JP2010236792A - Ebullient cooling device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an ebullient cooling device properly forming the flow of refrigerant vapor in a container. <P>SOLUTION: In this ebullient cooling device 10 including a refrigerant storing section 12 for storing a liquid refrigerant receiving heat of a heating element inside, and a condensing section 15 connected to the refrigerant storing section 12 and condensing the evaporated refrigerant vapor, a hollow plate-like condensation pipe 17 circulating cooling fluid, is disposed in the condensing section 15, the condensation pipe 17 includes a condensing face kept into contact with the refrigerant vapor of the condensing section 15, an upstream end section as an inlet side of the refrigerant vapor, and a downstream end section as an outlet side of the refrigerant vapor, the condensing face is disposed in an inclined state to the flowing direction of the refrigerant vapor toward the direction different from the condensation pipe 17 just before introduced to the condensation pipe 17 in the condensing section 15, and the upstream end section is positioned upstream in the flowing direction of the refrigerant vapor just before introduced to the condensation pipe 17 in the condensing section 15, with respect to the downstream end section. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a boiling cooling device that cools a semiconductor element and a heating element such as a power module including the semiconductor element.

As a conventional boiling cooling device, for example, a cooling device for an electronic device disclosed in Patent Document 1 is known.
In this type of apparatus, a lower part in a sealed container is used as a refrigerant storage part, and a condenser for exchanging heat with the outside is provided in the upper part of the container.
A circuit board to which the electronic element is attached is disposed in the reservoir so as to be cooled in the refrigerant in the reservoir.
A reservoir for collecting the refrigerant dropped from the condenser is provided below the condenser and above the reservoir.
A return pipe for returning the refrigerant to the reservoir is provided at the bottom of the reservoir.

According to this type of apparatus, when the electronic element generates heat by energization, the refrigerant takes heat from the generated electronic element and cools it.
When the refrigerant boils due to heat taken from the electronic element, vapor bubbles are generated in the refrigerant.
The vapor moves to a space above the liquid level of the refrigerant, and heat is taken away by the condenser and returns to the liquid phase by condensation.
The refrigerant that has returned to the liquid phase is dropped into the reservoir and collected.

JP-A-2-129999

  However, in the prior art, although the refrigerant vapor moves to the condenser based on the upward flow of the refrigerant vapor evaporating from the liquid level in the container, it is mentioned that an appropriate refrigerant vapor flow is formed in the container. It has not been.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide a boiling cooling device capable of forming an appropriate flow of refrigerant vapor in a container.

  In order to solve the above problems, the present invention includes a refrigerant reservoir that stores therein a liquid refrigerant that receives heat from a heating element, a condenser that is connected to the refrigerant reservoir and condenses evaporated refrigerant vapor, A condensing pipe having a hollow plate that circulates a cooling fluid therein, the condensing pipe having a condensing surface in contact with the refrigerant vapor of the condensing part, and a refrigerant vapor An upstream end that is the inlet side of the refrigerant and a downstream end that is the outlet side of the refrigerant vapor, and the condensing surface is in a flow direction of the refrigerant vapor immediately before introduction into the condensation pipe in the condenser. The upstream end portion is positioned more upstream than the downstream end portion in the flow direction of the refrigerant vapor immediately before being introduced into the condensing pipe in the condensing portion. And

According to the present invention, the heating element is cooled by the liquid refrigerant in the refrigerant reservoir.
The liquid refrigerant in the refrigerant reservoir is boiled by heat received from the heating element, and refrigerant vapor is generated as bubbles in the liquid refrigerant.
The refrigerant vapor is discharged to the condensing part, and the refrigerant vapor discharged to the condensing part forms a flow in a different direction from the hollow plate-like condensing pipe.
Since the condensing surface of the condensing tube is inclined with respect to the flow direction of the refrigerant vapor immediately before introduction into the condensing tube, the refrigerant vapor can easily pass from the upstream end to the downstream end along the condensing surface. .
As a result, the refrigerant vapor can smoothly pass through the condensing surface, form an appropriate refrigerant vapor flow with respect to the condenser pipe that condenses the refrigerant vapor, and improve the refrigerant vapor condensation capacity of the boiling cooling device than before. Can do.
When there are a plurality of condensing tubes, the condensation surface of at least some of the condensing tubes should be inclined with respect to the flow direction of the refrigerant vapor just before introduction into the condensing tubes, It is assumed that the condensing surfaces of all the condensing tubes do not have to be inclined with respect to the flow direction of the refrigerant vapor immediately before introduction into the condensing tubes.

  In the boiling cooling device according to the present invention, the condensing surface may be arranged so that the refrigerant vapor in contact with the condensing surface flows from the upper side to the lower side along the condensing surface.

In this case, the liquid-phase refrigerant condensed on the condensing surface is directed from above to below along the condensing surface by its own weight.
Since the refrigerant vapor in contact with the condensing surface travels from the upper side to the lower side along the condensing surface, the downward movement of the refrigerant condensed on the condensing surface can be promoted.

  Further, the present invention provides the above-described boiling cooling apparatus, wherein the condensing unit is partitioned into an introduction passage and a condensation passage, and a passage forming plate that guides refrigerant vapor from the introduction passage to the condensation passage is provided in the condensation unit. The condensation tube may be disposed in the condensation passage.

In this case, the inside of the condensing part is divided into an introduction passage and a condensation passage by a passage forming plate.
Since the refrigerant vapor in the condensing part is guided from the introduction passage to the condensation passage, the flow of the refrigerant vapor immediately before introduction into the condensation tube that is directed in a different direction from the condensation tube and is inclined with respect to the condensation surface of the condensation tube Can be formed.

  In the boiling cooling apparatus according to the present invention, a plurality of the condensing tubes may be provided in parallel.

  In this case, the condensing efficiency can be improved by providing a plurality of condensing pipes in parallel in the condensing part.

  In the boiling cooling device according to the present invention, the gap between the condensation surfaces of the condensing tubes adjacent to each other may be set to a constant distance from the upstream end portion to the downstream end portion of the condensing tube. .

  In this case, the flow directions of the vapor refrigerant passing through the gaps between the condensation surfaces adjacent to each other can be the same direction.

  In the boiling cooling device according to the present invention, the liquid surface side in the gap between the condensing surfaces of the condensing tubes adjacent to each other may be expanded.

In this case, it is possible to prevent a bridge (liquid bridge) in which the condensed liquid-phase refrigerant bridges between the condensation pipes on the liquid surface side in the gap between the condensation surfaces of the adjacent condensation pipes. it can.
When the refrigerant vapor passing through the gap of the condenser tube is directed from the upstream end to the downstream end, if the liquid surface side of the gap is widened, the bridge on the downstream end side that is the liquid surface side (liquid bridge) Can be prevented.

  Further, the present invention provides the above-described boiling cooling apparatus, wherein the condensing unit includes a condensing unit housing, and the condensing unit housing forms an inclined ceiling wall that forms a flow of the refrigerant vapor immediately before being introduced into the condensing pipe. May be provided.

