JP2006112706A - Duct device for supplying dehumidified air - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a novel duct device for supplying dehumidified air, capable of attaining an energy saving as the whole by further improving the heat exchange efficiency between an air inlet side and an air outlet side in a device for supplying dry air to a cupola or the like. <P>SOLUTION: This device comprises a duct body 10 having the air inlet port 11 at one end and the air outlet port 12 at the other end and a dehumidifier 15 provided therein, the areas across the dehumidifier 15 being linked by a heat exchanger, in which air taken through the inlet port 11 is dehumidified, and supplied to an intended facility 2 through the outlet port 12 while leveling the temperature difference between the inlet port 11 and the outlet port 12. As the heat exchanger, a heat pipe 20 is applied. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to an apparatus suitable for supplying combustion air to, for example, an iron furnace or foundry cupola, and the supplied air may be in a dehumidified state. The present invention relates to a novel dehumidified air supply duct device that can greatly reduce the running cost when required.

For example, iron ore furnaces and cupolas require a large amount of air supply for high-temperature combustion, but in order to stably melt raw materials such as iron ore, the supply of sufficiently dehumidified air is required. It has been.
For this reason, it has been common practice to provide a dehumidifying device in the supply duct, and the principle adopted in this dehumidification is to cool the air that has been taken in, and the water vapor that the air can contain. By reducing the limit amount (saturated water vapor amount), the excess water vapor is formed into water droplets, collected and removed as moisture, and the supplied air is dehumidified. For this reason, the air supplied to the cupola or the like is supplied with the air that has been cooled simultaneously with the dehumidification.

  However, considering that the air supplied to the cupola and the like is for the purpose of promoting combustion, it is not necessarily preferable that the air is cooled. For this reason, in the conventional air supply method, for example, as shown in FIG. 5, for the purpose of dehumidification, once cooled air is heated and then supplied to a cupola or the like. That is, in the conventional method, a heat exchanger is arranged so that the intake port 11 ′ side that is the outside air intake side and the intake port 12 ′ side that is the combustion air discharge port side are linked to cool the intake port 11 ′. A method has been adopted in which the previous air calorie (heat quantity of the outside air) is applied to the air on the outlet 12 'side after cooling and is heated and then supplied to a cupola or the like. Moreover, the heat exchange method in this case is generally performed by, for example, simply using water or a brine solution as a heat medium and circulating the heat medium to exchange heat.

However, such a method is merely heat exchange by utilizing the sensible heat of the heat medium, and also requires power for circulating the heat medium. Therefore, the operation efficiency is not always good, and there is still room for improvement. there were.
Incidentally, the cooling and heating of the air in the conventional apparatus will be described with reference to specific numerical values by actual machines, as shown in FIG. 5 above, for example, intake air of about 35 ° C. (this outside air is in a standard state). For example, when dehumidifying by taking up 25 g of water per m ³ into the apparatus, it is necessary to cool the taken-in air to about 4 ° C. in order to forcibly reduce dehumidification, that is, the saturated water vapor amount. there were. In addition, when supplying to the cupola or the like, the cooled and dehumidified air is finally heated to about 17 ° C. by heat exchange with the intake outside air and then supplied to the cupola or the like (after dehumidification) As an example, warm air contains about 5 g of water per m ^{3 in the} standard state). As described above, the air supplied to the cupola or the like can only rise in temperature by about 13 ° C. from 4 ° C. to 17 ° C. after dehumidification cooling, and the inlet air can only be cooled from 35 ° C. to 29 ° C. For this reason, the dehumidifying refrigerator needs to be cooled from 29 ° C. to 4 ° C., and the cooling and dehumidifying load is very large.

  The present invention has been made in view of such a background, and further improves the heat exchange efficiency between the inlet side and the outlet side, thereby achieving energy saving as a whole. This is an attempt to develop a dehumidified air supply duct device.

