Document 1 promotes natural convection by rotating the fin mounting plate so that the direction of the heat dissipating fins is vertical regardless of whether the electronic device is placed flat or vertically. . Further, in the heat sink disclosed in Patent Document 2, even if a part of the cooling fan unit breaks down and the flow direction of the airflow changes, the plate portion on which the fins are projected is rotated by a rolling bearing to turn the fins into an airflow. Parallel to improve cooling efficiency.

Japanese Patent Laid-Open No. 10-13068

JP 2011-77247 A

  However, the mechanisms disclosed in Patent Documents 1 and 2 are mechanisms that rotate the entire air-cooled fin, and in such a mechanism, a mechanical mechanism, that is, a rotating mechanism and good thermal conductivity, is provided between the heating element and the air-cooled fin. It is necessary to have a property that is difficult to do. Therefore, in Patent Document 2, a complicated structure using a roller bearing is provided. In addition, when installing air-cooled fins for heat generating elements that require heat dissipation, if such a complicated rotation mechanism is built in, if any malfunction occurs, the element may fail without sufficient heat dissipation. There is. Furthermore, in the examples disclosed in Patent Documents 1 and 2, since the fins are fixed to the metal base, the intervals and the number of fins cannot be changed according to the convection state (natural / forced), which is efficient. I could not radiate heat.

  By the way, in recent years, energy harvesting that collects energy such as sunlight, illumination light, vibration generated by machines, heat, and the like to obtain electric power is known. One type of energy harvesting is temperature difference power generation in which heat energy generated by a motor is used, a thermoelectric element is attached to the motor, and a temperature difference is generated by a cooling device. Fins are also used in the cooling device for temperature difference power generation, and cooling is performed using cooling air flowing in a direction parallel to the rotation axis of the motor while the motor is operating, but the motor stops and cools. When the wind disappears, the fins cannot radiate heat sufficiently. That is, when the cooling air stops, cooling is performed by natural convection, but the direction of the fins obstructs the flow of natural convection, so that the fins cannot sufficiently dissipate heat.

  Therefore, also in the field of temperature difference power generation using thermal energy, the cooling device does not have a complicated rotating mechanism, and the direction of airflow changes with time, or the direction of airflow seen from the device is There is a demand for a cooling device that can cope with changing cases.

  In one aspect, the present application provides a cooling device that efficiently attaches a temperature difference using cooling air in temperature difference power generation in which a thermoelectric element is attached to a heat source that is air-cooled during operation, and power is generated by the temperature difference between the heat source and the cooling air. The purpose is to provide.

  According to one aspect of the embodiment, there is provided a cooling device for temperature difference power generation that generates power by giving a temperature difference to a thermoelectric element attached to a heat source, and a base plate that is attached to the thermoelectric element, and protrudes from the base plate. There is provided a cooling device for temperature difference power generation comprising at least one rotating shaft and a fin attached to the rotating shaft and rotatable about the rotating shaft. In this case, the heat source is provided with an air cooling device that flows cooling air in a direction transverse to the heat source during heat generation, the base plate is fixed to the thermoelectric element in parallel to the cooling air, and the fins are When the heat source generates heat, it rotates and becomes parallel to the cooling air, and when the heat source stops generating heat, it turns in the vertical direction due to its own weight.

(A) is a side view of a motor in which the cooling device of the present application is attached to a thermoelectric element for temperature difference power generation attached to an industrial motor that generates thermal energy, and (b) is a partially enlarged view of the cooling device. 2 is a front view of the motor shown in FIG. 2 and a partially enlarged view of a thermoelectric element for temperature difference power generation to which the cooling device of the present application is attached. It is a circuit diagram of one Example of the form which takes out and uses the electric power generated with the thermoelectric element shown in FIG.1 (b). (A) is an assembly perspective view which shows the structure of 1st Example of the cooling device of this application, (b) is operation | movement explanatory drawing explaining operation | movement of the fin shown to (a). (A) is the partial expanded side view which shows operation | movement of the cooling device of 1st Example when the motor shown to Fig.1 (a) is operating, (b) is the cooling device shown to (a). An arrow view seen from the direction of arrow A, (c) is a partially enlarged side view showing the operation of the cooling device of the first embodiment when the motor shown in FIG. 1 (a) is stopped, (d). FIG. 4 is an arrow view of the cooling device shown in FIG. (A) is a perspective view which shows the shape of the fin attached to the cooling device of 2nd Example of this application, (b) is the perspective view which shows another shape of the fin attached to the cooling device of 2nd Example of this application. FIGS. 1C and 1C are partially enlarged side views showing the operation of the fins of the cooling device of the second embodiment when the motor shown in FIG. 1A is operating, and FIG. It is a partial expanded side view which shows operation | movement of the fin of the cooling device of 2nd Example when the motor shown in (2) has stopped. (A) is a side view of the cooling device of the third embodiment of the present application, (b) is a perspective view showing the shape of fins attached to the cooling device shown in (a), and (c) is shown in (b). FIG. 4D is a partially enlarged side view showing the operation of the fin of the cooling device of the third embodiment when the motor shown in FIG. 1A is operating. FIG. 5E is a partially enlarged side view showing the operation of the fins of the cooling device of the third embodiment when the motor shown in FIG. (A) is a perspective view which shows the 1st modification of the shape of the fin attached to the cooling device of 3rd Example of this application, (b) of the fin attached to the cooling device of 3rd Example of this application The perspective view which shows the 2nd modification of a shape, (c) is a perspective view which shows the 3rd modification of the shape of the fin attached to the cooling device of the 3rd Example of this application. (A) is an assembly perspective view which shows the structure of the fin attached to the cooling device of 4th Example of this application, (b) is a perspective view which shows the state which assembled the fin shown to (a), (c) is (B) is a partial enlarged view of the cooling device when the fin shown in (b) is attached to the rotating shaft and viewed from the direction of arrow D, (d) is a view showing a modification of the fin shown in (c), (e) (D) is a partially enlarged view of the cooling device showing an initial state when the motor is operated when the fin is attached to the cooling device, and (f) is a deformation of the fin shown in (e) by the cooling air during operation of the motor. It is the elements on larger scale which show operation | movement. (A) is a perspective view which shows the structure of the modification of the fin attached to the cooling device of 4th Example of this application, (b) attaches the fin shown to (a) to a rotating shaft, and sees from the arrow E direction. (C) is a partially enlarged view of the cooling device showing an initial state when the fin motor shown in (b) is operated, and (c) is a fin shown in (b) of the motor. It is the elements on larger scale which show the operation | movement which deform | transforms with the cooling air at the time of operation. (A) is a perspective view which shows the shape of the fin attached to the cooling device of 5th Example of this application, (b) is the perspective view which shows another shape of the fin attached to the cooling device of 2nd Example of this application. (C) is the elements on larger scale which show the state which attached the fin shown to (a) to the cooling device, (c) is a side view of the fin shown in (b), (d) is Drawing 1 (a) The partial expanded side view which shows the operation | movement of the fin of the cooling device of 5th Example when the motor shown to (4) is operating, (e) is when the motor shown to Fig.1 (a) has stopped. It is a partial expanded side view which shows operation | movement of the fin of the cooling device of 5th Example.

