JP2019082273A - Cooling system - Google Patents

Abstract

To provide a cooling system capable of naturally circulating a refrigerant more surely.SOLUTION: A cooling system 1 includes a circulation flow passage 3 through which a refrigerant is circulated, and a bubble reservoir 5. The circulation flow passage 3 includes a heat absorbing portion 7 which absorbs heat from a cooling object fluid L1 in the outside, a first flow passage 9 including a region which extends to the upper side from the heat absorbing portion 7, a heat radiation portion 11 which is connected to a side opposite from the heat absorbing portion 7 of the first flow passage 9 and radiates the heat to the outside, and a second flow passage 13 which extends from the heat radiation portion 11 to the heat absorbing portion 7, in this order. The bubble reservoir 5 constitutes a sealed space which branches to the upper side from the first flow passage 9.SELECTED DRAWING: Figure 1

Description

  The present disclosure relates to a cooling system that naturally circulates a refrigerant.

  A cooling system is known that circulates a refrigerant through a circulation channel, absorbs heat from an object to be cooled in an endothermic unit that is a part of the circulation channel, and dissipates heat from the refrigerant in another radiator unit that is another part of the circulation channel. It is done. In addition, among such cooling systems, one that naturally circulates a refrigerant without using a power of a pump or the like is also known (for example, Patent Documents 1 and 2). In patent document 1 and 2, a bubble is produced in a refrigerant | coolant and the refrigerant | coolant is circulated using the buoyancy of the bubble.

JP, 2015-129594, A JP, 2015-230907, A

  In the experiments of the present applicant, it was found that when the cooling system as disclosed in Patent Documents 1 and 2 is used, natural circulation may be stopped. Therefore, a cooling system capable of naturally circulating the refrigerant more reliably is desired.

  A cooling system according to an aspect of the present disclosure is a circulation flow path through which a refrigerant circulates, and a heat absorption portion absorbing heat from an external cooling target, a first flow path including a portion extending upward from the heat absorption portion, A circulation flow path which is connected to the opposite side to the heat absorption portion of one flow path and includes a heat dissipation portion for radiating heat to the outside, and a second flow path extending from the heat dissipation portion to the heat absorption portion And an air bubble reservoir forming an enclosed space which branches upward from the first flow path.

  In one example, the bubble reservoir branches from the highest position of the circulation channel.

  In one example, the heat dissipation unit is located above the heat absorption unit.

  In one example, the average value of the cross-sectional areas of the second flow channels is larger than the average value of the cross-sectional areas of the first flow channels.

  In one example, the second flow path has a tank portion where the cross-sectional area is locally increased halfway.

  In one example, the refrigerant has a boiling point of 30 ° C. or more and 60 ° C. or less.

  According to the above configuration, natural circulation can be more reliably generated.

BRIEF DESCRIPTION OF THE DRAWINGS The schematic diagram which shows schematic structure of the cooling system which concerns on 1st Embodiment. The schematic diagram which shows schematic structure of the cooling system which concerns on 2nd Embodiment.

First Embodiment
(overall structure)
FIG. 1 is a schematic view showing a schematic configuration of a cooling system 1 according to the first embodiment.

  The cooling system 1 is configured to cool a cooling target fluid L1 as a cooling target. The fluid to be cooled L1 may be a gas or a liquid. Further, the component of the fluid to be cooled L1 is also optional. In addition, the temperature before cooling of the fluid to be cooled L1 and the temperature after cooling (target temperature) may be appropriately set.

  The fluid to be cooled L1 is stored in the cooling container 15. For example, the cooling container 15 has an inlet and an outlet (not shown), although not shown. The fluid to be cooled L1 is continuously or intermittently supplied from the inlet to the cooling container 15, temporarily retained in the cooling container 15, and discharged from the outlet. In the process, the fluid to be cooled L1 is cooled by the cooling system 1.

  In addition, the shape and volume of the container 15 for cooling may be set suitably. The cooling container 15 may be a closed container or a container opened to the atmosphere. Further, the cooling container 15 may have a shape (for example, a part of a flow passage having a constant cross-sectional area) such that the fluid to be cooled L1 does not temporarily stay. The cooling container 15 may be captured as part of the cooling system 1 or may be captured as a separate member from the cooling system 1.