  In other words, the dehumidified air supply duct device according to claim 1 has one opening of the duct body as an air inlet, the other opening as an air outlet, and a dehumidifier inside the duct body. The area sandwiching the dehumidifying device is linked by a heat exchanger to dehumidify the air from the inlet, and level the temperature difference between the inlet and the outlet, so that the inlet to the target equipment In the apparatus for supplying air, the heat exchanger is formed by applying a heat pipe.

  Further, the dehumidified air supply duct device according to claim 2 is characterized in that, in addition to the requirement of claim 1, the duct main body is curved in the middle between the inlet and the outlet, It is characterized in that it is in a state of being arranged almost in parallel, and a plurality of heat pipes are arranged in this arrangement range.

  Further, in the dehumidified air supply duct device according to claim 3, in addition to the requirement of claim 2, the plurality of heat pipes are arranged so that the temperatures acting on the pipes are balanced. It consists of features.

  The above-described problems can be solved by using the configuration of the invention described in each of the claims. That is, according to the invention described in claim 1, since the heat pipe principle is used, heat exchange efficiency is excellent, and no power for forcibly circulating the heat medium as in the prior art is required. Energy saving as a whole device can be achieved. Also, the supplied air can be supplied with dry air that has been sufficiently heated (heated up), and more suitable air can be supplied for use in an iron ore furnace.

  Moreover, according to the invention of Claim 2, the arrangement | positioning aspect of a heat pipe can be comprised more rationally.

  Furthermore, according to the invention described in claim 3, the heat load applied to each heat pipe can be made substantially uniform.

  The best mode of the present invention is as described in the following examples, and further includes various modes that can be improved under this technical idea.

Hereinafter, the present invention will be specifically described based on illustrated embodiments. As shown in FIG. 1 as an example, the dehumidified air supply duct apparatus 1 of the present invention supplies combustion air to a target facility 2 such as a cupola or a steelmaking ore furnace. Since it is performed by pressure feeding, a blower 3 is provided in the front stage of the apparatus.
Hereinafter, the dehumidified air supply duct device 1 of the present invention will be described more specifically. Reference numeral 10 in the figure denotes a duct body, which is a hollow duct having a square cross section, for example, having an intake port 11 opened on the front side and an intake port 12 opened on the other end. In the embodiment shown in FIG. 1, the duct body 10 is partially provided with a curved portion 13 in the body portion (midway portion) between the inlet 11 and the outlet 12, so that the duct body 10 is as if. And the intake port 11 and the intake port 12 are arranged side by side.

  An air filter 14 is provided near the intake 11 of the duct body 10, and a dehumidifying device 15 is provided inside the duct body 10 so as to act on the air flow. The dehumidifying device 15 follows a normal dehumidifying principle, and includes two cooling devices as an example, which are referred to as a primary cooling device 16 and a secondary cooling device 17. Note that a heat pump is applied to each of the primary cooling device 16 and the secondary cooling device 17, and an evaporator for cooling (in the case shown separately, 16 a, 17 a and so on) is provided in the duct body 10. Only) is provided. Furthermore, a filter-like eliminator 18 that collects and removes water removed from the air flow by cooling is provided at the subsequent stage of the evaporator 17a of the secondary cooling device 17.

As a characteristic configuration of the present invention, a large number of heat pipes 20 as heat exchangers are provided so as to link the vicinity of the inlet 11 of the duct body 10 and the vicinity of the outlet 12. As shown in FIG. 1 as an example, the heat pipe 20 is evacuated by enclosing an appropriate amount of a heat medium M such as Freon or CO _{2 in} a tubular main body (hereinafter referred to as a container C) called a container. In the container C, a wick layer W made of a mesh material or the like is formed. The wick layer W is for efficiently moving the liquefied heat medium M by capillary action or gravity. Moreover, the symbol FI in the figure is a fin for increasing the heat exchange efficiency.