  Hereinafter, embodiments of the present application will be described in detail based on specific examples with reference to the accompanying drawings. In the embodiment described below, an industrial motor that generates cooling air during operation will be described as a thermal energy generator in temperature difference power generation. However, a thermal energy generator to which the cooling device of the present application is applied is an industrial motor. It is not limited to motors for use. Examples of the heat energy generating device with other cooling air to which the cooling device of the present application can be applied include an engine, piping of a building or factory with cooling air, and the like.

  FIG. 1A shows an industrial motor 50 that generates thermal energy as viewed from the side, and FIG. 1B shows the industrial motor 50 as viewed from the front. The housing 51 of the industrial motor 50 fixed on the base base 55 by the leg portion 56 is provided with a rotating shaft 52 through which power is taken out, on the opposite side of the rotating shaft 52 from the power extracting side. Is provided with a cooling fan 53 for generating cooling air for cooling the industrial motor 50. The cooling air CW generated by the cooling fan 53 flows inside or on the side of the housing 51. The housing 51 of the industrial motor 50 is provided with a plurality of radiating fins 54 in order to increase the cooling efficiency by the cooling air CW.

  And the temperature difference power generation apparatus 10 using the temperature difference between the heat generated by the industrial motor 50 and the cooling air is attached to a part of the housing 51 of the industrial motor 50. The temperature difference power generation device 10 includes a thermoelectric conversion unit 1, a sensor unit 2, a sensing / radio unit 3, and a wiring 4 that connects them, which are installed on a side surface of a casing 51. The thermoelectric conversion part 1 is provided with the heat collecting plate 5, the thermoelectric element 6, the base plate 7, the rotating shaft 8, and the fin 9, as shown to the enlarged part of Fig.1 (a), (b). The heat collecting plate 5 efficiently transfers the heat of the casing 51 to the thermoelectric element 6. The base plate 7 is in a position facing the heat collecting plate 5 and is attached to the thermoelectric element 6. The base plate 7, the rotary shaft 8 and the fins 9 constitute the cooling device 20 of the thermoelectric conversion unit 1, and the rotary shaft 8 protrudes from the open space side of the base plate 7 along the vertical and horizontal intervals to rotate. A fin 9 is attached to the shaft 8 so as to be swingable.

  FIG. 2 is a circuit diagram showing an internal configuration of the sensing / radio unit 3 which is an embodiment of the mode of taking out and using the electric power generated by the thermoelectric element 6 of the thermoelectric conversion unit 1 shown in FIG. is there. The sensing / wireless unit 3 includes a booster circuit 31, a storage battery 32, an MPU 33, a wireless circuit 34, and an antenna 35. Reference numeral 36 is a power supply line, and 37 is a signal line. The electric power input from the thermoelectric element 6 shown in FIG. 1B is boosted to 3.3 V through the booster circuit 31. Since the power generation by the thermoelectric element 6 is not always constant, the storage battery 32 is provided in the power supply line 36, and the power supply line 36 is always kept at a stable voltage (3.3V). Depending on the type of the storage battery 32, a dedicated circuit may be required, but here, the storage battery 32 is also described.

  Based on the obtained electric power, the MPU 33 is operated, and the sensor unit 2 is intermittently operated by the MPU 33 to measure the temperature and acceleration of the industrial motor 50. The measured data enters the wireless circuit 34 from the MPU 33 through the communication line 37 and is wirelessly transmitted through the antenna 35 provided in the wireless circuit 34. Examples of wireless include Zigbee (registered trademark) and Bluetooth (registered trademark) LE. The wirelessly transmitted data is notified to the measurer via a nearby receiver. By obtaining these data continuously, it is possible to grasp the state of the industrial motor 50, such as whether the industrial motor 50 is malfunctioning, normal, or in a situation where it is malfunctioning. . Here, the sensor unit 2 is made to measure the temperature and acceleration, but it is also conceivable that other parameters such as humidity and sound are measured.

  FIG. 3A shows the configuration of the cooling device 21 of the first embodiment of the cooling device 20 in the thermoelectric conversion section 1 shown in FIG. In the cooling device 21 of the first embodiment, twelve rotating shafts 8 are projected on the base plate 7 at equal intervals. A screw hole 81 is provided on the top surface of the rotating shaft 8. In the cooling device 21 of the first embodiment, the fin 9 attached to the rotary shaft 8 is provided with a ring portion 90 through which the rotary shaft 8 is inserted into the through hole 91 and a side surface of the ring portion 90 along the axial direction. One wing portion 92 is provided. The length of the ring portion 90 is the same as the height of the rotating shaft 8. The fin 9 is rotatable with respect to the rotary shaft 8 by inserting the rotary shaft 8 into the through hole 91 of the ring portion 90 and screwing the screw 93 into the screw hole 81 of the rotary shaft 8 exposed from the through hole 91. Attached to.

  The base plate 7 in the cooling device 21 of the first embodiment has a 6 cm square and a thickness of about 1 mm. The rotating shaft 8 has a diameter of 1 mm and a height of about 2 cm. The fins 9 have a height of about 2 cm and a width of about 2 cm, and are all made of aluminum, and the surface is all black anodized. Further, as shown in FIG. 3B, a low-viscosity heat transfer grease 94 is injected between the rotary shaft 8 and the inner peripheral surface of the through hole 91 of the ring portion 90 of the fin 9. As shown in FIG. 3B, the fins 9 that are rotatably attached to the rotating shaft 8 are adjacent to each other even if the wing portion 92 makes one rotation around the rotating shaft 8. There is no collision with the outer peripheral surface of the ring portion 90 of the fin 9 attached to the rotating shaft 8.