  The cooling system 1 has a circulation flow path 3 for circulating the refrigerant L3 that takes heat from the fluid to be cooled L1, and a bubble reservoir 5 for more reliably generating natural circulation of the refrigerant L3. The materials and dimensions of the members constituting the circulation channel 3 and the bubble reservoir 5 may be set appropriately. For example, these members are made of metal. Moreover, the diameter (for example, the minimum diameter, the average diameter, or the maximum diameter) of the circulation flow path 3 and the bubble reservoir 5 is, for example, 10 mm or more or 100 mm or more.

  The cooling system 1 is, for example, configured not to require power and / or signal input (operation). For example, a pump for circulating the refrigerant L3, a control valve for controlling the flow of the refrigerant L3 (which is controlled by the controller), and / or a fan for cooling the refrigerant L3 (in the heat release unit 11 described later) are provided. It is not done. However, such a component may be provided depending on the application and / or size of the cooling system 1 and the like.

(Circulation channel)
The circulation flow path 3 has a heat absorbing portion 7, a first flow path 9, a heat dissipation portion 11, and a second flow path 13 in order in the flow direction of the refrigerant L3 (indicated by the dotted arrow in the figure).

  The heat absorption unit 7 is a portion (flow path) that performs heat absorption of the fluid to be cooled L1 by the refrigerant L3. The heat absorption portion 7 is located, for example, in the cooling target fluid L1 (and / or in the cooling container 15), and the outer surface thereof is in contact with the cooling target fluid L1. Moreover, the heat absorption part 7 is extended so that the direction from the upstream side of the refrigerant | coolant L3 to the downstream side turns into a direction from upper direction, for example as a whole. In other words, the outlet of the heat absorbing portion 7 is located above the inlet of the heat absorbing portion 7. In addition, the direction from the upstream side to the downstream side may be a horizontal direction or a direction from the upper side to the lower side in part of the heat absorbing portion 7.

  The heat absorption part 7 may be made into a suitable shape so that a contact area with the cooling object fluid L1 may become large. For example, the heat absorbing portion 7 may extend in a shape of a coil (in the example shown) or a meander. That is, the heat absorption part 7 may be bent and / or curved and extended appropriately. Further, for example, the heat absorbing portion 7 may branch into a plurality of flow paths and merge again, or may form a thin and wide flow path. The cross-sectional area of the heat absorbing portion 7 (the area of the cross section (cross section perpendicular to the flow). Hereinafter, the same applies unless otherwise noted) may be set as appropriate. For example, the cross-sectional area of the heat absorption part 7 may be smaller than the cross-sectional area of the other part of the circulation flow path 3.

  The first flow path 9 is a portion that connects the downstream side of the heat absorbing portion 7 and the upstream side of the heat radiating portion 11. The first flow path 9 has, for example, a front stage 9 a extending upward from the heat absorption section 7 and a rear stage 9 b extending from the front stage 9 a and reaching the heat dissipation section 11.

  The front stage 9a extends, for example, linearly in the vertical direction. However, the front part 9a may extend upward from the heat absorbing part 7 as a whole (the outlet of the front part 9a may be located above the inlet of the front part 9a), and is inclined in the vertical direction Or may include a portion that bends or curves halfway. Also, in part, the direction from the upstream side to the downstream side may be a horizontal direction or a direction from the upper side to the lower side. The cross-sectional area of the front part 9a is, for example, constant.

  The rear part 9 b linearly extends in the horizontal direction from the front part 9 a. However, the rear part 9 b may extend downward from the front part 9 a. In addition, the rear part 9b may include a portion that bends or curves halfway. Also, in part, the direction from the upstream side to the downstream side may be the horizontal direction or the direction from the lower side to the upper side. The cross-sectional area of the rear part 9 b is, for example, constant.