In this case, the inclined ceiling wall of the condensing unit housing forms a flow of refrigerant vapor that is inclined with respect to the condensing surface of the condensing tube.
Even if the condensing tube is arranged so that the condensing surface coincides with the vertical direction, the condensing surface of the condensing tube can be inclined with respect to the flow of the refrigerant vapor.

  In the boiling cooling apparatus according to the present invention, heights of at least one of the upstream end portion and the downstream end portion of the condensing pipes adjacent to each other may be different from each other.

  In this case, the range where the condensing surface of the condensing tube faces the condensing surface of another condensing tube is reduced, and the condensed liquid phase refrigerant condenses the bridge (liquid bridge) that bridges between the condensing tube and the condensing tube. At least one of the upstream end and the downstream end of the tube can be prevented.

  ADVANTAGE OF THE INVENTION According to this invention, the boiling cooling device which can form the flow of a more suitable refrigerant | coolant vapor | steam with respect to the condenser in a container can be provided.

It is a section front view of the boiling cooling device concerning a 1st embodiment of the present invention. It is a side view of the boiling cooling device which concerns on the 1st Embodiment of this invention. It is a principal part expanded sectional view of the boiling cooling device which concerns on the 1st Embodiment of this invention. It is a principal part expanded sectional view of the boiling cooling device which concerns on the 2nd Embodiment of this invention. It is a principal part expanded sectional view of the boiling cooling device which concerns on the 3rd Embodiment of this invention. It is a principal part expanded sectional view of the boiling cooling device which concerns on the 4th Embodiment of this invention. It is a principal part expanded sectional view of the boiling cooling device which concerns on the 5th Embodiment of this invention. It is a principal part expanded sectional view of the boiling cooling device which concerns on the 6th Embodiment of this invention.

(First embodiment)
Hereinafter, the boiling cooling apparatus according to the first embodiment will be described with reference to FIGS.
As shown in FIG. 1 and FIG. 2, the boiling cooling device 10 includes a refrigerant reservoir 12 that stores a liquid refrigerant (hereinafter referred to as “liquid refrigerant”) R, and an evaporated refrigerant (hereinafter referred to as “refrigerant vapor”). And a condensing unit 15 for condensing.

The refrigerant reservoir 12 includes a metallic reservoir housing 13 that has a rectangular parallelepiped shape.
The reservoir housing 13 includes a pair of heat receiving walls 13A, a pair of side walls 13B formed between side end portions of the heat receiving walls 13A, and a bottom wall 13C.
In this embodiment, three heating elements 11 are respectively attached to the outer surface of the heat receiving wall 13A (in FIG. 2, only the heating element 11 fixed to the outer surface of one heat receiving wall 13A is shown).
The heat receiving wall 13 </ b> A has a heat transfer surface that transmits the heat of the heating element 11 to the liquid refrigerant R in the reservoir housing 13.
The heating element 11 is an electronic circuit unit such as a power module having a switching element such as an IGBT.

As shown in FIG. 1, the condensing unit 15 is connected to the refrigerant storage unit 12.
The condensing unit 15 includes a metallic condensing unit housing 16 having a rectangular parallelepiped shape.
The condensing unit housing 18 has a space part that is expanded in the horizontal direction more than the space part in the refrigerant reservoir 12.
The condensing unit casing 16 is connected to the heat receiving wall 13A, and extends horizontally from the horizontal wall 16A, the vertical wall 16B extending upward from the end of the horizontal wall 16A, and the storage unit casing 13 A side wall 16C that forms the same plane as the side wall 13B and a ceiling wall 16D that forms a ceiling are provided.

As shown in FIGS. 1 and 2, a pair of passage forming plates 14 that divide the inside of the refrigerant reservoir 12 and the condenser 15 into a plurality of passages are provided.
The passage forming plate 14 is formed of a bent plate material, and the side ends of the passage forming plate 14 are fixed to the side walls 13B and 16C.
The passage forming plate 14 has a storage portion-side vertical portion 14A, most of which is located in the storage portion housing 13, and an inclination extending from the storage portion-side vertical portion 14A toward the vertical wall 16B of the condensing portion housing 16. 14B and the condensing part side vertical part 14C extended upwards from the inclination part 14B.

A passage formed between the storage portion side vertical portion 14A and the heat receiving wall 13A is a first refrigerant passage T1.
In this embodiment, by providing the pair of passage forming plates 14, a pair of first refrigerant passages T <b> 1 is formed in the reservoir housing 13.
Further, a second refrigerant passage T2 is formed between the pair of storage portion side vertical portions 14A.
A third refrigerant passage as an introduction passage between a part of the condensing unit casing 16 (horizontal wall 16A and vertical wall 16B) and a part of the passage forming plate 14 (inclined part 14B and condensing unit side vertical part 14C). T3 is formed.
A fourth refrigerant passage T4 as a condensing passage is formed between a part of the pair of passage forming plates 14 (the inclined portion 14B and the condensing portion side vertical portion 14C).
Accordingly, the passage forming plate 14 corresponds to passage forming means for forming the first refrigerant passage T1 to the fourth refrigerant passage T4.

In this embodiment, the liquid level of the liquid refrigerant R is located slightly above the horizontal wall 16 </ b> A of the condensing unit housing 16.
In this state, the first refrigerant passage T1 and the second refrigerant passage T2 have the liquid refrigerant R, and the third refrigerant passage T3 and the fourth refrigerant passage T4 have the refrigerant vapor.
The refrigerant vapor evaporating from the liquid surface passes from the third refrigerant passage T3 to the fourth refrigerant passage T4. In the third refrigerant passage T3, the inclined portion 14B and the condensing portion side vertical portion 14C guide the refrigerant vapor and move upward. A flow of refrigerant vapor is generated.
The refrigerant vapor introduced from the third refrigerant passage T3 into the fourth refrigerant passage T4 becomes a horizontal flow along the ceiling wall 16D as a wall portion.

The lower end of the passage forming plate 14 does not reach the bottom wall 13C of the reservoir housing 13, and a gap is formed between the bottom wall 13C and the bottom wall 13C.
Therefore, the pair of first refrigerant passage T1 and second refrigerant passage T2 communicate with each other through a gap below the passage forming plate 14.
A gap is formed between the upper end of the passage forming plate 14 and the ceiling wall 16D.
The pair of third refrigerant passage T3 and fourth refrigerant passage T4 communicate with each other through a gap above the passage forming plate.
The fourth refrigerant passage T4 is located above the second refrigerant passage T2.