  A cooling device 21 as shown in FIG. 3A is attached to a 2 cm square thermoelectric element 6 via grease, and a 6 cm square aluminum base plate 7 is attached to the lower surface of the thermoelectric element 6. As shown in FIG.4 (b), it installed in the housing | casing 51 of an industrial motor. At this time, the base plate 7 is installed so as to be along the vertical direction. In this structure, since the lower surface of the thermoelectric element 6 is installed on the outer surface of the casing heated by the operation of the industrial motor, it is heated and the upper surface is cooled by the cooling device 21 that is air-cooled by the cooling air CW. For this reason, a temperature difference occurs between both surfaces of the thermoelectric element 6, and temperature difference power generation (thermoelectric power generation) is performed by the thermoelectric element 6. The electric power generated by the thermoelectric element 6 is taken out by the wiring 4 and goes to the sensing / radio unit.

  In the industrial motor 50 shown in FIGS. 1A and 1B, the cooling fan 53 works during operation, and the cooling air CW is generated, so that the temperature of the casing 51 is slightly lowered. On the other hand, since the cooling fan 53 also stops when the industrial motor 50 is stopped, the temperature of the housing 51 rises. The industrial motor 50 is repeatedly operated and stopped approximately every 10 minutes. In the present application, the thermoelectric conversion unit 1 is attached to the casing 51 of the industrial motor 50 such that the base plate 7 faces the vertical direction as described above.

  When the cooling device 21 of the first embodiment is attached to the thermoelectric conversion unit 1, as shown in FIGS. 4A and 4B, the cooling air CW generated by the cooling fan 53 is used when the industrial motor 50 is in operation. In addition, all the fins 9 are rotated by the flow of the cooling air, and all the fins 9 face in the lateral direction. As a result, the cooling air CW flows smoothly along the fins 9 and the base plate 7 efficiently dissipates heat, so that the temperature difference between both sides of the thermoelectric element 6 increases, and the power generation capability of the thermoelectric element 6 improves.

  On the other hand, when the industrial motor 50 is stopped, the cooling air CW from the cooling fan 53 disappears. At this time, as shown in FIGS. 4C and 4D, all the fins 9 rotate around the rotation axis 8 by gravity and face in the vertical direction. In this state, natural convection NC that rises due to heat remaining in the casing 51 of the industrial motor 50 is generated, but since all the fins 9 are oriented in the vertical direction, the rising natural convection rises along the fins 9. The fins 9 are cooled by rising natural convection. For this reason, even if the industrial motor 50 is in a stopped state, the heat dissipation effect of the cooling device 21 of the first embodiment is high, and the power generation capability of the thermoelectric element 6 is improved.

  In the present embodiment, the fins 9 are made of aluminum, but it is also possible to use copper or an alloy thereof having higher thermal conductivity. In addition to metals, for example, ceramics with high thermal conductivity such as alumina may be used. It is also conceivable to use different materials for the fin 9, the rotating shaft 8, and the base plate 7.

  In the structure of the cooling device 21 of the first embodiment, there are many rotating shafts 8, and heat transfer grease is filled between the fins 9 and the rotating shaft 8, so that the rotation of the fins 9 is smooth, Since the rotation of the fin 9 with respect to the rotating shaft 8 is also due to the cooling air and its own weight, the probability of failure is low. Further, the heat contact between the rotating shaft 8 and the fins 9 is good due to the heat transfer grease. And since the weight which the rotating shaft 8 receives is only the weight of each fin 9, the burden added to the rotating shaft 8 is small. Also, even if it becomes difficult for several fins 9 to rotate with respect to the rotating shaft 8, there is only a slight decrease in performance, and it does not lead to a fatal failure of the device.

  FIG. 5A shows the shape of fins attached to the cooling device of the second embodiment of the present application. The only difference between the cooling device of the second embodiment and the cooling device of the first embodiment is the shape of the fins, and the arrangement of the plurality of rotating shafts protruding on the base plate is the same. In the second embodiment, only the shape of the fin and the operation of the fin will be described. Moreover, since the shape of the ring part 90 of the fin attached to the cooling device of 2nd Example and the through-hole 91 is the same as 1st Example, it attaches | subjects and demonstrates the same code | symbol about a ring part and a through-hole. .

  The fin 9 used in the cooling device of the second embodiment is provided with a ring portion 90 provided with a through hole 91 through which the rotary shaft 8 is inserted, and protrudes along the axial direction at a position opposite to the side surface of the ring portion 90. The two wing portions 95A and 95B are provided. As shown in FIG. 5C, in the cooling device 22 of the second embodiment, the vertical and horizontal intervals of the rotary shaft 8 are the same. The rotation trajectories of the tip portions of the two wing portions 95A and 95B do not intersect with the rotation trajectories of the tip portions of the two wing portions 95A and 95B protruding from the ring portion 90 of the adjacent fin 9. It has become. That is, even if the fin 9 rotates around the rotation shaft 8, the tip portions of the two wing portions 95A and 95B do not collide with each other.

  The length and thickness of the two blade portions 95A and 95B from the ring portion 90 are the same, but a hole 95C is provided in one blade portion 95A. The role of the hole 95C is to allow air to pass therethrough and to reduce the weight of the wing portion 95A to be lighter than the weight of the wing portion 95B. This is so that the portion 95B comes down. Therefore, the wing portion 95A may be provided with a recess instead of the hole 95C. Further, as in the modification shown in FIG. 5B, the thickness of the wing portion 95A is made thinner than the thickness of the wing portion 95B, and the weight of the wing portion 95A is made larger than the weight of the wing portion 95B. It may be lightened.

  FIG.5 (c) shows operation | movement of the fin 9 of the cooling device 22 of the 2nd Example when the industrial motor 50 shown to Fig.1 (a) is working. All the fins 9 face in the lateral direction by the cooling air CW. FIG. 5 (d) shows the operation of the fin 9 of the cooling device 22 of the second embodiment when the industrial motor 50 shown in FIG. 1 (a) is stopped. When there is no cooling air CW, all the fins 9 rotate so that the heavier wing portion 95B is positioned downward, so that the direction of all the fins 9 is in the vertical direction. Therefore, the rising natural convection NC generated by the heat remaining in the industrial motor 50 rises smoothly along the fins 9 and cools the fins 9.