  Here, the operation of the heat pipe 20 will be described. Since the inlet 11 side comes into contact with a relatively high temperature outside air and the outlet 12 side comes into contact with a relatively low temperature dehumidified cold wind, the heat pipe 20 The inlet 11 side becomes a part (heating part) to be heated, and the outlet 12 side becomes a part (heat radiation part) that releases heat. For this reason, on the inlet 11 side, the liquid heat medium M itself evaporates and vaporizes due to heating from the outside air wind, and as a result, it becomes gaseous and moves toward the outlet 12 in the heat pipe 20. (When viewed from the outside air, the heat pipe 20 is cooled by the amount of heat applied). On the other hand, at the outlet 12 side, heat is released to the dehumidified cold air, and the gaseous heat medium M condenses, liquefies and returns to the inlet 11 side (when viewed from the dehumidified cold air, the heat pipe 20 It is heated by the amount of heat released). At this time, due to the capillary structure of the wick layer W and the gravity of the liquefied heat medium M itself, the liquefied heat medium M instantaneously returns to the intake 11 side. In the present invention, heat exchange is performed by refluxing the heat medium M in the heat pipe 20 as described above, and this phenomenon itself is a liquid phase / gas phase change (state change) of the heat medium M, That is, it is an extremely efficient heat exchange means using latent heat. In view of this, when viewed from the heat pipe 20, it can be said that the intake 11 side is an evaporating part and the outlet 12 side is a condensing part.

  The outside air taken into the duct main body 10 is subjected to various treatments by the above-described components while flowing in the duct, and the temperature and humidity change. Organize about. First, since the outside air has a relatively high temperature, the outside air temperature F1 is used. Further, since the outside air temperature F1 removes dust, dirt, and the like by the air filter 14, the air that has passed therethrough is referred to as a dust removal hot air F2. Further, since the dust removal hot air F2 is preliminarily cooled by the action of the heat pipe 20, the air passing through here is referred to as precooling air F3. Further, since the pre-cooling air F3 is cooled by the action of the primary cooling device 16, the pre-cooling air F3 is referred to as the primary cooling air F4. Further, since the primary cold air F4 is cooled to a target temperature by the action of the secondary cooling device 17, the air passing through here is referred to as secondary cold air F5. Further, since the secondary cold air F5 removes (dehumidifies) water that cannot be present in the cooling air by the eliminator 18, the air passing through the secondary cool air F5 is defined as dehumidified cold air F6. And since the dehumidification cold wind F6 is heated by the effect | action of the heat pipe 20 in the vicinity of the taking-out port 12, and will be in the state in which the desired dehumidification and the heating process were performed, let this be the dehumidification warm air F.

The dehumidified air supply duct device 1 of the present invention has the basic structure as described above, and hereinafter, the taken-in outside air (outside air temperature F1) is dehumidified and heated by this device to the target facility 2. A mode of supplying will be described.
(1) Intake of outside air and dust removal For example, outside air is introduced by the blower 3 and guided into the duct body 10. By the way, as an example of the configuration specification of the actual air intake amount per hour, in 210000M ³ under standard conditions, moisture is 23g per 1 m ^3. The temperature of the air (outside air temperature) is about 35 ° C., and is about 59% in terms of relative humidity (RH). The outside air temperature F1 is taken into the duct main body 10 and then reaches the evaporation portion of the heat pipe 20 as the dust removal hot air F2 in which dust or dust is captured by the air filter 14.

(2) Pre-cooling by heat pipe When the dust removal hot air F2 reaches the evaporation section of the heat pipe 20, the heat is taken away by the heat medium M enclosed in the pipe and precooled (preliminarily cooled). Here, the cooling by the heat pipe 20 is referred to as “pre-cooling” because the air (pre-cooling air F3) is cooled to the target temperature by the subsequent dehumidifying device 15 (two cooling devices 16, 17). Because. Incidentally, the temperature of the pre-cooling air F3 depends on the number of installed heat pipes 20, the type of the heat medium M, and the like, but is cooled to about 21 ° C. as an example. Note that the heat absorption from the dust removal hot air F2 by the heat medium M is that heat is applied from the heat pipe 20, whereby the heat medium M in the inlet 11 portion evaporates and moves to the outlet 12 side. To do.