In the condensing unit casing 16, ten hollow plate-shaped condensing tubes 17 are arranged in parallel.
As shown in FIG. 2, the condensing pipe 17 penetrates the condensing unit housing 16 and is fixed to the side wall 16C by welding.
A condenser pipe 17 corresponding to a condenser is connected to a cooling water pipe (not shown) including a pump and a heat radiating means. Cooling water C as a cooling fluid is supplied to the condenser pipe 17 through the cooling pipe, and condensed. In the pipe 17, the cooling water C flows from one to the other.
The cooling water C in the condensing pipe 17 condenses the refrigerant vapor by heat exchange with the refrigerant vapor in the condenser 15.

As shown in FIG. 3, the condensing tube 17 is formed by a pair of flat walls 17A facing each other and a connecting wall 17B having an arcuate cross section that connects the edges of the flat wall 17A.
The surface of the flat wall 17A constitutes the condensing surface of the condensing tube 17.
In this embodiment, the boiling cooling device 10 is installed in a vertical state, and the ceiling wall 16D is horizontal.
Since the surface of the flat wall 17A of each condensing tube 17 is not perpendicular to the ceiling wall 16D, each condensing tube 17 is disposed in the condensing portion 15 in a state inclined with respect to the vertical direction.
Furthermore, the condensing pipe 17 is inclined so as to fall in a state in which the connection wall 17B above the condensing pipe 17 is directed to the outside in the condensing portion 15.
Further, the flat wall 17A is inclined with respect to the flow direction of the refrigerant vapor in the fourth refrigerant passage T4 (indicated by the arrow F in FIG. 3), and the flow direction of the refrigerant vapor in the fourth refrigerant passage T4 and the flat wall 17A The inclination angle S is an acute angle.
The flow of the refrigerant vapor indicated by the arrow F in FIG. 3 is the flow of the refrigerant vapor after being guided from the third refrigerant passage T3 to the fourth refrigerant passage T4 and immediately before being introduced into the condenser tube 17.
Here, “immediately before introduction into the condensation pipe 17” refers to a period after the refrigerant vapor is guided to the fourth refrigerant passage T4 and during which no refrigerant vapor is introduced into the condensation pipe 17.
Furthermore, the direction of the “flow of refrigerant vapor immediately before introduction into the condenser tube 17” herein is limited to the direction indicated by the arrow F in FIG.
Further, the flow of the refrigerant vapor indicated by the arrow F in FIG. 3 is a flow in a direction parallel to the ceiling wall 16D.
Furthermore, the flow of the refrigerant vapor in an inclined state with respect to the flat wall 17 </ b> A is a horizontal flow of the refrigerant vapor from the outside to the inside in the condensing unit 15.
Since the flat wall 17 </ b> A is inclined with respect to the flow direction of the refrigerant vapor, the refrigerant vapor easily passes through the gap X of the condensation pipe 17.
Therefore, the upper connection wall 17B of the condensing pipe 17 corresponds to the upstream end of the condensing pipe 17 on the refrigerant vapor introduction side, and the lower connection wall 17B is provided on the downstream end of the refrigerant vapor outlet side. Equivalent to.
The upper connection wall 17B is located outside the lower connection wall 17B in the condenser 15.
More specifically, the upper connection wall 17B of each condensing pipe 17 is located on the upstream side in the flow direction of the refrigerant vapor indicated by the arrow F in FIG. 3, and the lower connection wall 17B is downstream in the flow direction of the refrigerant vapor. Located in.
That is, the upstream end of the condensing pipe 17 is positioned upstream of the refrigerant vapor flow direction just before introduction into the condensing pipe 17 in the condensing section 15.

The gap X between the flat walls 17A of the adjacent condensation tubes 17 is set to a constant distance from the upstream end portion to the downstream end portion of the condensation tube 17, and the flat walls 17A of the adjacent condensation tubes 17 are mutually connected. Parallel.
The gap X between the flat walls 17 </ b> A of the adjacent condensation tubes 17 is set at a distance that can prevent a bridge (liquid bridge) in which the condensed liquid-phase refrigerant bridges between the condensation tubes 17. ing.
Incidentally, the distance between two objects that does not bridge (liquid bridging) is determined by the Laplace length equation using constants determined by the surface tension, density, refrigerant vapor density, gravity acceleration, and liquid refrigerant R type of the liquid refrigerant R. (For example, refer to Japanese Unexamined Patent Publication No. 2000-74536.)

Next, the operation of the boiling cooling device 10 will be described.
When the heating element 11 generates heat, the liquid refrigerant R in the refrigerant reservoir 12 receives heat from the heating element 11 through the heat transfer surface of the heat receiving wall 13A and boils.
The refrigerant vapor generated by the boiling of the liquid refrigerant R is generated in the liquid refrigerant R as bubbles B, and the bubbles B rise in the first refrigerant passage T1.
Refrigerant vapor is discharged to the condensing unit 15 from the bubbles B that have risen in the first refrigerant passage T1 and have reached the liquid level.

As the bubbles B rise in the first refrigerant passage T1, a flow from the lower side to the upper side of the liquid refrigerant R occurs in the first refrigerant passage T1.
As the liquid refrigerant R flows from the lower side to the upper side in the first refrigerant passage T1, the flow of the liquid refrigerant R from the second refrigerant passage T2 toward the first refrigerant passage T1 occurs at the lower end portion of the passage forming plate 14. .

On the other hand, the refrigerant vapor discharged from the liquid surface generates a flow along the vertical wall 16B of the condensing unit housing 16, the inclined portion 14B of the passage forming plate 14, and the condensing unit side vertical portion 14C.
In the third refrigerant passage T3, an upward flow of refrigerant vapor is formed.
The refrigerant vapor that has passed through the third refrigerant passage T3 is introduced between the ceiling wall 16D and the passage forming plate 14 into the fourth refrigerant passage T4.
When the refrigerant vapor is introduced from the third refrigerant passage T3 into the fourth refrigerant passage T4, the refrigerant vapor flows along the ceiling wall 16D.
The third refrigerant passage T3 is formed outside the fourth refrigerant passage T4 in the condensing unit 15, and the refrigerant vapor guided from the third refrigerant passage T3 to the fourth refrigerant passage T4 is outside the condensing unit 15. It flows inward from the inside.
In the fourth refrigerant passage T4, a refrigerant vapor flow (indicated by an arrow F in FIG. 3) immediately before introduction into the condensing pipe 17 is formed.

The refrigerant vapor in the fourth refrigerant passage T4 flows along the flat wall 17A of each condensing pipe 17 and also moves toward the vicinity of the center of the condensing part 15 and merges with the horizontal refrigerant vapor flow from the other condensing pipe 17 side. And flow downward.
Since the surface of the flat wall 17A is inclined at an inclination angle S with respect to the flow direction of the refrigerant vapor in the fourth refrigerant passage T4, compared to the case where the flat wall 17A is arranged to be vertical, The refrigerant vapor is easily introduced smoothly into the gap X between the condensation pipe 17 and the condensation pipe 17.