  FIG. 6A shows the cooling device 23 according to the third embodiment of the present application as viewed from the direction perpendicular to the base plate 7. The cooling device 23 of the third embodiment differs from the cooling devices 21 and 22 of the first and second embodiments in the shape of the fins 9 and the plurality of rotating shafts 8 projecting from the base plate 7. It is arrangement of. In the first and second embodiments, as shown in FIG. 3A, twelve rotary shafts 8 are projected on the base plate 7 at equal intervals. On the other hand, in the cooling device 23 of the third embodiment, when the vertical interval of the rotary shaft 8 is L, the horizontal interval of the rotary shaft 8 is approximately 2L. Specifically, when the vertical interval L of the rotary shaft 8 is 2.5 to 5 mm, the horizontal interval 2L of the rotary shaft 8 is set to 5 to 10 mm. Since the shapes of the ring portion 90 and the through hole 91 of the fin 9 attached to the cooling device 23 of the third embodiment are the same as those of the first and second embodiments, the same reference numerals are used for the ring portion and the through hole. A description will be given.

  As shown in FIG. 6 (b), the fin 9 used in the cooling device of the third embodiment has a ring portion 90 provided with a through hole 91 through which the rotating shaft 8 is inserted, and a side surface of the ring portion 90. Two wing portions 96A and 96B are provided in a projecting position along the axial direction. The two wing portions 95A and 95B of the second embodiment were provided at positions facing the axis (center) of the rotary shaft 8. On the other hand, as shown in FIG. 6C, the two wing portions 96A and 96B of the third embodiment are side surfaces at positions offset left and right with respect to a virtual plane P passing through the center of the rotating shaft 8. Are provided so as to be parallel to each other. In other words, the surface obtained by virtually extending the two blade portions 96 </ b> A and 96 </ b> B toward the ring portion 90 is slightly shifted from the axis of the rotation shaft 8.

  The length and thickness of the two blade portions 96A and 96B from the ring portion 90 are the same, but a hole 96C is provided in one blade portion 96A. The role of the hole 96C is to allow the air to pass therethrough and to reduce the weight of the wing portion 96A to be lighter than the weight of the wing portion 96B. This is because the part 96B comes down. Therefore, the wing portion 96A may be provided with a recess instead of the hole 96C. The two wing portions 96A and 96B have a length that does not collide with the wing portions 96A and 96B of the fin 9 adjacent in the lateral direction, as shown in FIG. .

  On the other hand, when the two wing parts 96A and 96B are rotated and faced in the vertical direction, the interval between the rotary shafts 8 in the vertical direction is half of the interval between the rotary shafts 8 in the horizontal direction. 96B overlaps the wing portion 96A of the fin 9 adjacent in the vertical direction. However, since the wing portion 96A and the wing portion 96B are offset to the left and right with respect to the virtual plane P passing through the center of the rotating shaft 8, the wing portion 96A and the wing portion 96B adjacent in the vertical direction are shown in FIG. As shown in Fig. 2, they overlap without facing each other.

  FIG. 6 (d) shows the operation of the fins 9 of the cooling device 23 of the third embodiment when the industrial motor 50 shown in FIG. 1 (a) is operating. When the industrial motor 50 is operating, all the fins 9 receive the force of the cooling air CW and rotate so as to face in the horizontal direction all at once. At this time, the distance between the fins 9 is effectively narrow at L, and the cooling efficiency is increased.

  On the other hand, in natural air cooling, if the gap between the fins is narrowed, the ventilation resistance increases and convection does not occur, and the heat dissipation effect is worsened. It is known that the optimum fin interval at this time is about 5 to 10 mm. FIG. 6 (e) shows the operation of the fins 9 of the cooling device 23 of the third embodiment when the industrial motor 50 shown in FIG. 1 (a) is stopped. When there is no cooling air CW, all the fins 9 rotate so that the heavier wing portion 96B is located downward, and the orientation of all the fins 9 is in the vertical direction. At this time, since the wing portion 96B overlaps the wing portion 96A adjacent to the lower side, the horizontal interval between the fins 9 is substantially 2L, which is doubled when the industrial motor 50 is in operation. For this reason, the rising natural convection NC generated by the heat remaining in the industrial motor 50 rises smoothly along the fins 9 and cools the fins 9, so that the heat dissipation effect is improved.

  As described above, in the cooling device 23 of the third embodiment, the width of the flow path through which the rising natural convection NC flows when the industrial motor is stopped is larger than the width of the flow path through which the cooling air CW flows when the industrial motor is operated. Is wide (L <2L). For this reason, the optimum fin arrangement can be automatically taken regardless of forced air cooling or natural air cooling.

  FIG. 7A shows a first modification of the shape of the two blade portions 96A and 96B of the fin 9 attached to the cooling device 23 of the third embodiment of the present application. In the first modification, one wing portion 96A is provided with a hole 96C having a large diameter, and the other wing portion 96B is provided with a hole 96D having a smaller diameter. The roles of the holes 96C and 96D are for the purpose of passing air and for reducing the weight of the wing portion 96A to be lighter than the weight of the wing portion 96B. When the fin 9 rotates around its rotation axis 8 by its own weight, This is to ensure that the wing portion 96B comes down. Therefore, the wing portions 96A and 96B may be provided with large and small concave portions instead of the holes 96C and 96D.

  FIG. 7B shows a second modification of the shape of the two wing portions 96A and 96B of the fin 9 attached to the cooling device 23 of the third embodiment of the present application. In the second modification, the wing portions 96A and 96B are equal in thickness, and a protrusion 96E for increasing the area of the wing portion 96B is provided in the vicinity of the tip of one wing portion 96B. The role of the projecting portion 96E is to make the weight of the wing portion 96B heavier than the weight of the wing portion 96A. When the fin 9 is rotated by its own weight around the rotation shaft 8, the wing portion 96B is always on the lower side. This is to make it come. Further, when the cooling air is blown by the protruding portion 9E, the fins 9 are rotated in a direction parallel to the cooling air according to the weathercock principle.