  For example, the entire rear portion 9b is located within the same height range (position of the same height in the illustrated example) as the highest position (connection position with the rear portion 9b) of the front portion 9a. There is. However, it is also possible to position a part of the rear part 9b higher than the highest position of the front part 9a. The front stage 9 a and the rear stage 9 b may have different cross sections or may be the same.

  The heat radiating portion 11 is a portion for radiating the heat of the refrigerant L3 to the outside of the circulation flow path 3. The heat radiating portion 11 may be cooled by, for example, the atmosphere, may be cooled by a gaseous and / or liquid refrigerant, or may be buried in the ground and cooled.

  In the example of illustration, the thermal radiation part 11 is arrange | positioned in the container 17 for thermal radiation with which the refrigerant | coolant L5 was filled, and is cooled by this. The refrigerant L5 has, for example, a relatively low boiling point, and boils in the heat radiation container 17. Although not particularly illustrated, in the heat radiation container 17, the gas phase refrigerant L5 is positioned above the liquid phase refrigerant L5.

  The heat radiating portion 11 is, for example, a channel extending in such a manner that the direction from the upstream side to the downstream side of the refrigerant L3 is from the upper side to the lower side as a whole. That is, the outlet of the heat radiating portion 11 is located below the inlet of the heat radiating portion 11. However, for example, the whole of the heat dissipation portion 11 may extend in the horizontal direction, or in part, the direction from the upstream side to the downstream side may be a direction from the lower side to the upper side. Furthermore, as a whole, the heat radiating portion 11 can also make the direction from the upstream side to the downstream side a direction from the lower side to the upper side.

  The heat radiating portion 11 may be appropriately shaped so as to increase the contact area with the refrigerant L5 (or the one for cooling the other heat radiating portion 11). For example, the heat dissipation portion 11 may extend in a shape such as a meander shape (example shown) or a coil shape. That is, the heat dissipation part 11 may be bent and / or curved and extended appropriately. Further, for example, the heat dissipation unit 11 may be branched into a plurality of flow paths and may be merged again, or a thin and wide flow path may be formed. The cross-sectional area of the heat dissipation unit 11 may be set appropriately.

  For example, the whole of the heat dissipation part 11 is located above the whole of the heat absorption part 7. However, the heat dissipating portion 11 is partially located below the highest position of the heat absorbing portion 7, or the whole is located lower than the highest position of the heat absorbing portion 7, or a portion thereof is heat absorbing portion It may be located below the whole of 7, or the whole may be located under the whole of the heat absorption part 7.

  The second flow path 13 is a portion that connects the downstream side of the heat radiating portion 11 and the upstream side of the heat absorbing portion 7. As a whole, the second flow path 13 extends such that the direction from the upstream side to the downstream side of the refrigerant L3 is a direction from the upper side to the lower side. That is, the outlet of the second flow path 13 is located below the inlet of the second flow path 13. However, the direction from the upstream side to the downstream side may be a horizontal direction or a direction from the upper side to the lower side in part of the second flow path 13. In the illustrated example, the second flow path 13 has a portion (reference numeral omitted) extending in the horizontal direction from the heat dissipation portion 11 and a hanging portion 13a extending downward from the portion.

  The hanging portion 13a extends, for example, linearly in the vertical direction. However, the hanging portion 13a may be inclined in the vertical direction, or may include a portion bent or curved halfway. Also, in part, the direction from the upstream side to the downstream side may be a horizontal direction or a direction from the upper side to the lower side.

  The downstream side portion (drooping portion 13a) of the second flow path 13 is located in the fluid to be cooled L1 (and / or in the cooling container 15), and is connected to the heat absorbing portion 7. In the second flow path 13, for example, heat is less likely to flow from the fluid to be cooled L1 to the refrigerant L3 as compared to the heat absorption portion 7. For example, while the heat absorption portion 7 is configured to increase the contact area with the fluid to be cooled L1 as described above, the drooping portion 13a has a cross-sectional area larger than that of the heat absorption portion 7, It extends in a straight line. That is, in the fluid to be cooled L1, the ratio of the surface area to the volume of the drooping portion 13a is sufficiently smaller than the ratio of the surface area to the volume of the heat absorbing portion 7.