(3) Cooling and dehumidification by dehumidifying device The precooled air F3 preliminarily cooled by the heat pipe 20 is then cooled by the dehumidifying device 15 to a target temperature (about 4 ° C. as an example). Here, since the dehumidifying device 15 is composed of two cooling devices 16 and 17, the precooling air F3 is cooled to about 10 ° C. by the primary cooling device 16, and the primary cooling air F4 is 4 by the secondary cooling device 17. It is cooled to about ℃.
In addition, the air (outside air temperature F1) is subjected to such cooling (pre-cooling, primary cooling, secondary cooling) sequentially, so that the saturated water vapor amount is reduced, and the surplus water vapor component is turned into water droplets. It is transferred in the form of an air stream. Therefore, this water droplet is finally captured by the eliminator 18 and removed as drain water D. Therefore, the air (dehumidified cold air F6) that has passed through the eliminator 18 is in a state where it has been subjected to dehumidification as well as cooling.

(4) Heating by heat pipe In the present embodiment, the dehumidified cold air F6 then passes through the curved portion 13 and reaches the outlet 12 side, and reaches the condensing portion that is the other end side of the heat pipe 20. . Here, the dehumidified cold air F6 is heated by the heat medium M enclosed in the pipe, and is supplied to the target facility 2 as the dehumidified warm air F having a desired humidity and temperature. The heat medium M giving heat to the dehumidified cold air F6 means that the heat is taken away from the heat pipe 20, whereby the heat medium M at the outlet 12 is condensed and liquefied. It moves to the intake 11 side mainly through the wick layer W in the pipe 20.

  Further, in such a heat exchange system to which the heat pipe 20 is applied, the heat medium M in the heat pipe 20 works to precool the dust removal hot air F2 on the intake 11 side. From the viewpoint of M, this is heated and easily vaporized and moved in combination with the vacuum condition, and acts (heats) on the dehumidified cold air F6 on the outlet 12 side. At this time, the heat medium M is cooled and gaseous The heat medium M is liquefied and returned to the intake 11 side. As described above, the action of the heat medium M in the heat pipe 20 is a phase change between a liquid phase and a gas phase, and is heat exchange by using latent heat, so that the operation efficiency is excellent, and the intake 11 side (evaporation part) Thus, the dust removal hot air F2 can be sufficiently precooled, and the dehumidification cold air F6 can be sufficiently heated on the outlet 12 side (condensing part). Further, since the heat pipe 20 itself only forms a circulation flow by vaporization and liquefaction of the heat medium M enclosed inside, the heat pipe 20 itself is exceptionally efficient without requiring any power such as a pump for circulating the heat medium M. Is.

  Here, the arrangement of the heat pipe 20 will be described. In the embodiment shown in FIG. 1, a plurality of heat pipes 20 are provided for the counter-flowing dust removal hot air F2 and the dehumidification cold air F6. The heat pipe 20 on the upstream side in contact with the dehumidified hot air F2 is arranged on the downstream side, that is, in contact with the dehumidified cold air F6 on the outlet 12 side. Similarly, the heat pipe 20 that comes into contact with the dust-removing hot air F2 last on the inlet 11 side, that is, the downstream heat pipe 20 with respect to the dust-removing hot air F2, first comes into contact with the dehumidified cold air F6 on the outlet 12 side, that is, upstream. It is to be arranged on the side. With such an arrangement, the heat pipe 20 having the highest precooling evaporation temperature on the inlet 11 side is arranged at the position where the heating temperature is highest on the outlet 12 side, and the precooling evaporation temperature is on the inlet 11 side. The lowest heat pipe 20 is arranged at a position where the heating temperature is lowest on the outlet 12 side. As a result, the temperature applied to each heat pipe 20 can be leveled, and a sufficient cooling effect and heating effect can be expected.