  FIG.7 (c) shows the 3rd modification of the shape of the two wing | blade part 96A, 96B of the fin 9 attached to the cooling device of the 3rd Example of this application. In the third modification, the wing portions 96A and 96B have the same thickness, and a bulging portion 96F for increasing the thickness of the wing portion 96B is provided in the vicinity of the tip portion of the one wing portion 96B. The role of the bulging portion 96F is to make the weight of the wing portion 96B heavier than the weight of the wing portion 96A. When the fin 9 is rotated by its own weight around the rotation shaft 8, the wing portion 96B is always lowered. So that you can come to. Therefore, the shape and installation position of the bulging portion 9F are not particularly limited.

  FIG. 8A shows an exploded structure of the fin 9 attached to the cooling device 24 of the fourth embodiment of the present application. FIGS. 8B and 8C show the assembled state of the fin 9. Show. FIG. 8B is a perspective view of the fin 9, and FIG. 8C is a view of the fin 9 shown in FIG. In the cooling device 24 of the fourth embodiment, the arrangement of the rotating shaft 8 protruding from the base plate 7 may be the same as the arrangement of the rotating shaft 8 in the cooling device 23 of the third embodiment. That is, in the cooling device 24 of the fourth embodiment, the vertical interval between the rotary shafts 8 is L, and the horizontal interval between the rotary shafts 8 is approximately 2L.

  The fin 9 used in the cooling device 24 of the fourth embodiment has a first wing portion 97A projecting along the axial direction on the side surface of the ring portion 90 having a through hole 91 through which the rotation shaft is inserted. And a second wing portion 97B connected to the tip of the first wing portion 97A via a hinge 99. The hinge 99 includes two brackets 99A provided at the distal end portion of the first wing portion 97A, a bracket 99B provided at the distal end portion of the second wing portion 97B, and a hinge shaft 99C. When the bracket 99B is fitted between the two brackets 99A and the hinge shaft 99C is inserted into the through holes provided in the brackets 99A and 99B, the second wing portion 97B is moved to the first wing portion 97A by the hinge 99. It will be able to rotate.

  In this embodiment, there are two spaces between the outer surfaces of the first wing portion 97A and the second wing portion 97B in a state where the second wing portion 97B is closed with respect to the first wing portion 97A. The spring 19 is attached, and the second wing portion 97B is closed with respect to the first wing portion 97A. The urging force of the spring 19 attached between the outer surfaces of the first wing portion 97A and the second wing portion 97B is weak, and the overlapping surface of the first wing portion 97A and the second wing portion 97B. When the wind enters from the outside, the second wing portion 97B has an urging force enough to open the first wing portion 97A.

  FIG. 8 (d) shows a modification of the fin 9 shown in FIG. 8 (c) so that wind can easily enter the overlapping surface of the first wing portion 97A and the second wing portion 97B from the outside. The guide portion 97G is provided at the tip of the second wing portion 97B. The guide portion 97G is provided to be bent outward from the tip portion of the second wing portion 97B. FIG. 8D shows one fin 9 in a state where there is no cooling air in the cooling device 24 of the fourth embodiment. In this state, the fin 9 is second with respect to the first wing portion 97A. The wing portion 97B is folded and closed.

  When the industrial motor is operated and the cooling air CW is generated from the state shown in FIG. 8D, the fins 9 that have been in the vertical direction by the cooling air CW rotate around the rotation shaft 8, and FIG. As shown in (), it faces in the horizontal direction parallel to the flow of the cooling air CW. In this state, the cooling air CW is guided to the guide portion 97G and enters the overlapping surface of the first wing portion 97A and the second wing portion 97B. Then, the second wing portion 97B rotates around the hinge 99 against the urging force of the spring 19 by the force of the cooling air CW, and finally the second wing portion 97B becomes the flow of the cooling air CW. The fins 9 are in a state as shown in FIG.

  In the state shown in FIG. 8F, the guide portion 97G provided at the tip of the second wing portion 97B does not collide with the fin 9 adjacent in the lateral direction. As described above, the cooling device 24 of the fourth embodiment is similar to the cooling device 23 of the third embodiment in that the industrial motor is larger than the width of the flow path through which the cooling air CW flows during operation of the industrial motor. The width of the flow path through which the rising natural convection NC flows can be widened when stopping. For this reason, the cooling device 24 of the fourth embodiment can automatically take the optimum fin arrangement regardless of forced air cooling or natural air cooling.

  FIG. 9A shows a structure of a modified example of the fin 9 attached to the cooling device 24 of the fourth embodiment of the present application. In the cooling device 24 of the fourth embodiment, the second wing portion 97B is connected to the tip of the first wing portion 97A via a hinge 99. On the other hand, in the modification shown in FIG. 9A, the hinge is omitted, and the second wing portion 97B is directly connected to the tip portion of the first wing portion 97A via the two springs 19. The urging force of the spring 19 having both ends fixed to the outer surfaces of the first wing portion 97A and the second wing portion 97B in the closed state is weakened. For this reason, when the wind enters the overlapping surface of the first wing portion 97A and the second wing portion 97B from the outside, the second wing portion 97B has an urging force enough to open the first wing portion 97A. Further, in the modification shown in FIG. 9A, a gap S is formed between the tip of the second wing portion 97B and the first wing portion 97A in a state where the second wing portion 97B is closed. The urging force of the spring 19 is adjusted.

  FIG. 9B shows a state where there is no cooling air in the cooling device 24 of the fourth embodiment in which the fin 9 of the modification shown in FIG. 9A is attached to the rotating shaft 8. In a state where there is no cooling air, the fins 9 are rotated by their own weight and turned in the vertical direction, and the second wing portion 97B is closed with a slight gap S with respect to the first wing portion 97A. It is in a state.

  When the industrial motor is operated and the cooling air CW is generated from the state shown in FIG. 9B, the fins 9 that have been in the vertical direction by the cooling air CW rotate around the rotation shaft 8, and FIG. As shown in (), it faces in the horizontal direction parallel to the flow of the cooling air CW. In this state, the cooling air CW enters the overlapping surface of the first wing portion 97A and the second wing portion 97B from the gap S. Then, the second wing portion 97B rotates against the urging force of the spring 19 by the force of the cooling air CW, and finally the second wing portion 97B moves in a lateral direction parallel to the flow of the cooling air CW. The direction and the fins 9 are in the state shown in FIG.