On the surface of the flat wall 17 </ b> A, heat exchange between the refrigerant vapor and the cooling water C flowing in the condenser tube 17 is performed.
The refrigerant vapor is condensed and converted into a liquid phase by heat exchange with the cooling water C in the condenser pipe 17.
When the condensation of the refrigerant vapor is promoted on the surface of the flat wall 17A, the gap X of the condensation pipe 17 becomes a low pressure in the fourth refrigerant passage T4 as compared with the region where the refrigerant vapor excluding the gap X flows.
Introduction of refrigerant vapor into the gap X of the condensing pipe 17 is promoted by reducing the pressure of the gap of the condensing pipe 17.

The liquid phase refrigerant moves downward along the flat wall 17A due to its own weight accompanying the growth of droplets due to condensation.
At this time, since the refrigerant vapor that is not condensed flows from the upper side to the lower side along the flat wall 17A, the refrigerant vapor that flows along the flat wall 17A promotes the downward movement of the refrigerant condensed on the flat wall 17A.
As the flat wall 17A moves toward the downstream end, the condensed refrigerant droplet grows larger.
The condensed refrigerant is dropped from the downstream end of the condensing pipe 17 and collected in the second refrigerant passage T2.

This embodiment has the following effects.
(1) The refrigerant vapor generated as bubbles B in the first refrigerant passage T1 and released to the condensing unit 15 is introduced into the condenser pipe 17 after being guided from the third refrigerant passage T3 to the fourth refrigerant passage T4. The immediately preceding refrigerant vapor flow is formed. Since the surface of the flat wall 17A of the condensing tube 17 is inclined with respect to the flow direction (horizontal direction) of the refrigerant vapor immediately before being introduced into the condensing tube 17, the flow direction of the refrigerant vapor is smoothly conducted in the condensing unit 15. The refrigerant vapor can easily be changed along the flat wall 17A. As a result, the refrigerant vapor can smoothly pass through the surface of the flat wall 17A to form an appropriate refrigerant vapor flow with respect to the condensation pipe 17 that condenses the refrigerant vapor. Can also be improved. Incidentally, when the flat wall 17A of the condensing tube 17 is not inclined with respect to the flow direction (horizontal direction) of the refrigerant vapor immediately before being introduced into the condensing tube 17, the refrigerant vapor smoothly passes through the gap X of the condensing tube 17. Can not be. If the refrigerant vapor cannot pass smoothly into the gap X, the required condensing capacity cannot be obtained. Further, in this embodiment, since the condensing tube 17 having a large surface area as a tube is used, heat exchange with the refrigerant vapor is promoted by increasing the surface area in contact with the refrigerant vapor, thereby improving the condensation capacity. it can.
(2) The liquid-phase refrigerant condensed in the flat wall 17A of the condensing tube 17 moves from the upper side to the lower side along the flat wall 17A by its own weight. The refrigerant vapor passing through the periphery of the flat wall 17A travels from above to below along the flat wall 17A. Therefore, it is possible to promote the downward movement of the refrigerant condensed on the flat wall 17A. That is, the direction in which the refrigerant vapor flows in the gap X of the condensing tube 17 and the direction in which the liquid-phase refrigerant flows in the flat wall 17A are the same, and are unlikely to interfere with each other's flow.

(3) Since the gap X between the flat walls 17A of the condensing pipes 17 adjacent to each other is set at a constant distance from the upstream end to the downstream end of the condensing pipe 17, the gaps X have the same conditions as each other. (The distance of the gap X and the inclination angle). For this reason, the direction of the flow of the vapor refrigerant passing through the gap X between the flat walls 17A of the condensing pipes 17 adjacent to each other can be made the same direction.
(4) The gap X between the flat walls 17 </ b> A of adjacent condensing tubes 17 is set at a distance at which the condensed liquid phase refrigerant does not form a bridge (liquid bridge) that bridges between the condensing tubes 17. ing. As a result, bridges (liquid bridges) in the condensation pipe 17 can be prevented, and a decrease in condensation efficiency due to the occurrence of bridges (liquid bridges) can be prevented.

(Second Embodiment)
Next, the boiling cooling device according to the second embodiment will be described.
The boiling cooling device according to the second embodiment is configured such that the inclination angle of the flat wall in the condensing tube is different for each condensing tube.
In the second embodiment, the arrangement state of the condensing tube is only different from that of the first embodiment. Therefore, for each element excluding the condensing tube, the description of the first embodiment is used and the description thereof is omitted. The code used in the first embodiment is used in common.

FIG. 4 is a diagram showing a main part of the condensing unit 15 in the boiling cooling device, and shows one of the third refrigerant passage T3 and the fourth refrigerant passage T4 that are partitioned and formed on the one vertical wall 16B side in the condensing unit 15. And five condensing pipes 117 arranged in parallel in the condensing unit 15.
Therefore, although not shown in FIG. 4, another third refrigerant passage T3 and five condensing pipes 117 exist on the other vertical wall 16B side in the condensing unit 15.
The condensing pipe 117 includes a pair of flat walls 117A facing each other and a connecting wall 117B having an arcuate cross section that connects the edges of the flat wall 117A.

As shown in FIG. 4, five condensing pipes 117 are arranged in the fourth refrigerant passage T <b> 4 on the one vertical wall 16 </ b> B side in the condensing unit 15.
In this embodiment, among the five condensing tubes 117, the condensing tube 117 closest to the passage forming plate 14 is arranged vertically such that the flat wall 117A coincides with the vertical direction.
That is, the flat wall 117A of the condensing pipe 117 closest to the passage forming plate 14 is perpendicular to the ceiling wall 16D.
Each condensing tube 117 is arranged so that the inclination angle of the flat wall 117A of the condensing tube 117 with respect to the vertical direction increases as the installation position of the condensing tube 117 becomes farther from the passage forming plate 14.
Therefore, the gap X between the flat walls 117A of the adjacent condensing pipes 117 is expanded from the upstream end toward the downstream end, and the liquid surface side in the gap X between the flat walls 117A is expanded most. Yes.

