JPS59123252A - Condenser - Google Patents

Abstract

PURPOSE:To obtain a condenser with high rate of heat transfer by a method wherein the inside of a condenser container is divided into a mixing chamber and a condensing chamber by a partition wall having a plurality of air passages, and coolant vapor is forced to conduct convection by utilizing the pressure difference due to the difference of temperatures between both of the chambers. CONSTITUTION:The partition wall 3 is provided, and the inside of the closed container 1 is divided, thus forming the mixing chamber 4 and the condensing chamber 5. A partition wall wherein a plurality of the air passages, e.g., holes 2 are formed is used for the partition wall 3. The coolant vapor generated by a heat generator 8 is led to the mixing chamber 4. On the other hand, since a tube 6 is supplied with low temperature fluid, the temperature in the condensing chamber 5 is lower than in the chamber 4, resulting in the decrease of the density of condensed gas, and then the pressure difference generates between the mixing chamber 4 and the condensing chamber 5. The coolant vapor flows into the condensing chamber 5 through the holes 2, is condensed by collision with the upper part of the condensed heat transfer surface of the tube 6, drops to the bent curved surface in the lower part of the partition wall 3 in the form of condensate 7, and then returns to the bottom in the closed container 1 through a condensate reflux passage B.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a condensing device that is used to cool a heat generating element such as a large-capacity semiconductor or a transformer, and that condenses refrigerant vapor generated by the boiling phenomenon of an organic refrigerant such as Freon.

[Technical background of the invention]

BACKGROUND ART Conventionally, cooling methods such as air cooling and oil cooling have been used to cool heavy electrical equipment, particularly equipment using large-capacity semiconductors such as rectifiers and frequency converters, or stationary equipment such as transformers.

However, these cooling methods have major problems in the reduction of the size of heavy electrical equipment, the removal of energy loss due to increased energy density due to large WJ, the non-flammability of the equipment, and safety.

For this reason, heavy electrical equipment is being put into practical use that not only keeps the temperature rise low, but also maintains the temperature of the entire system uniformly and applies the phase change phenomena of boiling and condensation, which dramatically increases the surface heat transfer coefficient. .

Such heavy electrical equipment utilizes the phase change when boiling an organic refrigerant such as FI/ON as a means of cooling the object to be cooled, but a condensing device that condenses the refrigerant vapor generated during continuous use is used. is essential.

[Problems with background technology]

By the way, this type of condensing device consists of a boiling section and a condensing section. Conventionally, in order to increase the condensing heat transfer coefficient of this condensing section, irregularities were provided on the condensing heat transfer surface of the tube forming the cooling fluid path. There are also ideas for adding an extended heat transfer effect of 1 m. On the other hand, it can be said that this condensing device determines the quality of the operation of the entire cooling system including the boiling part. However, the countercurrent that improves the condensation heat transfer performance of this part is still insufficient, and it cannot be said that it has reached the level of practical use.

[Purpose of the invention]

This invention was made based on the above-mentioned circumstances, and an object thereof is to provide a condensing device capable of increasing the condensing heat transfer coefficient.

[Summary of the invention]

In order to achieve the above object, the present invention divides the inside of a closed container into a mixing chamber and a condensation chamber by a partition wall having a plurality of ventilation passages, and directs steam generated by a heating element inside the closed container from the mixing chamber to the passageway. The refrigerant liquid is introduced into the condensing chamber through the condensing chamber, and the refrigerant liquid liquefied in the condensing chamber is introduced around the heating element.

[Embodiments of the invention]

A first embodiment of the present invention will be described below with reference to the drawings. FIG. 1 shows a cross-sectional view of this condensing device. This closed container 1 has a nearly trapezoidal cross section, and the upper half gradually increases in size toward the top. It has a T+ shape,
The lower half is straight. Inside this airtight container l, a partition wall 3 is installed which is mostly or almost parallel to the side wall on the upper half side and whose lower end is bent so as to be close to the side wall on the lower half side. A mixing chamber 4 and a condensing chamber 5 are formed by dividing the space. The partition wall 3 is formed with a plurality of ventilation passages, for example, holes 2, and the lower end of the partition wall 3 and the airtight container 1 are connected to each other.
This constitutes a reflux path B. Inside the condensation chamber 5, tubes 6 having a circular cross section and having a number of a number of tubes forming cooling fluid passages are arranged as shown in the figure.The valley body 6 is horizontal and the condensing heat transfer surface of each tube 6 In order to prevent any of the tubes 6 from being damaged due to the fall of the condensate 7 generated during the process, the tubes 6 are disposed horizontally so as to be shifted vertically and horizontally. A low-temperature fluid is supplied to the inside of each tube 6 from a low-temperature fluid supply section (not shown). Further, a heating element 8 is installed at the bottom of the airtight container 1, and an organic refrigerant liquid 9 such as Freon is sealed in the bottom of the airtight container 1. It consists of a boiling section that produces refrigerant vapor.