  In the state shown in FIG. 9D, the tip of the second wing portion 97B does not collide with the fin 9 adjacent in the lateral direction. As described above, in the modification of the cooling device 24 of the fourth embodiment, as in the cooling device 23 of the third embodiment, the industrial width is larger than the width of the flow path through which the cooling air CW flows when the industrial motor is operated. The width of the flow path through which the rising natural convection NC flows when the motor for motor is stopped can be widened. For this reason, even in the modified example of the cooling device 24 of the fourth embodiment, the optimum fin arrangement can be automatically taken regardless of forced air cooling or natural air cooling.

  FIG. 10A shows the shape of the fin 9 attached to the cooling device 25 of the fifth embodiment of the present application. The difference between the cooling device 25 of the fifth embodiment and the cooling device 23 of the third embodiment is the shape of the fins 9 and the arrangement of a plurality of rotating shafts 8 protruding on the base plate 7. In the cooling device 23 of the third embodiment, when the vertical interval of the rotary shaft 8 is L, the horizontal interval of the rotary shaft 8 is approximately 2L. This is because in the third embodiment, the lengths of the two wing portions 96A and 96B provided on the fin 9 are the same. On the other hand, the two wing portions 98A and 98B of the fifth embodiment have two wing portions 98A and 98B with respect to a virtual plane P passing through the center of the rotating shaft 8, as shown in FIG. Imaginary plane Q that bisects in the thickness direction is offset from plane P. That is, the two wing portions 98A and 98B are provided so as to be offset in the left and right directions relative to the virtual plane P and to be parallel to each other.

  Furthermore, although the thickness of the two wing parts 98A and 98B is the same, the length from the ring part 90 is longer than that of the wing part 98B from the wing part 98A as shown in FIGS. 10 (a) to 10 (c). Is longer. For this reason, the weight of the wing part 96B is heavier than the weight of the wing part 96A, and the wing part 96B always comes down when the fin 9 rotates by its own weight around the rotation shaft 8. Then, assuming that the length of the wing portion 98B is about twice the length of the wing portion 98A, the interval between the horizontal rotation shafts 8 is about 1.5 L with respect to the interval L between the vertical rotation shafts 8. It has become. Since the interval between the fins 9 has an optimum interval according to the convection velocity, the interval between the rotating shafts 8 in the horizontal direction may be set according to the convection velocity. In this embodiment, the interval L of the rotating shaft 8 is assumed to be 2.5 to 5 mm, but the interval ratio of the fins 9 in the vertical and horizontal directions and the length of L are not limited to this length.

  FIG. 10 (d) shows the operation of the fins 9 of the cooling device 25 of the fifth embodiment when the industrial motor 50 shown in FIG. 1 (a) is operating. When the industrial motor 50 is operating, all the fins 9 receive the force of the cooling air CW and rotate so as to face in the horizontal direction all at once. In the state where the fins 9 are turned sideways, the interval between the rotary shafts 8 and the lengths of the wing portions 98A and 98B are determined so that the wing portion 98A and the adjacent wing portion 98B of the fin do not collide. At this time, the interval between the fins 9 (the flow path width of the cooling air CW) is effectively narrow at L, and the cooling efficiency is increased.

  FIG. 10 (e) shows the operation of the fins 9 of the cooling device 25 of the fifth embodiment when the industrial motor 50 shown in FIG. 1 (a) is stopped. When there is no cooling air CW, all the fins 9 rotate so that the longer wing portion 98B faces downward, and the orientation of all the fins 9 becomes the vertical direction. At this time, since the lengths of the wing part 98A and the wing part 98B are different, the wing part 98B partially overlaps the wing part 98A adjacent to the lower side. The horizontal interval between the fins 9 (the flow width of the rising natural convection NC) is substantially 1.5 L, which is 1.5 times larger than when the industrial motor 50 is in operation. For this reason, the rising natural convection NC generated by the heat remaining in the industrial motor 50 rises smoothly along the fins 9 and cools the fins 9, so that the heat dissipation effect is improved.

  As described above, in the cooling device 25 of the fifth embodiment, the width of the flow path through which the rising natural convection NC flows when the industrial motor is stopped is larger than the width of the flow path through which the cooling air CW flows when the industrial motor is operated. Is wide (L <1.5L). For this reason, the optimum fin arrangement can be automatically taken regardless of forced air cooling or natural air cooling.

  In the embodiment described above, heat transfer grease is used between the rotation shaft and the fins to achieve both the rotation mechanism and the heat transfer mechanism. On the other hand, liquid metal can also be used between the rotating shaft and the fins. As the liquid metal, for example, a metal that is always in a liquid state at room temperature, such as mercury, gallium, and cesium, can be used. When a liquid metal is inserted between the rotating shaft and the fin, the interval between the rotating shaft and the fin is made very narrow so that the liquid metal can be held with surface tension. In this way, smooth rotation with respect to the rotation axis of the fin can be realized. Further, since the liquid metal has better heat conduction than the heat transfer grease, the heat radiation effect of the cooling device can be enhanced.

  As another example, a low-melting-point metal having a melting point Tm between the installation temperature T1 during forced convection and the installation temperature T2 during natural convection at a higher temperature is inserted between the rotating shaft and the fin. Is also possible. For example, various low melting point metals can be obtained by using various alloys such as gallium having a melting point of 29.77 ° C.

  The operation of the fins of the cooling device when such a low melting point metal is inserted between the rotating shaft of the cooling device and the fins will be described. First, let us consider a case where the motor is completely stopped from a forced convection state due to cooling air to a natural convection state. When forced convection by cooling air stops, the installation temperature T1 during forced convection rises to the installation temperature T2 during natural convection. After a while in this state, the liquid metal melts and changes from a solid to a liquid, so that the fins fixed to the rotating shaft rotate downward, and heat dissipation is started by natural convection.

  Thereafter, when the motor rotates and forced convection starts, the installation temperature T2 at the time of natural convection falls to the installation temperature T1 at the time of forced convection. However, since the liquid metal does not suddenly change from liquid to solid, before the liquid metal solidifies, the fin rotates around the rotation axis and faces in the lateral direction. As time elapses, the liquid metal is solidified and solidified by being cooled by forced convection. In this state, the fins are fixed horizontally even if the forced convection air volume slightly varies. Therefore, the fins are fixed in a horizontal state optimal for forced convection and are always liquid, even under conditions (such as industrial motors) where a large air volume is generated at the start of forced convection and the air volume fluctuates depending on the load. The heat dissipation effect can be enhanced as compared with the heat transfer grease in the state. Thereafter, when the forced convection completely stops, the above cycle is repeated.