The flow of refrigerant vapor after guidance from the third refrigerant passage T3 to the fourth refrigerant passage T4 (indicated by the arrow F in FIG. 4) is the flow of refrigerant vapor just before introduction into the condenser tube 117, and the passage forming plate 14 Except for the condensing pipe 117 closest to the flat wall 117A, the flat wall 117A is inclined.
Here, “immediately before introduction into the condensation pipe 117” refers to a period after the refrigerant vapor is guided to the fourth refrigerant passage T4 and during which no refrigerant vapor is introduced into the condensation pipe 117.
Furthermore, the direction of the “flow of refrigerant vapor immediately before introduction into the condenser tube 117” herein is limited to the direction indicated by the arrow F in FIG.
The flow of the refrigerant vapor indicated by the arrow F in FIG. 4 is a flow in a direction parallel to the ceiling wall 16D.
The upper connecting wall 117B of each condensing pipe 117 is located on the upstream side in the flow direction of the refrigerant vapor indicated by the arrow F in FIG. 4 except for the condensing pipe 117 closest to the passage forming plate 14, and the lower connecting wall 117B. Is located downstream in the flow direction of the refrigerant vapor.
That is, the upstream end of the condensing pipe 117 is located upstream of the downstream end of the condensing pipe 117 in the flow direction of the refrigerant vapor just before introduction into the condensing pipe 117 in the condensing section 15.
The flow of the refrigerant vapor in an inclined state with the flat wall 117A is in the horizontal direction, and goes from the outside in the condensing unit 15 to the center side.
In the arrangement of the condensing pipe 17 as in the first embodiment, as the flow of the refrigerant vapor moves toward the center of the condensing part 15, the resistance to the flow of the refrigerant vapor to the gap X increases. The closer to 14, the smaller the resistance to the refrigerant vapor flow into the gap X.
In this embodiment, by increasing the resistance to the flow of the refrigerant vapor that passes through the gap X close to the passage forming plate 14, the flow rate of the refrigerant vapor that passes through the gap X is made uniform, and the refrigerant vapor in each gap X is smooth. A flow is formed.
As shown in FIG. 4, when a plurality of condensing tubes 117 are arranged, even if the condensing tube 117 having a flat wall 117A perpendicular to the flow direction of the refrigerant vapor indicated by the arrow F exists, If at least one condensing pipe 117 having a flat wall 117A inclined with respect to the flow direction of the refrigerant vapor indicated by F is included, the flow of the refrigerant vapor is formed by at least the condensing pipe 117 having the inclined flat wall 117A. be able to.

According to this embodiment, there exists an effect equivalent to the effect (1), (2) of 1st Embodiment.
Further, since the gap distance on the downstream end side that is the liquid surface side of the gap X of the condensing tube 117 is set larger than the gap distance on the upstream end side, the liquid level of the gap X of the flat wall 117A. The side is widened, and on the downstream end side of the condensing tube 117, a liquid-phase refrigerant droplet that increases is prevented from bridging between the condensing tube 117 and the condensing tube 117. Can do.

(Third embodiment)
Next, a boiling cooling device according to a third embodiment will be described.
The boiling cooling device according to the third embodiment is configured so that the inclination angle of the flat wall in the condensing tube is different for each condensing tube.
In the third embodiment, the arrangement state of the condensing tube is only different from that of the first embodiment, and therefore the description of the first embodiment is omitted for each element excluding the condensing tube. The symbols used in the first embodiment are commonly used.

FIG. 5 is a view showing a main part of the condensing unit 15 in the boiling cooling device, and includes a third refrigerant passage T3 that is partitioned and formed in one side of the condensing unit 15, a part of the fourth refrigerant passage T4, and a condensing unit. 15 shows five condensing pipes 217 arranged in parallel on one side.
Therefore, although not shown in FIG. 5, another third refrigerant passage T <b> 3 and five condensing pipes 217 exist on the other side in the condensing unit 15.

Five condensing pipes 217 are arranged in the fourth refrigerant passage T4 in the condensing unit 15 in the boiling cooling apparatus shown in FIG.
The condensing pipe 217 includes a pair of flat walls 217A facing each other and a connecting wall 217B having an arcuate cross section that connects the edges of the flat wall 217A.
In this embodiment, among the five condensing tubes 217, the condensing tube 217 farthest from the passage forming plate 14 is arranged vertically so that the flat wall 217A coincides with the vertical direction.
Each condensing tube 217 is arranged so that the inclination angle of the flat wall 217A of the condensing tube 217 with respect to the vertical direction becomes larger as the installation position of the condensing tube 217 becomes closer to the passage forming plate 14.
For this reason, the gap X between the flat walls 217A of the adjacent condensing pipes 217 decreases from the upstream end toward the downstream end.
The downstream end side of the gap X between the flat walls 217A of the adjacent condensation pipes 217 prevents a bridge (liquid bridge) in which the condensed liquid-phase refrigerant bridges between the condensation pipe 217 and the condensation pipe 217. It is set by the distance that can be.
The condensing pipe 217 close to the passage forming plate 14 is arranged to be inclined with respect to the flow of the refrigerant vapor (indicated by the arrow F in FIG. 5), so that the vapor refrigerant can easily pass through the gap of the condensing pipe 217. Yes.
The flow of the refrigerant vapor indicated by the arrow F in FIG. 5 is the flow of the refrigerant vapor immediately before being introduced into the condensing tube 217, and is inclined with respect to the flat wall 217A except for the condensing tube 217 farthest from the passage forming plate 14.
Here, “immediately before introduction into the condensation pipe 217” refers to a period after the refrigerant vapor is guided to the fourth refrigerant passage T4 and during which no refrigerant vapor is introduced into the condensation pipe 217.
The flow of the refrigerant vapor in an inclined state with the flat wall 217A is in the horizontal direction, and is directed from the outside to the inside in the condensing unit 15.
Further, the flow of the refrigerant vapor indicated by the arrow F in FIG. 5 is a flow in a direction parallel to the ceiling wall 16D.
Furthermore, the direction of the “flow of refrigerant vapor immediately before introduction into the condenser tube 217” here is limited to the direction indicated by the arrow F in FIG.
The connection wall 217B above each condensing tube 217 is located on the upstream side in the flow direction of the refrigerant vapor indicated by arrow F in FIG. 5 except for the condensing tube 217 farthest from the passage forming plate 14, and the lower connecting wall 217B is It is located downstream in the flow direction of the refrigerant vapor.
That is, the upstream end of the condensing pipe 217 is positioned upstream of the refrigerant vapor flow direction just before introduction into the condensing pipe 217 in the condensing section 15.
As shown in FIG. 5, when a plurality of condensing tubes 217 are arranged, even if there is a condensing tube 217 having a flat wall 217A perpendicular to the flow direction of the refrigerant vapor indicated by the arrow F, the arrow If at least one condensing tube 217 having a flat wall 217A inclined with respect to the flow direction of the refrigerant vapor indicated by F is included, the flow of the refrigerant vapor is formed by at least the condensing tube 217 having the inclined flat wall 217A. be able to.

According to this embodiment, there exists an effect equivalent to the effect (1), (2) of 1st Embodiment.
Further, a bridge (liquid bridge) in which the liquid-phase refrigerant bridges between the condensation pipe 217 and the condensation pipe 217 on the downstream end side of the condensation pipe 217 can be prevented.
Further, since the gap X on the downstream end side in the condensing pipe 217 is reduced, the condensed refrigerant can be easily concentrated in the narrower second refrigerant passage T2 below the condensing pipe 217.

(Fourth embodiment)
Next, a boiling cooling device according to a fourth embodiment will be described.
In the boiling cooling device according to the fourth embodiment, the inclination angle of the flat wall in the condensing pipe is the same inclination angle in all the condensing pipes, but the height of the upstream end and the downstream end is the same for each condensing pipe. Configured differently.
Furthermore, the condensing unit housing includes a ceiling wall that is inclined corresponding to the position of the upstream end.
In the fourth embodiment, the configuration of the condensing unit housing and the arrangement state of the condensing tube are only different from those in the first embodiment, and therefore, for the common elements, the description of the first embodiment is cited. The description thereof is omitted, and the symbols used in the first embodiment are used in common.