In this structure, when one heating element 8 generates heat, the organic refrigerant liquid 9 around it boils and generates refrigerant vapor A, and this refrigerant vapor A is mixed in the upper part of the closed container l. You will be led to room 4.

On the other hand, the mixing chamber 4 and the condensing chamber 5 are partitioned by a partition wall 3, and a low-temperature fluid is supplied into a pipe body 6 within the condensing chamber 5. Therefore, the temperature in the condensing chamber 5 is lower than that in the mixing chamber 4, and since it is in a condensed state on the condensing heat transfer surface of the tube body 6, the concentration of this condensable gas in the condensing chamber 5 decreases and the pressure becomes low. becomes. Therefore, a pressure difference occurs between the mixing chamber 4 and the condensing chamber 5, and the refrigerant vapor A in the mixing chamber 4 is transferred to the partition wall 5.
It flows into the condensation chamber 5 through the hole 2 . The refrigerant vapor A that has flowed into the condensing chamber 5 collides with the upper part of the condensation heat transfer surface of the tube body 6 and is condensed. Here, it becomes condensed liquid 7 and falls on the bent surface at the bottom of the partition wall 3, where it is condensed. Follow liquid return path B to airtight container 1
Return to the bottom inside.

In the first embodiment described above, since the partition wall 3 having a plurality of holes 2 is provided immediately before the condensing heat transfer surface of the tube body 6 in the condensing chamber 5, the mixing chamber 4 formed by this partition wall 3 Condensation chamber 5
A pressure difference is generated between the refrigerant vapor and the refrigerant vapor flowing through the vent hole 2 to the condensing heat transfer surface, and a good tQ compression heat transfer coefficient can be obtained.

This is fact 11 in Figure 2. This is also clear from the empty results. In other words, Fig. 2 shows a condensing device that is exactly the same as the one described above (in case 5, one stone wall 3 with a number of holes 2 is present, C, and the case where this partition wall 3 is removed). The pressure inside the 1-4 joint 4 is compared with the output of the heating element 8.As is clear from this, the internal pressure increases more slowly when the partition wall 3 is present, and the usage conditions are better.

It should be noted that since five holes 2 are formed in the partition wall 3, the amount of internal pressure generated increases or the internal pressure increases slowly.

Next, a second embodiment will be described with reference to FIG.

This actual case shows a condensing device 1 in which a condensable gas and a non-condensable gas coexist in a closed container 10, and the structure is almost the same as that in Fig. 1, and the closed container ≠ The cross-sectional structure of the container 10 is known, and the only difference is the internal structure of the degenerate 5.

In this second embodiment, the steam A generated by heat generation passes through the holes 2 of the partition wall 3 and collides with the condensation heat transfer surface of the tube body 6, and the heat transfer coefficient is not increased, but the condensation of the tube body 6 Blow away non-condensable gas that is disturbed near the heat transfer surface. For this reason,
The heat transfer surface in this part is always in contact with condensable vapor, which makes it possible to reverse the decrease in heat transfer coefficient caused by non-condensable gas, and promotes the condensation action.

On the other hand, condensation occurs not only on the tube body 6 but also on the surface of the closed container 1. The pressure distribution and flow inside the condensing chamber 5 are determined by the temperature of the cooling fluid supplied to the inside of the tube body 6 which houses the condensing heat transfer surface. Condensable gases become present in high concentrations.

Therefore, since the low-temperature tube body 6 is installed at a location t'fl away from the partition wall 3, non-condensable gas is collected around it, improving the condensation heat transfer coefficient in the area near the partition and γ3. can be kept.