  In the cooling device used for the temperature difference power generation of the present application described above, a plurality of fins are rotatably supported via a heat transfer grease on a rotating shaft installed in a large number perpendicular to the plate-like base plate. ing. For this reason, even when the direction of the airflow flowing through the cooling device changes with time, the thermoelectric element can be efficiently cooled. Further, when the heat source for temperature difference power generation is small and the scale of the thermoelectric converter is small, even one fin is effective.

  The present application has been described in detail with particular reference to preferred embodiments thereof. For easy understanding of the present application, specific forms of the present application are appended below.

(Appendix 1) A cooling device for temperature difference power generation that generates power by giving a temperature difference to a thermoelectric element attached to a heat source,
A base plate attached to the thermoelectric element;
At least one rotating shaft projecting from the base plate;
A cooling device for temperature difference power generation, comprising a fin attached to the rotating shaft and rotatable about the rotating shaft.
(Appendix 2) The heat source is provided with an air cooling device that causes cooling air to flow laterally with respect to the heat source during heat generation.
The base plate is fixed to the thermoelectric element in parallel to the cooling air,
2. The cooling for temperature difference power generation according to claim 1, wherein when the heat source generates heat, the fin rotates and becomes parallel to the cooling air, and when the heat source stops generating heat, the fin is directed in the vertical direction by its own weight. apparatus.
(Supplementary Note 3) There are a plurality of the rotation shafts, and they are arranged on the base plate in the vertical and horizontal directions at equal intervals.
The fin includes a ring portion through which the rotating shaft is inserted, and one wing portion projecting along the axial direction on a side surface of the ring portion,
The cooling device for temperature difference power generation according to appendix 2, wherein a tip portion of the wing portion has a length extended to a position close to a ring portion of the adjacent fin.
(Supplementary Note 4) There are a plurality of the rotation shafts, which are arranged on the base plate in the vertical and horizontal directions at equal intervals.
The fin includes a ring portion through which the rotating shaft is inserted, and two wing portions projecting along the axial direction at positions opposed to side surfaces of the ring portion,
The temperature according to appendix 2, wherein the rotation trajectories of the tip portions of the two wing portions do not intersect with the rotation trajectories of the tip portions of the two wing portions protruding from the ring portions of adjacent fins. Cooling device for differential power generation.
(Supplementary Note 5) There are a plurality of the rotation shafts, and the horizontal intervals in the vertical and horizontal directions are arranged side by side at a longer interval than the vertical intervals on the base plate.
The fin includes two wing portions provided in parallel with each other on a ring portion through which the rotation shaft is inserted and side surfaces at positions offset to the left and right from a plane passing through the center of the ring portion on both sides of the ring portion. With
The two wings have a length that does not collide with the wings of the fins adjacent in the lateral direction at the lateral position, and overlap the wings of the fins adjacent in the vertical direction at the longitudinal position. The cooling device for temperature difference power generation according to appendix 2, wherein

(Additional remark 6) The thickness of the said 2 wing | blade part is uniform, The hole is provided in one wing | blade part, The cooling device for temperature difference power generation of Additional remark 4 or 5 characterized by the above-mentioned.
(Supplementary note 7) The cooling device for temperature difference power generation according to supplementary note 4 or 5, wherein the thickness of the two wing portions is uniform, and holes having different sizes are provided respectively.
(Additional remark 8) The thickness of the said 2 wing | blade part is uniform, and the area of one wing | blade part is larger than the area of the other wing | blade part. Cooling system.
(Supplementary note 9) The cooling device for temperature difference power generation according to supplementary note 4 or 5, wherein the thickness of the two blade portions is uniform, and a bulge portion is provided on one of the blade portions. .
(Supplementary note 10) The temperature difference power generation according to supplementary note 4 or 5, wherein the thickness of the two blade portions is uniform, and the length of one of the blade portions is longer than the length of the other blade portion. Cooling device.

(Additional remark 11) The cooling apparatus for temperature difference power generation of Additional remark 4 or 5 characterized by the thickness of one wing | blade part being thicker than the thickness of the other wing | blade part among the said 2 blade | wing parts.
(Supplementary Note 12) There are a plurality of the rotation shafts, and the horizontal intervals in the vertical and horizontal directions are arranged side by side at a longer interval than the vertical intervals on the base plate.
The fin includes a ring part through which the rotating shaft is inserted, a first wing part protruding in the axial direction on a side surface of the ring part, and a hinge at a tip part of the first wing part. Second wings connected to each other,
The length of the second wing portion is formed to be equal to or less than the length of the first wing portion,
The second wing part is superimposed on the first wing part side when the heat source is not generating heat by an urging member attached around the hinge,
The urging force of the urging member is such that when the first wing portion rotates and becomes parallel to the cooling air when the heat source generates heat, the second wing portion is moved with respect to the first wing portion. Is an urging force of a degree that opens the part in a state parallel to the flow of the cooling air,
The length of the first wing portion is a length that prevents the hinge from colliding with the ring portion of the fin adjacent in the vertical direction when the heat source is not generating heat.
In a state where the second wing portion is open with respect to the first wing portion, a length obtained by adding the length of the second wing portion to the length of the first wing portion is set in the lateral direction. The cooling device for temperature difference power generation according to appendix 2, wherein the cooling device has a length that does not collide with a ring portion of an adjacent fin.
(Supplementary note 13) There are a plurality of the rotation shafts, and the horizontal intervals in the vertical and horizontal directions are arranged side by side at a longer interval than the vertical intervals on the base plate .
The full fin is biased with said rotary shaft ring portion to be inserted, the first wing portion projecting in the axial direction on the side surface of the ring portion, ahead of the first wing portion Comprising a second wing connected via a member;
The length of the second wing portion is formed to be equal to or less than the length of the first wing portion,
The second wing portion is overlapped by the biasing member on the first wing portion side when the heat source is not generating heat,
The urging force of the urging member is such that the second wing is parallel to the flow of the cooling air with respect to the first wing by the cooling air generated when the heat source generates heat. It is an energizing force that opens,
The length of the first wing portion is such a length that the biasing member does not collide with the ring portion of the fin adjacent in the vertical direction when the heat source is not generating heat.
In a state where the second wing portion is open with respect to the first wing portion, a length obtained by adding the length of the second wing portion to the length of the first wing portion is set in the lateral direction. The cooling device for temperature difference power generation according to appendix 2, wherein the cooling device has a length that does not collide with a ring portion of an adjacent fin.
(Additional remark 14) Between the said rotating shaft and the said ring part, heat-transfer grease or a liquid metal is inserted as a lubrication agent, The temperature difference electric power generation in any one of Additional remark 3 to 12 characterized by the above-mentioned. Cooling system.
(Additional remark 15) The low-melting-point metal is inserted as a lubricant between the said rotating shaft and the said ring part, The cooling device for temperature difference power generation in any one of Additional remark 3 to 12 characterized by the above-mentioned.