FIG. 6 is a view showing a main part of the condensing unit 15 in the boiling cooling device, and includes a third refrigerant passage T3 that is partitioned and formed in one side of the condensing unit 15, a part of the fourth refrigerant passage T4, and a condensing unit. 15 shows five condensing pipes 317 arranged in parallel on one side of 15.
Accordingly, although not shown in FIG. 6, another third refrigerant passage T <b> 3 and five condensing pipes 317 exist on the other side in the condensing unit 15.
The condensing pipe 317 includes a pair of flat walls 317A facing each other and a connecting wall 317B having an arcuate cross section that connects the edges of the flat wall 317A.

The condensing unit 15 of the boiling cooling device shown in FIG.
The condensing unit casing 26 includes a horizontal wall 26A as a wall, a vertical wall 26B, a horizontal ceiling wall 26C, an inclined ceiling wall 26D, and side walls (not shown).
The horizontal wall 26A and the vertical wall 26B are the same as those in the first embodiment.
The horizontal ceiling wall 26 </ b> C is a wall extending in the horizontal direction from the upper end portion of the vertical wall 26 </ b> B and reaches near the upper end of the upper end portion of the passage forming plate 14.
The inclined ceiling wall 26D is connected to the horizontal ceiling wall 26C and is inclined downward.

In this embodiment, the third refrigerant passage T3 is partitioned by the inclined portion 14B, the condensing portion-side vertical portion 14C, the horizontal wall 26A, and the vertical wall 26B.
The fourth refrigerant passage T4 is partitioned by the inclined ceiling wall 26D, the inclined portion 14B of the passage forming plate 14, and the condensing portion side vertical portion 14C.
Due to the presence of the inclined ceiling wall 26D as the wall portion, the refrigerant vapor introduced from the third refrigerant passage T3 into the fourth refrigerant passage T4 forms a refrigerant vapor flow (indicated by an arrow F in FIG. 6) directed downward. To do.
The flow indicated by the arrow F in FIG. 6 is the flow of the refrigerant vapor just before being introduced into the condensing tube 317, and is inclined with the flat wall 317A.
Here, “immediately before introduction into the condensation pipe 317” refers to a period after the refrigerant vapor is guided to the fourth refrigerant passage T4 and during which no refrigerant vapor is introduced into the condensation pipe 317.
Furthermore, the direction of the “flow of refrigerant vapor immediately before introduction into the condenser tube 317” here is limited to the direction indicated by the arrow F in FIG.
In addition, the flow of the refrigerant vapor indicated by the arrow F in FIG. 6 is a flow in a direction parallel to the inclined ceiling wall 26D.
The flow of the refrigerant vapor in an inclined state with the flat wall 317A is directed from the outside to the inside in the condensing unit 15 along the inclined ceiling wall 26D.

Five condensing pipes 317 are arranged in the fourth refrigerant passage T4 in the condensing unit 15.
In this embodiment, the surface of the flat wall 317A of each condensing tube 317 is disposed in the condensing unit 15 in a state in which the surface is inclined with respect to the vertical direction.
Furthermore, the inclination angle S between the flow direction of the refrigerant vapor in the fourth refrigerant passage T4 and the flat wall 317A is an acute angle, and the refrigerant vapor easily passes through the gap X of the condensation pipe 317.
The gap X between the flat walls 317A of adjacent condensing pipes 317 is set to a constant distance from the upstream end to the downstream end.
That is, the flat walls 317A of the adjacent condenser tubes 317 are parallel to each other.
Furthermore, the upper connection wall 317B of each condensing pipe 317 is located on the upstream side in the flow direction of the refrigerant vapor indicated by the arrow F in FIG. 6, and the lower connection wall 317B is on the downstream side in the flow direction of the refrigerant vapor. Located in.
That is, the upstream end of the condensing tube 317 is located upstream of the downstream end of the condensing tube 317 in the flow direction of the refrigerant vapor just before introduction into the condensing tube 317 in the condensing unit 15.

In this embodiment, the height with respect to the liquid level of the liquid refrigerant R at the upstream end portion and the downstream end portion of the condensing pipes 317 adjacent to each other is different.
The distance between the upstream end of each condensing tube 317 and the inclined ceiling wall 26 </ b> D is equal. The further away from the passage forming plate 14, the lower the condensing tube 317 is with respect to the liquid surface of the liquid refrigerant R.

According to this embodiment, there exists an effect equivalent to the effect (1), (2) of 1st Embodiment.
The inclined ceiling wall 26D and the condensing pipe 317 can smoothly change the flow of the refrigerant vapor going upward, and thus the condensing capacity can be improved.
In this embodiment, the range in which the flat wall 317A of the condensing tube 317 faces the flat wall 317A of another condensing tube 317 is small.
That is, of the pair of flat walls 317A in the condensation pipe 317, a flat wall on the opposite side of the passage formation plate 14 side of another condensation pipe 317 is located near the downstream end of the flat wall 317A on the passage formation plate 14 side. 317A does not oppose.
Therefore, a bridge (liquid bridge) in which the condensed liquid-phase refrigerant bridges between the condensation pipe 317 and the condensation pipe 317 can be prevented at the downstream end side of the condensation pipe 317.

(Fifth embodiment)
Next, a boiling cooling device according to a fifth embodiment will be described.
In the boiling cooling device according to the fifth embodiment, the condensing tube is arranged at the same height in the condensing unit so that the flat wall in the condensing tube is vertical, and the condensing unit housing is inclined downward. It has a ceiling wall.
In the fifth embodiment, the configuration of the condensing unit housing and the arrangement state of the condensing pipes are only different from those in the first embodiment. Therefore, for the common elements, the description of the first embodiment is cited. The description thereof is omitted, and the symbols used in the first embodiment are used in common.
Moreover, since the condensation part housing | casing which concerns on 5th Embodiment is the structure substantially the same as the condensation part housing | casing 26 of 4th Embodiment, the code | symbol used in 4th Embodiment is used in common. .

FIG. 7 is a diagram showing a main part of the condensing unit 15 in the boiling cooling device, and includes a third refrigerant passage T3 that is partitioned and formed in one side of the condensing unit 15, a part of the fourth refrigerant passage T4, and a condensing unit. 15 shows five condensing pipes 417 arranged in parallel on one side.
Accordingly, although not shown in FIG. 7, another third refrigerant passage T <b> 3 and five condensing pipes 417 exist on the other side in the condensing unit 15.
The condensing pipe 417 includes a pair of flat walls 417A facing each other and a connection wall 417B having an arcuate cross section that connects the edges of the flat wall 417A.