  The relative relationship between the sizes of the cross-sectional areas may be set appropriately at various portions in the circulation flow path 3. For example, as described above, the cross-sectional area of the heat absorption portion 7 may be smaller than the cross-sectional areas of the other portions. The cross-sectional areas of the first channel 9 and the second channel 13 may be identical to each other or may be different from each other

(Bubble pool)
The bubble reservoir 5 comprises a closed container. The bubble reservoir 5 is connected to the first flow path 9 to form a sealed space which branches upward from the first flow path 9. For example, an opening 3a (an opening that opens to the side of the bubble reservoir 5 at a branch point) connecting the first channel 9 and the bubble reservoir 5 is, for example, opened upward from the first channel 9. Thus, when the closed space is branched upward from the first flow passage 9, for example, the opening 3a is opened upward from the first flow passage 9, and at least a part of the closed space is positioned above the opening 3a. Say that. The opening 3a does not have to be open in parallel with the vertical direction as long as the opening 3a is opened upward from the first flow path 9 toward the bubble reservoir 5, and is opened obliquely with respect to the vertical direction May be

  More specifically, in the illustrated example, the opening 3 a is formed on the end face of the front portion 9 a of the first flow passage 9. In another viewpoint, the extending direction of the front portion 9a and the opening direction of the opening 3a to the bubble reservoir 5 coincide with each other. And, the direction is the vertical direction (not inclined in the vertical direction). The position of the opening 3 a is, in the illustrated example, the highest position of the first flow passage 9 and the highest position of the circulation flow passage 3.

  The shape of the bubble reservoir 5 may be an appropriate shape. In the illustrated example, the bubble reservoir 5 includes a container 5a having a columnar space extending upward with a cross-sectional area larger than the cross-sectional area (for example, the largest cross-sectional area) of the circulation flow path 3. In addition, the part (code | symbol abbreviation | omission) between the container part 5a and the opening 3a (branch point) shall also be a part of bubble accumulation part 5 by description of this embodiment. The container portion 5a is in communication with the first flow passage 9 at the lower surface.

  The volume of the bubble reservoir 5 may be set appropriately. For example, the volume of the bubble reservoir 5 or the container 5 a is 10% or more and 60% or less, or 30% or more and 50% or less of the volume of the circulation channel 3.

(Refrigerant)
The components of the refrigerant L3 (the boiling point in another aspect) are appropriately set according to the application of the cooling system 1 (in another aspect, the type of the fluid L1 to be cooled, the temperature before cooling and the temperature after cooling), etc. Good. For example, the refrigerant L3 is selected from those that can boil by taking heat from the fluid to be cooled L1 in the heat absorbing portion 7. Further, for example, the refrigerant L3 has a boiling point of 30 ° C. or more and 60 ° C. or less. A fluorine-type refrigerant | coolant can be mentioned as a refrigerant | coolant of such a boiling point. In addition, depending on the application of the cooling system 1, water may be used as the refrigerant L3.

(Function of cooling system)
When the fluid to be cooled L1 having a temperature higher than that of the refrigerant L3 in the heat absorbing portion 7 is supplied into the cooling container 15, the refrigerant L3 takes heat from the fluid to be cooled L1. Under the present circumstances, a part of refrigerant | coolant L3 deprives the calorie | heat amount corresponded to a latent heat from the fluid L1 for cooling, forming the bubble B and boiling. Thereby, the fluid to be cooled L1 is cooled quickly and / or sufficiently.

  With the above-described action, in the circulation flow path 3, a flow from the second flow path 13 to the first flow path 9 via the heat absorbing portion 7 occurs. That is, natural circulation of the refrigerant L3 occurs. The reason is that, for example, in the second flow path 13 and the heat absorbing portion 7, the density of the refrigerant L3 in the latter is lower, and in the latter, the pressure due to gravity is lower. Also, for example, the bubbles B generated in the heat absorbing portion 7 float up in the liquid refrigerant L3 due to the buoyancy.

