JPS60185091A - Condenser - Google Patents

Abstract

PURPOSE:To obtain high coefficiency in transmitting condensation heat in a condenser, by efficiently dripping condensed drain, by providing tubular projections, of which one side is made in smooth slope and the other side is made in plane so as to form a ridge line, to the outer surface of a heat transfer pipe, with the sloped side upward, having distances one another in the longitudinal direction. CONSTITUTION:Tubular projections 31, 31... extending outwardly to the radius direction, are monolithically formed on the outer surface of a heat transfer pipe 30, having distances one another in the longitudinal direction. The tubular projection 21 is composed so as to form a smooth slope 32 on one side, while the other side forms a plaen 33, and a ridge line 34 is formed between these faces. The projections 31 are formed on the outer surface of a heat transfer pipe 30, so as to put the sloped surface 32 upward, that is the upstream side for the deep-sea water flowing down through the heat transfer pipe 30. The root of a slope 32 is jointed to the outer surface of a heat transfer pipe 30 with a smooth surface. With such an arrangement, condensed drain adhered to the outer surface of a heat transfer pipe 30 drips along the outer surface of a pipe 30, flowing outwardly to the radius direction along the slope 32 of a projection 31, turning into drips on the ridge line 34 provided at the tip of a slope 32, from which the drain is dripped down.

Description

DETAILED DESCRIPTION OF THE INVENTION [Technical Field of the Invention] The present invention relates to a condenser installed in a low heat drop power generation '7° land etc. that generates electricity using low heat drop energy such as the temperature difference of seawater. 1 ゜ [Technical Agency for Invention]: The generator 1 ゜ vitral dialect 2, as shown in Fig. 1, the marine temperature that generates electricity using the temperature difference of seawater is used.
．． Steam turbine 3. Condenser 4. The tank 5 is connected by a pipe 6 to form a closed circuit. The evaporated working fluid is heated and evaporated by relatively high temperature seawater.
The steam is sent to the steam turbine 3 via the steam control valve 2, where it is subjected to an expansion effect and rotates the steam turbine 3, which rotates the generator 7 attached to the steam turbine 3 to generate electricity. Condenses the steam discharged from W4
The condensed water is sent to the tank, where it is condensed with relatively low-temperature seawater from the deep ocean, and the condensed water is stored in a tank 5 and then returned to the evaporator 1 by a circulation pump 8.

In addition, the load fluctuation of the generator 7 can be adjusted by opening and closing the sawbino valve 10 installed in the path 9 connecting the upper 6H7 side of the steam control valve 2 and the downstream side of the steam turbine 3. It looks like this.

In the above-mentioned ocean temperature difference power generation plant, the temperature difference between the high and low heat sources is small, so the transmission net efficiency is low, on the order of a few degrees, and the heat exchanger heat load per unit power generation output is extremely large. The temperature difference between the heat source and the working fluid is 2 to 5 degrees Celsius.
It is necessary to set the heat exchanger to be extremely small, which increases the manufacturing cost and installation space of the heat exchanger, making it important to improve the performance and make the heat exchanger compact. Furthermore, compared to water, which is a conventional working fluid, low-boiling point media such as fluorocarbons have lower
Since the heat transfer characteristics are inferior by about one order of magnitude, in order to improve the performance and make the heat exchanger more compact, it is necessary to improve the heat transfer performance on the working fluid side, which defines the heat transfer coefficient.

MB installed in the above ocean temperature difference power generation plant
The two types of condensers used are plate type and shell-and-tube type, and these types of condensers are becoming larger as turbine output increases, making installation on land a space issue. Since the slight increase or decrease in pressure loss on the seawater side affects the output of the turbine at the transmission end, it is not a good idea to forcefully convey the intake seawater to land, and various types of equipment are being considered to be installed offshore. .

That is, in order to install various devices on the purge, the condenser is also designed to be vertical due to the need for compact equipment arrangement.

As shown in FIG. 2, the vertical condenser includes a vertical casing 11, partition plates 12, 12 arranged at intervals in the vertical direction within the vertical casing, and a plurality of heat transfer tubes 13.
The partition plates 12 and 1 are arranged in parallel with the T-support plate 14 interposed therebetween.
2, and a vertical partition plate 15 that divides the chamber defined by the casing 11 and the upper partition plate 12 into two, and one chamber 16 has a deep seawater introduction pipe 17, A deep seawater outlet pipe 19 is connected to the other chamber 18 . Further, a working flow sampling inlet pipe and a working fluid condensation drain outlet pipe 21 are connected to the wall of the casing 11 between the partition plates 12 and 12.