The condensing unit 15 of the boiling cooling device shown in FIG.
The condensing unit casing 26 includes a horizontal wall 26A as a wall, a vertical wall 26B, a horizontal ceiling wall 26C, an inclined ceiling wall 26D, and side walls (not shown).
In this embodiment, the third refrigerant passage T3 is partitioned by the inclined portion 14B, the condensing portion-side vertical portion 14C, the horizontal wall 26A, and the vertical wall 26B.
The fourth refrigerant passage T4 is partitioned by the inclined ceiling wall 26D, the inclined portion 14B of the passage forming plate 14, and the condensing portion side vertical portion 14C.
Due to the presence of the inclined ceiling wall 26D, the refrigerant vapor introduced from the third refrigerant passage T3 to the fourth refrigerant passage T4 forms a flow of refrigerant vapor that goes obliquely downward.

Five condensing pipes 417 are arranged in the fourth refrigerant passage T4 in the condensing unit 15.
In this embodiment, it is arrange | positioned in the condensation part 15 in the state in which the surface of flat wall 417A of each condensation pipe | tube 417 becomes perpendicular | vertical.
The upper and lower connection walls 417B of the condensing pipe 417 are located on the same side in the condensing unit 15.
For this reason, the inclined ceiling wall 26 </ b> D of the condensing unit housing 26 forms a refrigerant vapor flow (indicated by an arrow F in FIG. 7) that is inclined with respect to the surface of the flat wall 417 </ b> A of the condensing pipe 417.
The flow of the refrigerant vapor indicated by the arrow F in FIG. 7 is the flow of the refrigerant vapor immediately before being introduced into the condensing pipe 417, and is inclined with respect to the flat wall 417A.
Here, “immediately before introduction into the condensation pipe 417” refers to a period after the refrigerant vapor is guided to the fourth refrigerant passage T4 and during which no refrigerant vapor is introduced into the condensation pipe 417.
Furthermore, the direction of the “flow of refrigerant vapor immediately before introduction into the condenser tube 417” here is limited to the direction indicated by the arrow F in FIG.
Further, the flow of the refrigerant vapor indicated by the arrow F in FIG. 7 is a flow in a direction parallel to the inclined ceiling wall 26D.
The flow of the refrigerant vapor in an inclined state with the flat wall 417A is directed from the upper outer side to the lower inner side in the condensing unit 15 by the inclined ceiling wall 26D.
Since the refrigerant vapor in the fourth refrigerant passage T4 flows obliquely downward, the inclination angle S between the flow direction of the refrigerant vapor and the flat wall 417A is an acute angle, and the refrigerant vapor easily passes through the gap X of the condensation pipe 417. Yes.

The gap X between the flat walls 417A of adjacent condensing pipes 417 is set to a certain distance from the upstream end to the downstream end.
That is, the flat walls 417A of the adjacent condenser tubes 417 are parallel to each other.
In this embodiment, the height of each condensing pipe 417 is the same as each other, and therefore the distance between the upstream end of each condensing pipe 417 and the inclined ceiling wall 26 </ b> D differs for each condensing pipe 417.
More specifically, the upper connection wall 417B of each condensing pipe 417 is located on the upstream side in the flow direction of the refrigerant vapor indicated by the arrow F in FIG. 7, and the lower connection wall 417B is on the downstream side in the flow direction of the refrigerant vapor. Located in.
In other words, the upstream end of the condensing pipe 417 is positioned upstream of the downstream end of the condensing pipe 417 in the flow direction of the refrigerant vapor immediately before introduction into the condensing pipe 417 in the condensing section 15.

According to this embodiment, there exists an effect equivalent to the effect (1), (2) of 1st Embodiment.
The inclined ceiling wall 26D and the condensing pipe 417 can smoothly change the flow of the refrigerant vapor that goes upward, so that the condensing capacity can be improved.
Further, even when the condensing pipe 417 is not inclined, it is possible to realize a state in which the surface of the flat wall 417A that is the condensing surface of the condensing pipe 417 is inclined with respect to the flow direction of the refrigerant vapor.

(Sixth embodiment)
Next, a boiling cooling device according to a sixth embodiment will be described.
In the boiling cooling device according to the sixth embodiment, the condensing pipe is arranged in the fourth refrigerant passage so that the flat wall of the condensing pipe is inclined.
In the sixth embodiment, the arrangement state of the condensing tube is only different from that of the first embodiment. Therefore, for the common elements, the description of the first embodiment is used and the description thereof is omitted. The code used in the embodiment is commonly used.

The boiling cooling device shown in FIG. 8 includes a condensing unit casing 16 connected to the storage unit casing 13.
A pair of passage forming plates 34 are disposed inside the condensing unit housing 16 and the storage unit housing 13.
The passage forming plate 34 includes a storage portion side vertical portion 34A, which is mostly located in the storage portion housing 13, an inclined portion 34B extending from the storage portion side vertical portion 34A toward the vertical wall 16B, and an inclined portion. A condensing portion side vertical portion 34C extending upward from 34B is provided.

In this embodiment, the height of the upper end of the passage forming plate 34 is set at a position near the middle of the vertical wall 16B.
The third refrigerant passage T3 is partitioned by the inclined portion 34B of the passage forming plate 34, the condensing portion side vertical portion 34C, and the lower half of the vertical wall 16B of the condensing portion casing 16.
The fourth refrigerant passage T4 is defined by the inclined portion 34B of the passage forming plate 34, the condensing portion-side vertical portion 34C, the upper half of the vertical wall 16B, and the ceiling wall 16D.
In the condensing unit housing 16, the refrigerant vapor introduced from the third refrigerant passage T3 to the fourth refrigerant passage T4 forms a flow from below to above.

Ten condensing pipes 517 are arranged in parallel in the fourth refrigerant passage T4 in the condensing unit 15.
The condensing pipe 517 includes a pair of flat walls 517A facing each other and a connecting wall 517B having an arcuate cross section that connects the edges of the flat wall 517A.
In this embodiment, the surface of the flat wall 517A of each condensing tube 517 is inclined with respect to the vertical direction.
The gap between the flat walls 517A of the adjacent condensation pipes 517 is set to a fixed distance from the upstream end to the downstream end, and the flat walls 517A of the adjacent condensation pipes 517 are parallel to each other.