  Here, when the bubble reservoir 5 is not provided, the flow rate of the natural circulation may be reduced or the natural circulation may be stopped. The inventor of the present application has found that one of the factors is that air bubbles B flow from the front part 9a to the rear part 9b (and further to the heat dissipation part 11). The natural circulation is hindered, for example, because the density of the refrigerant L3 above the second flow path 13 (the heat release portion 11 and / or the rear portion 9b) is lowered by the air bubble B. The pressure difference with the part 7 may be reduced. In addition, for example, the buoyancy of the air bubble B acts in a direction that hinders the circulation in the rear part 9 b and / or the heat dissipation part 11.

  However, in the present embodiment, since the air bubble reservoir 5 constitutes a sealed space which is branched upward from the first flow path 9, the possibility of such a problem is reduced, and natural circulation is more reliably performed. Can be generated. Specifically, the bubbles B enter the bubble reservoir 5 from the front stage 9 a and stay in the bubble reservoir 5. That is, the bubble B does not easily flow into the subsequent stage 9 b and thereafter. As a result, the possibility that the air bubble B interferes with natural circulation is reduced.

  Furthermore, the pressure rise in the circulation flow path 3 resulting from the generation of the bubble B can be suppressed by providing the bubble reservoir portion 5. By suppressing the pressure rise, for example, first, the pressure resistance and / or the durability in the circulation flow path 3 can be lowered. As a result, costs can be reduced. Further, for example, by suppressing the pressure rise, the rise of the boiling point of the refrigerant L3 in the circulation flow path 3 can be suppressed. As a result, it is possible to suppress a decrease in the cooling capacity due to the vaporization of the refrigerant L3. From another viewpoint, material selection (boiling point adjustment) of the refrigerant L3 is facilitated.

  Thus, by providing the bubble reservoir 5, not only the decrease in natural circulation caused by the bubble B is suppressed, but also the rise in the boiling point of the refrigerant L3 caused by the bubble B (a pressure increase) is suppressed. By dramatically reducing the possibility that the cooling capacity may decrease (fluctuate) due to, for example, the temperature change of the fluid to be cooled L1 and / or the temperature change of the environment around the cooling system 1 by exhibiting both effects. Can. In other words, it is possible to dramatically widen the temperature range in which the cooling capacity can be sufficiently exhibited.

  Further, in the present embodiment, the bubble reservoir 5 is branched from the highest position of the circulation channel 3. Therefore, the above-mentioned effect that causes natural circulation more reliably is increased. For example, even when the air bubble reservoir 5 does not branch from the highest position of the circulation flow path 3 (in this case also included in the technology according to the present disclosure), the air bubbles B may be retained somewhat. If possible, it is possible to reduce the possibility that the air bubbles B disturb natural circulation. However, in this case, there is a possibility that the air bubble B may stay in the vicinity of the highest position of the circulation flow path 3 as well as the air bubble reservoir 5 or the air bubble B may flow into the subsequent stage 9b and thereafter. As a result, the effect of reducing the possibility that the air bubbles B interfere with natural circulation is reduced. However, in the present embodiment, it is such low.

  Further, in the present embodiment, the heat radiating portion 11 is located above the heat absorbing portion 7. Therefore, for example, the refrigerant L3 that has been cooled and has a relatively high density is located above the boundary between the second flow passage 13 and the heat absorbing portion 7 more. As a result, the pressure difference due to gravity between the heat absorbing portion 7 and the second flow path 13 is expanded. As a result, natural circulation can be more reliably generated, or the flow rate of natural circulation can be increased.

  Further, in the present embodiment, the refrigerant L3 has a boiling point of 30 ° C. or more and 60 ° C. or less. Therefore, for example, the fluid L1 to be cooled can be cooled even if the temperature is slightly higher than the normal temperature (for example, 20 ° C. ± 15 ° C.) (in other words, the temperature is relatively low as the object to be cooled). Further, for example, it is easy to dissipate the refrigerant L3 at normal temperature. As a result, for example, the relatively low temperature cooling target fluid L1 can be cooled without using power.

Second Embodiment
FIG. 2 is a schematic view showing a schematic configuration of a cooling system 201 according to the second embodiment.