In addition, mixing 148 F6 (sulfur hexafluoride) gas as the non-condensable gas with a non-condensing gas in a closed container will significantly reduce the condensation heat transfer performance, so it is better not to mix it. Good, but 1. A considerable amount of non-condensable gas is mixed in to maintain dielectric withstand voltage, which is a problem at startup when sufficient refrigerant vapor such as Freon is not generated. For this reason, conventional rod condensing devices are forced to be larger, and due to the size of the condensing device, secondary countermeasures such as earthquakes require installation space and are difficult to put into practical use. I was struggling with all my troubles.

The effect of the embodiment shown in FIG. 3 is also clear from the experimental results shown in FIG. That is, FIG. 4 shows the output of the heating element 8 and the inside of the mixing chamber 4 in the case E when the partition wall 3 having a plurality of holes 2 is present and in the case F when the partition wall 3 is removed in exactly the same condensing device. It is the ratio of the pressure of Note that these are experimental results when SF6 gas was used as the non-condensable gas and Freon (R113) was used as the cooling medium.

As described above, when the partition wall 3 is present, the internal pressure increases more slowly than when the partition wall 3 is not present, even if the generated heat loss increases, and the usage conditions are better.

Next, a third embodiment of the present invention will be described with reference to FIG.

In this embodiment, a crank-shaped partition wall 13 having a plurality of holes 12 is installed 7 in an airtight container 11 having a short cross-sectional shape, dividing it into a mixing chamber 14 and a condensing chamber 15.
A plurality of tubular bodies 17 forming a cooling fluid path connected by pipes 16 are arranged vertically within the closed container 11, and a heating element 18 is installed at the bottom of the closed container 11, and an organic refrigerant liquid is placed around the heating element 18. It is fulfilled. In addition, the code|symbol 20 has shown the condensate reflux path.

Of course, even in such a configuration, the same effects as in the above embodiment can be obtained.

Next, a fourth embodiment of the present invention will be described with reference to FIG. 6.

In this embodiment, the closed container 10 in FIG. 3 is vertically divided into two parts, one of which is made into a closed container 21, and one condensation chamber 5 is provided in this closed container 21, thereby reducing the size of the entire device. It is something. It goes without saying that this embodiment also provides the same effects as the second embodiment.

Next, regarding the fifth embodiment of this invention, please refer to FIG. 7! I will clarify.

In this embodiment, a container 22 has a shape slightly different from the closed container 21 shown in FIG. 6, and two or more layers of tubes 23 similar to the tubes 6 are arranged in a portion away from the partition wall 3.

Therefore, according to this embodiment, since the tube body 23 is arranged even in a portion remote from the partition wall 3, it is particularly effective for a case where non-condensable gas and condensable gas are mixed. That is, the condensing chamber 5
A difference in concentration occurs in the distribution of non-condensable gas within the tank, allowing it to function as a non-condensable gas reservoir.

Next, a sixth embodiment will be described with reference to FIG.

In this embodiment, a plurality of plate-shaped molded members, for example, members 24 having a U-shaped cross section, are arranged with a gap 25 between them, and this gap 25 is located diagonally above the condensing pipe 6. The partition wall 26 is constructed in a similar manner and has the same function as the partition wall 3 of the previous embodiment. In addition, the 8th
In the figure, reference numeral 27 indicates a cooling fluid.

According to this embodiment, since the gap 25 is provided along the tube body 6, the passage of the refrigerant vapor A is improved, and the condensing heat transfer coefficient is further increased.

Next, a seventh embodiment will be described with reference to FIGS. 9 and 10. In this embodiment, a plurality of plate-shaped molded members 24, for example, members 24 having a substantially V-shaped cross section, are arranged as partition walls 26 with a gap 25 left in order to form a ventilation path. The off-line heat transfer surface 30 of the tube body 29 forming the cooling fluid path is formed into a wave shape, and this protrusion 3θ
A corresponds to the gap 25, and its four parts 30
The condensate 7f'1.31 generated on the condensation heat transfer surface 30 is stored and flows down to B. With this structure, an enlarged heat transfer surface effect is added to the condensing heat transfer surface, and a thick protrusion with a large condensing effect, ? Since the thickness of the condensate film around the OA is kept small and the flow impingement effect is added, a high heat transfer coefficient can be maintained.

Incidentally, the present invention is not limited to the above-mentioned embodiment, but may be modified as follows. That is, a nozzle body may be provided at one end of the air passage in the embodiment described above to reduce pressure loss during flow of condensable steam. Further, the condensing heat transfer surface may be provided with a groove for allowing the condensate to flow down, so that the condensate can be efficiently removed from the condensing heat transfer surface. Furthermore, the formation of partition walls and ventilation passages may be made arbitrary. Other modifications may be made without departing from the gist of the invention.