The deep seawater introduced into the chamber 16 through the deep seawater introduction pipe 17 flows through the heat transfer tube 13 in the direction indicated by the arrow, and flows through the chamber 17.
The working fluid is discharged outside the vessel through the deep seawater outlet pipe 19, while the working fluid is led into the vessel from the working fluid steam introduction pipe.
Heat is exchanged with deep seawater flowing inside each heat exchanger tube 13,
The condensed liquid flows down along the outer surface of each heat transfer tube 13, is collected in a liquid reservoir at the bottom of the condenser, and is then discharged outside the vessel through the working fluid condensed drain outlet pipe 21.

[Problems with background technology]

However, in the above type of condenser, since the outer surface of the heat transfer tube is a smooth surface, the heat transfer surface can be set large, and there is a limit to increasing the heat transfer effect.

Therefore, as shown in FIG. 3, the heat transfer tube 13 is a fluted tube having longitudinally extending grooves 22 by machining or rolling the outer circumferential surface of the heat exchanger tube 13 as a technical measure to promote condensation heat transfer. was developed.

However, in the heat exchanger tube 13, as shown in FIG.
The condensate and water condensed at the peaks are guided to the valleys by the effect of surface tension, the condensate film at the peaks is thinned, and the condensed condensate is removed at the valleys to promote condensation heat transfer. However, in reality, as the condensation progresses, the condensed condensate increases, so the condensed condensate overflows from the Tanibe Sae, and the condensed condensate cannot be effectively removed at the Yamabe Otsu. You can't expect much improvement in performance.

Furthermore, a technical means has been proposed in which disks are externally fitted at intervals in the longitudinal direction of the heat exchanger tubes 13 to eliminate condensation drain, but in this case, a disk must be attached to each of the heat exchanger tubes. Furthermore, since the heat exchanger tubes are supported by support plates, there are restrictions on their mounting positions, making the assembly of the heat exchanger complicated and impractical.

[Purpose of the invention]

The present invention has been made in view of the above-mentioned points, and an object of the present invention is to provide a condenser that can easily remove condensation tubes adhering to the outer surface of a heat exchanger tube and improve its performance. purpose.

[Summary of the invention]

In the present invention, an annular protrusion is formed on the outer circumferential surface of a heat exchanger tube provided in a casing and extends in the vertical direction, with the - side being a gently sloped surface and the other side being a flat surface forming a ridgeline. The tubes are arranged at intervals in the longitudinal direction, and the condensate condensate adhering to the outer surface of the heat transfer tube is efficiently flowed down, thereby obtaining a high condensation heat transfer coefficient.

[Embodiments of the invention]

An embodiment of the present invention will be described below with reference to the drawings.

In FIG. 5, the reference numeral (capital) indicates a heat exchanger tube incorporated in the condenser of the present invention, and on the outer circumferential surface of the heat exchanger tube side, extending radially outward is provided at intervals in the longitudinal direction. The annular protrusions 31 and 31 are integrally formed.

As shown in FIG. 6, the annular protrusion 31 is configured to have a gentle slope 32 on the first side and a flat surface on the other side, forming a ridge line 34 between them. It is provided protrudingly on the outer circumferential surface of the heat exchanger tube I so as to be located on the upper side, that is, on the upstream side of the deep R1 seawater flowing through the heat exchanger tube 30. The base end of the inclined surface 32 has a smooth surface connected to the outer surface on the heat exchanger tube side. Therefore, heat exchanger tube (equipment)
The condensed condensate adhering to the outer circumferential surface of the projection 31 descends along the outer circumferential surface of the heat exchanger tube side, and then flows radially outward along the inclined surface 32 of the protrusion 31. At the provided ridgeline, it becomes drop-shaped and is dripped from there.

Experimentally, the distance between the annular protrusions provided on the heat transfer tube side varies depending on the type of condensed fluid and the amount of condensation per unit length, but it has been determined that the interval between the annular protrusions is approximately 10 to 100 mm. It is desirable to set the thickness to about 0.3 to 1.0 mm in consideration of the peeling effect and the assembly work of the heat exchanger.

Next, the action will be explained.

The deep seawater introduced into the chamber 16 via the deep seawater introduction pipe 17 provided inside the casing 11 passes through the heat transfer tubes 30 arranged in the vertical direction, and is discharged outside the chamber 17 through the deep seawater outlet pipe 19. However, a working fluid such as chlorofluorocarbon is introduced into the casing 11 through a working fluid introduction pipe 20, and when this working fluid passes between the heat transfer tubes (2) arranged in a row, it passes through the heat transfer tubes 30. Heat is exchanged with the deep seawater that passes through it, and it is condensed and liquefied. The condensed and liquefied condensate settles on the outer peripheral surface of the heat exchanger tube (9) and becomes droplets, and the condensed condensate descends along the outer surface between the heat exchanger tubes and reaches the base of the inclined surface (material) of the annular protrusion 31. # at the end and then radially outward along the ramp 32
As shown in Fig. 6, the liquid is guided to the ridge line provided at the tip of the annular protrusion 31, from which it drips under the action of gravity, collected in a reservoir provided at the bottom of the condenser, and condensed drain. It will be discharged outside the vessel through the pipe 21.