  In the description of the present embodiment, the same configuration as the configuration of the first embodiment is denoted by the same reference numeral as that of the first embodiment, and the description may be omitted. . Even when a code corresponding to (similar to) the configuration of the first embodiment is given a code different from the code attached to the configuration of the first embodiment, the first embodiment will be applied to matters that are not specifically stated. It may be the same as the configuration of the form.

  Similar to the cooling system 1 of the first embodiment, the cooling system 201 has a circulation flow path 203 and a bubble reservoir 5 branched upward from the first flow path 209 of the circulation flow path 203. However, the cooling system 201 is basically different from the cooling system 1 of the first embodiment in three points. One is the height of the bubble reservoir 5 and the heat sink 11 with respect to the heat absorber 7. The other is the cross-sectional area of the second channel. The remaining one is the shape of the second flow path (tank portion 213a). Specifically, it is as follows.

  In the cooling system 201, the heights of the air bubble reservoir 5 and the heat absorbing portion 7 of the heat radiating portion 11 are increased as compared with the cooling system 1 of the first embodiment. In another viewpoint, the front stage portion 209a and the second flow path 213 of the first flow path 209 are vertically longer than the front stage portion 9a and the second flow path 13 of the first embodiment. The opening 203a and the rear part 209b are the same as the opening 3a and the rear part 9b of the first embodiment.

  The inventors of the present application have found that the flow rate in the circulation flow path 203 can be increased by increasing the heights of the air bubble reservoir 5 and the heat sink 11 from the heat absorbing part 7. The reason is that, for example, the amount of the refrigerant L3 which is cooled by the heat radiating portion 11 and whose density is relatively increased is located on the heat absorbing portion 7 in a large amount, and the fall power can be used (the heat absorbing portion 7 and The possibility of expanding the pressure difference due to gravity with the second flow channel 213). In addition, it is mentioned that the distance by which the bubble B lifts up the first flow passage 209 is increased, and in turn, the urging action of the flow by the buoyancy of the bubble B is increased.

  As the natural circulation flow rate can be increased, for example, the cooling capacity of the cooling system 1 can be mentioned. From another point of view, the temperature of the fluid L1 to be cooled can be adjusted by adjusting the heights of the air bubble reservoir 5 and the heat sink 11 from the heat absorber 7. From this point of view, the heights of the bubble reservoir 5 and the heat dissipation portion 11 may not necessarily be increased. The same applies to the other two differences between the first embodiment and the second embodiment.

  Further, compared with the second flow path 13 of the cooling system 1 of the first embodiment, the second flow path 213 of the cooling system 201 does not include the cross-sectional area (even if the tank portion 213a described later is taken into consideration). The same applies in the following paragraph). Moreover, in another viewpoint, the cross-sectional area of the second flow channel 213 is made larger than that of the first flow channel 209. More specifically, for example, the average value of the cross sectional area of the second flow channel 213 (the value obtained by integrating the cross sectional area in the length direction of the flow channel and dividing it by the length of the flow channel) Greater than the average value of the cross-sectional area of Also, for example, in 80% or more of the length of the second flow channel 213, the cross-sectional area at any position is larger than the maximum diameter of the first flow channel 209. The degree of the difference in cross-sectional area between the first flow passage 209 and the second flow passage 213 may be set as appropriate.

  The inventors of the present application have found that the flow rate in the circulation channel 203 can be increased by thus increasing the cross-sectional area of the second channel 213. The reason is not always clear. However, for example, as the mass of the refrigerant L3 after being cooled by the heat radiating portion 11 increases, the proportion of the refrigerant L3 having a relatively high density in the circulation flow path 203 becomes large, and the refrigerant having a relatively high density It is considered that L3 makes it easy to push out the refrigerant L3 having a relatively low density.

  Further, while the second flow passage 13 of the first embodiment extends with a substantially constant diameter, the cross-sectional area of the second flow passage 213 of the cooling system 201 is locally increased halfway in the middle, A tank portion 213a is formed. Also by providing such a tank part 213a, the effect by enlarging the cross-sectional area of the 2nd flow path 213 mentioned above can be acquired.