In this embodiment, the flow of the refrigerant vapor (indicated by the arrow F in FIG. 8) introduced from the third refrigerant passage T3 to the fourth refrigerant passage T4 is on the inner side from the vertical wall 16B side that is the outer side in the condensing unit 15. It becomes a flow toward the center of a certain condensing part.
The flow of the refrigerant vapor indicated by the arrow F in FIG. 8 is the flow of the refrigerant vapor just before being introduced into the condensing tube 517, and in the horizontal direction of the refrigerant vapor from outside to inside below the condensing tube 517 in the condensing unit 15. It is the flow of.
Here, “immediately before introduction into the condensation pipe 517” refers to a period after the refrigerant vapor is guided to the fourth refrigerant passage T4 and during which no refrigerant vapor is introduced into the condensation pipe 517.
Furthermore, the direction of the “flow of refrigerant vapor immediately before introduction into the condenser pipe 517” here is limited to the direction indicated by the arrow F in FIG.
The lower connection wall 517B of each condensing pipe 517 is located on the upstream side in the flow direction of the refrigerant vapor indicated by the arrow F in FIG. 8, and the upper connection wall 517B is located on the downstream side in the flow direction of the refrigerant vapor.
That is, the upstream end of the condensing pipe 517 is positioned upstream of the refrigerant vapor flow direction just before introduction into the condensing pipe 517 in the condensing section 15.
Since the flat wall 517A of the condensing tube 517 is inclined to the flow of the refrigerant vapor, the surface of the flat wall 517A, which is the condensing surface of the condensing tube 517, is inclined to the flow direction of the refrigerant vapor. It passes along the flat wall 517A.
According to this embodiment, there exists an effect equivalent to the effect (1) of 1st Embodiment.

As another example of this embodiment, each condensing tube 517 may be arranged so that the gap on the upper end side of the condensing tube 517 is narrower than the gap on the lower end side, as in the second embodiment.
In the case of this other example, the lower end of the condensation pipe 517 is the upstream end, and the upper end is the downstream end, so the gap between the flat walls 517A of the adjacent condensation pipes 517 is the upstream end of the condensation pipe 517. It shrinks as it goes from the downstream end to the downstream end.
The liquefied refrigerant moves to the upstream end side along the flat wall 517A due to its own weight accompanying the growth of droplets due to condensation.
On the upstream end side of the condensation tube 517, a bridge (liquid bridge) in which the liquid-phase refrigerant bridges between the condensation tube 517 and the condensation tube 517 can be prevented.

The boiling cooling devices according to the first to sixth embodiments show one embodiment of the present invention, and the present invention is not limited to the above-described embodiments, and the invention is as follows. Various modifications are possible within the scope of the above.
In the first to sixth embodiments described above, the example in which ten condensing tubes are installed in the condensing unit has been described, but the number of condensing tubes is not particularly limited. In order to increase the condensation efficiency, the number of condensation tubes may be increased.
In the first to sixth embodiments, the heating elements are respectively attached to the pair of heat receiving walls of the reservoir housing, and the pair of first refrigerant passages and the third refrigerant passages are provided by installing the pair of passage forming plates. However, it is also possible to attach the heating element only to one heat receiving wall and to provide one passage forming plate. In this case, the first refrigerant passage to the fourth refrigerant passage are formed one by one.
In the above first to sixth embodiments, the condensing pipes having the same shape are used. However, the present invention is not limited to using condensing pipes having the same shape. For example, a plurality of types of condensing pipes having different flat wall lengths and cooling water passage widths may be mixed.
In the above first, fourth, and sixth embodiments, only the condensing pipe whose flat wall is inclined with respect to the vertical direction is arranged, but the present invention is not limited to arranging only the condensing pipe whose flat wall is inclined. For example, a condensing tube with a flat wall aligned with the vertical direction may be installed separately, and in this case, the condensing tube with the flat wall aligned with the vertical direction may cause an inappropriate flow of refrigerant vapor. It is desirable not to form.
In the second and third embodiments described above, among the plurality of condensing pipes installed in the condensing unit, the condensing pipes are arranged so that the flat walls coincide with the vertical direction, but the flat walls are not necessarily vertical. It is not necessary to include the condensing pipe arranged so as to coincide with the direction, and only the condensing pipe whose flat wall is inclined with respect to the vertical direction may be provided.
In the fourth and fifth embodiments described above, the condensing unit casing is provided with an inclined ceiling wall having a linear cross section, but the inclined ceiling wall is not limited to a linear cross section, for example, an arc It may be an inclined ceiling wall with a gentle continuous curved cross section. In this case, after the guidance from the third refrigerant passage to the fourth refrigerant passage, the flow of the refrigerant vapor from the outside to the inside in the condensing part immediately before being introduced into the condenser tube is inclined with respect to the flat wall of the condenser tube. Can do.

DESCRIPTION OF SYMBOLS 10 Boiling cooler 11 Heating body 12 Refrigerant storage part 13 Storage part housing | casing 14, 34 Passage formation board 15, 25 Condensing part 16, 26 Condensing part housing | casing 17, 217, 317, 417, 517 Condensation pipe | tube 17A, 217A, 317A 417A, 517A Flat wall 17B, 217B, 317B, 417B, 517B Connection wall R Liquid refrigerant B Bubble C Cooling water X Gap T1 First refrigerant passage T2 Second refrigerant passage T3 Third refrigerant passage T4 Fourth refrigerant passage

Claims (8)

A boiling cooling device comprising: a refrigerant reservoir that stores liquid refrigerant that receives heat from a heating element; and a condenser that is connected to the refrigerant reservoir and condenses evaporated refrigerant vapor,
A hollow plate-like condensing tube that circulates a cooling fluid inside is installed in the condensing part,
The condensing pipe includes a condensing surface in contact with the refrigerant vapor of the condensing part, an upstream end serving as a refrigerant vapor introduction side, and a downstream end serving as a refrigerant vapor outlet side.
The condensing surface is inclined with respect to the flow direction of the refrigerant vapor immediately before introduction into the condensing pipe in the condensing part, and is disposed.
The boiling cooling device, wherein the upstream end is positioned upstream of the downstream end in the flow direction of the refrigerant vapor immediately before introduction into the condensing pipe in the condensing unit.   The boiling cooling device according to claim 1, wherein the condensing surface is arranged so that refrigerant vapor in contact with the condensing surface flows from above to below along the condensing surface. The inside of the condensing part is partitioned into an introduction passage and a condensation passage, and a passage forming plate for guiding refrigerant vapor from the introduction passage to the condensation passage is provided in the condensation part,
The boiling cooling device according to claim 1 or 2, wherein the condensing pipe is disposed in the condensing passage.   The boil cooling device according to any one of claims 1 to 3, wherein a plurality of the condensing tubes are provided in parallel.   5. The boiling cooling according to claim 4, wherein a gap between the condensing surfaces of the condensing tubes adjacent to each other is set at a constant distance from the upstream end portion to the downstream end portion of the condensing tube. apparatus.   The boiling cooling device according to claim 4, wherein a gap between the condensing surfaces of the condensing pipes adjacent to each other is widened on a liquid surface side of the gap. The condensing unit includes a condensing unit housing,
The said cooling part housing | casing is equipped with the inclination ceiling wall which forms the flow of the said refrigerant | coolant vapor | steam immediately before the introduction to the said condensation pipe | tube, The boiling cooling device as described in any one of Claims 1-6 characterized by the above-mentioned.   The boiling cooling device according to claim 4, wherein heights of at least one of the upstream end portion and the downstream end portion of the condensing pipes adjacent to each other with respect to the liquid surface are different from each other.