Note that FIG. 1 is a skeletal view of the supply duct device viewed from above, and thus the arrangement of the plurality of heat pipes 20 is not clear, but in terms of heat exchange efficiency, for example, as shown in FIG. In addition, it is preferable to dispose a plurality of heat pipes 20 also in the vertical direction. In particular, in this case, by disposing the heat pipes 20 alternately with respect to the flow of the dust removal hot air F2 and the dehumidification cold air F6, that is, by disposing the heat pipes 20 disposed on the downstream side between the upstream ones. The heat exchange efficiency can be further improved.
Incidentally, it has been confirmed by the present applicant that the operating performance of the present apparatus, particularly the operating performance of the heat exchanger, is approximately twice as high as that of the conventional heat exchanger using sensible heat.

[Other Examples]
The present invention has the above-described embodiment as one basic technical idea, but the following modifications can be considered. That is, in the embodiment described above, in order to arrange the heat pipe 20 very reasonably, the curved portion 13 is formed in the flow path from the intake port 11 to the intake port 12, and the intake port 11 and the intake port are formed. 12 are arranged side by side. However, for example, as shown in FIG. 3, the duct body 10 can be formed substantially linearly without interposing the bending portion 13. In this case, the heat pipe 20 is formed as a long one so as to act on the inlet 11 and the outlet 12.

  Further, in the basic embodiment described above, the intake port 11 and the intake port 12 are provided side by side in a substantially horizontal manner, and the heat pipe 20 is also substantially horizontal so as to be substantially orthogonal to the air flow flowing through them. Arranged (see FIG. 4A). This is because the fins FI provided on the heat pipe 20 are provided almost vertically (to drop water droplets), promote circulation with liquefaction and vaporization of the heat medium M, and heat exchange can be performed more efficiently. However, the heat pipe 20 is not necessarily arranged almost horizontally. For example, as shown in FIG. 4B, the heat pipe 20 has an installation mode in which the outlet 12 side is directed upwards as much as possible. It is also possible to do this, and this is an inclination for promoting the movement of the heat medium M in the heat pipe 20. That is, since the heat medium M evaporates and vaporizes on the inlet 11 side and moves to the outlet 12 side, the inclined arrangement facilitates this upward movement, and the heat medium M is on the inlet 11 side. In this case, it is condensed and liquefied and moved to the intake port 11 side, so that the falling movement is facilitated by the inclined arrangement.

It is a plane sectional view showing the supply duct device of dehumidification air of the present invention skeleton. It is a perspective view which shows the arrangement | positioning aspect of a some heat pipe. It is a plane sectional view showing other examples which formed a duct body in the shape of a straight line. It is explanatory drawing (a) which shows the arrangement | positioning aspect of the heat pipe seen from the I direction in FIG. 1, and explanatory drawing (b) which shows the other arrangement | positioning aspect of the heat pipe seen from the same direction. It is a plane sectional view showing the conventional dehumidification air supply device skeleton.

1 Dehumidified air supply duct device 2 Target equipment (cupola)
DESCRIPTION OF SYMBOLS 3 Blower 10 Duct main body 11 Intake port 12 Outlet 13 Curved part 14 Air filter 15 Dehumidifier 16 Primary cooling device 16a Evaporator 17 Secondary cooling device 17a Evaporator 18 Eliminator 20 Heat pipe C Container D Drain water F Dehumidification warm air F1 Ambient air temperature F2 Dust removal warm air F3 Pre-cooling air F4 Primary cooling air F5 Secondary cooling air F6 Dehumidification cooling air FI Fin M Heat medium W Wick layer

Claims (3)

One opening of the duct body is used as an air inlet, and the other opening is used as an air outlet.
Furthermore, a dehumidifying device is provided inside the duct body, and the area sandwiching the dehumidifying device is linked by a heat exchanger,
In the apparatus for dehumidifying the air from the inlet, leveling the temperature difference between the inlet and the outlet, and supplying air from the outlet to the target equipment,
The dehumidified air supply duct device, wherein the heat exchanger is formed by applying a heat pipe.   The duct main body is bent in the middle between the intake and the outlet, and the intake and the outlet are substantially arranged side by side, and a plurality of heat pipes are arranged in the parallel arrangement range. The dehumidified air supply duct device according to claim 1.   3. The dehumidified air supply duct device according to claim 2, wherein the plurality of heat pipes are arranged so that temperatures acting on the pipes are balanced.

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