The drain attached to the outer surface of the heat exchanger tube is removed by the annular protrusion 31.
Since the condensate actively flows radially outward along the inclined surface 32 of the heat exchanger tube, the condensate does not remain attached to the outer surface of the heat exchanger tube, and the entire outer surface of the heat exchanger tube is used as a surface for heat exchange. Because of this, a high condensing heat transfer coefficient can be obtained.

Figure 7 shows the experimental results of the condenser according to the present invention, using Freon as the working fluid and showing the condensation temperature (℃).
I conducted an experiment with.

In Fig. 7, the vertical axis 4II+ is the ratio of the condensing heat transfer coefficient of the heat exchanger tube of the present invention to the condensing heat transfer coefficient of the heat exchanger tube with a flat outer surface (smooth tube), and the horizontal axis is the interval between the annular projections provided on the heat exchanger tube. It is.

According to the above experimental results, the performance ratio with that of a smooth tube gradually decreases as the interval between the annular protrusions increases. Since the seawater absorbs the latent heat of condensation from the working fluid outside the pipe and the temperature rises T, the heat flux gradually decreases in the longitudinal direction.

In other words, the amount of condensation per unit length gradually decreases, so
M kd per unit length The distance between the protrusions should be narrow in areas with a lot of lids, and the distance between the protrusions should be widened in areas with a small amount of condensation per unit length to effectively eliminate the condensation drain that is formed. This is desirable.

Is Fig. 8 another embodiment of the present invention? It is something that shows
In this case, an annular projection 31 is provided on the outer peripheral surface of the heat exchanger tube 40 in the same manner as on the heat exchanger tube side, and an annular projection 3] is provided on the outer peripheral surface of the heat exchanger tube 40.

A vertical groove 41 extending in the longitudinal direction in a portion located between 31 and 31.
I try to fully form it. It has been experimentally found that the provision of the vertical grooves 41 significantly improves the condensation heat transfer coefficient in this portion.

〔Effect of the invention〕

As described above, according to the present invention, protrusions are provided at intervals on the outer peripheral surface of the heat transfer tube to actively remove attached condensate condensate, so that the condensation heat transfer coefficient is significantly improved. ? L. The condensing performance is improved and the device can be made more compact.

[Brief explanation of the drawing]

Figure 1 is a schematic system diagram of the ocean temperature difference generator 7". Figure 2 is a sectional view of the vertical condenser installed at the ocean temperature difference generator tf/t. Figure 3 is a cross-sectional view of the vertical condenser FIG. 4 is an explanatory diagram of the action of the condensation drain attached to the heat exchanger tube. FIG. 5 is a partial perspective view of the sixth heat exchanger tube incorporated into the condenser according to the present invention. FIG. Fig. 7 is a diagram showing the experimental results of heat transfer performance. Fig. 8 is a diagram showing an embodiment of the pond of the present invention. 11...Vertical casing, 16...room, 18...
Room. 30... Heat exchanger tube, 31... 04-shaped projection, 32...
Slope direction, 33...Plane, 34...Ridge line. Submission of application Taku Mata Kiyoshi Figure 3 Figure 4121 Figure 5 ■+ ■- Figure 6 Imo Figure 8 Proceedings City book May 14, 1980 Commissioner of the Patent Office Kazuo Wakasugi 1 Display of the case 1982 Year Patent Application No. 39583 2 Name of the invention Condenser 3 Relationship with the case of the person making the amendment Patent applicant (307) Toshiba Corporation 4 Representative Agent 11th edition of the 11th publication β゛111 Drawings in simplified form.゛(Instruction 1. / 8 Contents of amendment (1) Mei III It, page 5, lines 14 to 15, the statement ``There is a limit to the heat transfer surface...'' is corrected as follows. The heat transfer performance on the fluid side is extremely low, and an enormous heat transfer area is inevitably required.'' (2) Request No. 41 in Figure 8 is amended so that it is not distributed in a separate sheet.

Claims (1)

[Claims] 1. A condenser in which a plurality of heat transfer tubes supported by a support plate are disposed inside a casing so as to extend vertically,
The current protrusions, which have one side as a gently sloped surface and the other side as a flat surface forming a ridgeline, are arranged at intervals on the outer circumferential surface of the heat exchanger tube, with the sloped surface facing upward. What I did f! : Condenser with % characteristics. 2. The condenser according to claim 1, wherein the interval between the annular protrusions is set to be narrower at a portion where the amount of condensation per unit length is large. 3. The condenser as set forth in item 1 or 2 of the scope of claim J1, characterized in that a groove extending in the longitudinal direction is formed on the outer circumferential surface of the heat transfer tube located between the annular protrusions.