(Supplementary note 16) The cooling device for temperature difference power generation according to supplementary note 15, wherein the melting point of the low melting point metal is between a maximum operating temperature and a minimum operating temperature.
(Appendix 17) A heat collection member that efficiently transfers heat from the heat source to the thermoelectric element is provided between the heat source and the thermoelectric element. Cooling device for temperature difference power generation.
(Supplementary note 18) The temperature difference power generation cooling device according to any one of supplementary notes 2 to 17, wherein the heat source is a motor, and the air cooling device is a fan attached to a rotating shaft of the motor.

1 Thermoelectric Conversion Unit 2 Sensor Unit 3 Sensing / Wireless Unit
4 Wiring 5 Heat collecting plate 6 Thermoelectric element 7 Base plate 8 Rotating shaft 9 Fin 10 Temperature difference power generator 19 Spring 20-25 Cooling device
31 Booster circuit
32 storage battery
33 MPU
34 Radio circuit
35 Antenna
36 Power line
37 signal lines
50 Industrial motor
51 box
52 Rotating shaft 53 Cooling fan
54 Radiation fins
55 base stand
56 legs
81 Screw hole 90 Ring part
91 through-holes 92 and 95A. 95B. 96A, 96B, 97A, 97B, 98A, 98B wings
93 screws
94 Heat transfer grease
95C, 96C6 hole
96E Protrusion
96F bulge 99 hinge
99A, 99B Bracket
99C Hinge shaft
CW cooling air
NC rising natural convection

Claims (5)

A cooling device for temperature difference power generation that generates power by giving a temperature difference to a thermoelectric element attached to a heat source,
A base plate attached to the thermoelectric element;
At least one rotating shaft projecting from the base plate;
A fin attached to the rotary shaft and rotatable around the rotary shaft;
The heat source is provided with an air cooling device that causes cooling air to flow transversely to the heat source when heat is generated,
The base plate is fixed to the thermoelectric element in parallel to the cooling air,
The fin, the at the time of the heat source of the heat generation becomes parallel to the cooling air is rotated, the cooling apparatus for thermal energy conversion, characterized in that facing the longitudinal direction by its own weight at the time of heat generation stop of the heat source. There are a plurality of the rotation shafts, arranged on the base plate at equal intervals in the vertical and horizontal directions,
The fin includes a ring portion through which the rotating shaft is inserted, and one wing portion projecting along the axial direction on a side surface of the ring portion,
2. The cooling device for temperature difference power generation according to claim 1 , wherein a tip end portion of the wing portion has a length extended to a position close to a ring portion of the adjacent fin. 3. There are a plurality of the rotation shafts, and the horizontal intervals in the vertical and horizontal directions are arranged on the base plate at a longer interval than the vertical interval.
The fin includes two wing portions provided in parallel with each other on a ring portion through which the rotation shaft is inserted and side surfaces at positions offset to the left and right from a plane passing through the center of the ring portion on both sides of the ring portion. With
The two wings have a length that does not collide with the wings of the fins adjacent in the lateral direction at the lateral position, and overlap the wings of the fins adjacent in the vertical direction at the longitudinal position. The cooling apparatus for temperature difference power generation according to claim 1 . There are a plurality of the rotation shafts, and the horizontal intervals in the vertical and horizontal directions are arranged on the base plate at a longer interval than the vertical interval.
The fin includes a ring part through which the rotating shaft is inserted, a first wing part protruding in the axial direction on a side surface of the ring part, and a hinge at a tip part of the first wing part. Second wings connected to each other,
The length of the second wing portion is formed to be equal to or less than the length of the first wing portion,
The second wing part is superimposed on the first wing part side when the heat source is not generating heat by an urging member attached around the hinge,
The urging force of the urging member is such that when the first wing portion rotates and becomes parallel to the cooling air when the heat source generates heat, the second wing portion is moved with respect to the first wing portion. Is an urging force of a degree that opens the part in a state parallel to the flow of the cooling air,
The length of the first wing portion is a length that prevents the hinge from colliding with the ring portion of the fin adjacent in the vertical direction when the heat source is not generating heat.
In a state where the second wing portion is open with respect to the first wing portion, a length obtained by adding the length of the second wing portion to the length of the first wing portion is set in the lateral direction. The cooling device for temperature difference power generation according to claim 1 , wherein the cooling device has a length that does not collide with a ring portion of an adjacent fin. There are a plurality of the rotation shafts, and the horizontal intervals in the vertical and horizontal directions are arranged on the base plate at a longer interval than the vertical interval.
The fin includes a ring portion through which the rotating shaft is inserted, a first wing portion projecting along the axial direction on a side surface of the ring portion, and a biasing member at a tip of the first wing portion. A second wing connected via
The length of the second wing portion is formed to be equal to or less than the length of the first wing portion,
The second wing portion is overlapped by the biasing member on the first wing portion side when the heat source is not generating heat,
The urging force of the urging member is such that the second wing is parallel to the flow of the cooling air with respect to the first wing by the cooling air generated when the heat source generates heat. It is an energizing force that opens,
The length of the first wing portion is such a length that the biasing member does not collide with the ring portion of the fin adjacent in the vertical direction when the heat source is not generating heat.
In a state where the second wing portion is open with respect to the first wing portion, a length obtained by adding the length of the second wing portion to the length of the first wing portion is set in the lateral direction. The cooling device for temperature difference power generation according to claim 1, wherein the cooling device has a length that does not collide with a ring portion of an adjacent fin.

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