〔Effect of the invention〕

According to the invention described above, the inside of the condenser container is divided into a mixing chamber and a condensing chamber by a partition wall having an air passage of Ney's number, and heat is generated by utilizing the pressure difference caused by the temperature difference between the compartments. Since the steam generated by the body is forced to undergo convection, it is possible to provide a condensing device with a high heat transfer coefficient.

[Brief explanation of drawings]

FIG. 1 is a sectional view of a device for explaining the first embodiment of the present invention, FIG. 4 is a characteristic diagram of the device for explaining the effects of the second embodiment, and FIGS. FIGS. 9 and 10 are cross-sectional views for explaining the third to sixth embodiments, and FIGS. 9 and 10 are cross-sectional views for explaining the seventh embodiment. DESCRIPTION OF SYMBOLS 1... Airtight container, 2... Ventilation path, for example, hole, 3... Seedling, 4... Mixing chamber, 5... Condensation chamber, 6... Pipe forming a cooling fluid path, 7...・Condensate, 8... Heating element, 9...
Organic refrigerant liquid, 10.11... Airtight container, 12 - Ventilation path, e.g. hole, 13... Partition wall, 14... Mixing chamber, 15
... Condensation chamber, 17... Pipe body forming a cooling fluid path,
18... Heating element, 19... Organic refrigerant liquid, 21, 22
... Sealed container, 23 Pipe body forming a cooling fluid path, 2
4... Plate-shaped molded member, 25... Gap, 26... Partition wall, 29... Pipe body forming cooling fluid path, 30...
Condensation heat transfer surface, A: refrigerant vapor, B: reflux path. Applicant's agent Patent attorney Takehiko Suzue Figure 1 Figure 2 Figure 44 View 1 Figure 3 Figure 4! L Book 4-Person Figure 5 - /i Volume 7 Figure 7? Figure 3b Figure 9 Whistle/θ Figure Director of the Patent Office Kazuo Wakasugi 1, Indication of the case g This application No. 57-233493 2, Condensed name of the invention T fatigue 3, Case of the person making the amendment Relationship Patent applicant (307) Tokyo Shibaura Mjf, Ki Co., Ltd. 4, agent

Claims (9)

[Claims] (1) An organic refrigerant liquid is sealed in the lower part of the sealed container, this organic refrigerant liquid is placed in the lower part of the sealed container, a steamed heating element generates refrigerant vapor, and this refrigerant vapor is placed in the upper part of the sealed container. In the condensing device that condenses on the condensation heat transfer surface of the condensing body and circulates it to the organic refrigerant liquid, a partition wall having a plurality of ventilation passages is provided in the upper part of the closed container to separate the condensation chamber where the tube body exists and the tubes. The refrigerant vapor in this mixing chamber is guided to the condensing chamber through the air passage of the partition wall, and the refrigerant liquid liquefied on the condensation heat transfer surface of the tube body is transferred to the heating element. A condensing device characterized in that it is guided around the (2) The condensing device according to claim 1, wherein the partition wall is made of an integral plate-like section, and a plurality of ventilation passages are formed in the partition wall. (3) The condensing device according to claim 1, wherein the partition wall includes a plurality of plate-shaped molded members arranged side by side with gaps between them, and the gaps constitute ventilation passages. (4) The condensing device according to claim 2, wherein the ventilation path of the partition wall is formed by a hole formed in an integral plate member and a nozzle provided in the hole. (5) The condensing device according to claim 1, wherein the tube body is formed of a circular tube member. (6) The condensing device described in the scope of the patent δI''■, item 1, wherein the condensing heat transfer surface is formed into a corrugated shape. (7) The condensing device according to claim 1, wherein the condensing chamber (d) has a plurality of tube bodies arranged to function as a non-condensable gas reservoir. (8) The condensing device according to claim 1, wherein a groove is formed to allow the condensed liquid of the pipe body within the amount of condensation to flow down. (9) A reflux path is formed at the lower end of the partition wall so that only the condensate flows down and refluxes, avoiding non-condensable gas from refluxing from the condensing chamber to the lower part of the closed container where the heating element is located. The condensing device according to item 1.