  Furthermore, in the case where the tank portion 213a is provided, it is not necessary to increase the overall cross-sectional area of the second flow passage 213. As a result, for example, the degree of freedom in the arrangement of the second flow channels 213 can be improved. In addition, for example, the degree of freedom in selecting the members constituting the second flow channel 213 is improved. Further, for example, in the case where a valve for controlling the flow of the refrigerant L3 is provided in the second flow path 213, attachment of the valve is facilitated. Further, for example, even when the arrangement of the heat absorbing portion 7 and the heat radiating portion 11 is restricted and the length of the second flow channel 213 can not be secured, the volume of the second flow channel 213 can be increased.

<Example of usage of cooling system>
The cooling system 1 or 201 (hereinafter, for convenience, reference will only be made to the code of the cooling system 1) may be used for various applications.

  For example, the cooling system 1 may be used to cool oil generating power (hydraulic pressure) in a hydraulic device such as a hydraulic cylinder. In other words, the fluid to be cooled L1 may be oil. In this case, for example, oil as the fluid to be cooled L1 flows from the hydraulic device into the cooling container 15, is cooled by the cooling system 1, and is returned to the hydraulic device.

  Also, for example, the cooling system 1 may be used to cool the refrigerant of another cooling system. For example, in an air conditioner that cools indoor air, compressed refrigerant may be supplied to the cooling container 15 and cooled by the cooling system 1.

  The technology according to the present disclosure is not limited to the above embodiments, and may be implemented in various aspects.

  The object to be cooled is not limited to the fluid. For example, the object to be cooled may be a solid that is in contact with the heat absorbing portion. For example, a semiconductor device as a cooling target may be in contact with the heat absorbing portion. In the case where the object to be cooled is a fluid, the heat absorption part may not be configured to be immersed in the fluid to be cooled. For example, the heat absorption portion may be configured to be close to or in contact with the flow path through which the fluid to be cooled flows.

  A so-called relief valve may be provided in the bubble reservoir. The relief valve is opened, for example, only while the pressure in the bubble reservoir exceeds a predetermined pressure, and exhausts the gas in the bubble reservoir to the outside. Thus, the pressure in the bubble reservoir is limited to the predetermined pressure or less. Note that, although the air bubble reservoir portion constitutes a sealed space which is branched upward from the circulation flow channel in this way, it is not necessary to always keep the sealed space. Also, the bubble reservoir may be capable of changing its volume by, for example, movement of a piston or deformation of a puddle.

  The heat dissipating part may be of various types as described in the description of the embodiment, and is not limited to the type to be immersed in the boiling coolant. For example, air cooling may be performed by providing a plurality of fins on the outside of the heat dissipation unit.

  DESCRIPTION OF SYMBOLS 1 ... Cooling system, 3 ... Circulation flow path, 5 ... Bubble accumulation part, 7 ... Heat absorption part, 9 ... 1st flow path, 11 ... Heat release part 11, 13 ... 2nd flow path.

Claims (6)

A circulation channel through which the refrigerant circulates,
A heat sink, which absorbs heat from the external cooling object,
A first flow path including a portion extending upward from the heat absorption portion;
A circulation which is connected to the side opposite to the heat absorption portion of the first flow path and which radiates heat to the outside, and a second flow path extending from the heat release portion to the heat absorption portion in this order With the flow path,
A bubble accumulation portion constituting an enclosed space which branches upward from the first flow path;
Has a cooling system. The cooling system according to claim 1, wherein the bubble accumulation portion branches from the highest position of the circulation flow path. The cooling system according to claim 1, wherein the heat radiation unit is located above the heat absorption unit. The cooling system according to any one of claims 1 to 3, wherein an average value of cross-sectional areas of the second flow paths is larger than an average value of cross-sectional areas of the first flow paths. The cooling system according to any one of claims 1 to 4, wherein a cross-sectional area of the second flow path is locally increased halfway to have a tank portion. The cooling system according to any one of claims 1 to 5, wherein the refrigerant has a boiling point of 30 ° C to 60 ° C.

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