JPS59195095A - Stationary type total heat exchanger - Google Patents

Abstract

PURPOSE:To increase the heat exchange efficiency of the titled heat exchanger and to miniaturize the heat exchanger by a method wherein porous hollow fibers having fine pores in the wall surfaces thereof are bundled, both ends of the bundled fibers are sealed and a secondary gas is introduced into gaps among the hollow fibers. CONSTITUTION:The porous hollow fibers 5 having fine pores in the wall surfaces thereof are bundled and housed into a vessel 7 and covers 16 and 17 having an inlet port 14 and an outlet port 15, respectively, for a primary gas A flowing through the hollow sections in the hollow fibers 5 are bonded to both ends, respectively, of the vessel 7. The primary gas A is introduced from the inlet port 14 and discharged from the outlet port 15 while the secondary gas B is introduced from the inlet port 12 and discharged from an outlet port 13 through the gaps among the hollow fibers 5. As a result, the density of the total heat transfer area becomes high so that the full heat exchange efficiency is increased and the heat exchanger can be miniaturized.

Description

[Detailed Description of the Invention] This invention is a ventilation system that simultaneously supplies fresh outside air and exhausts dirty/indoor air, or a fresh air outlet for an air conditioning machine room in a building. Total heat exchanger Kl: 5t, used for total heat exchange of indoor air), etc.

In particular, by bundling and using a large number of porous hollow tf5r threads ff with small diameters, the areal density of the total heat transfer surface can be increased by a large width (C), resulting in high total heat exchange efficiency and miniaturization of the total heat exchanger. There are seven components to the static total heat exchanger.

In recent years, as living spaces have become more insulated and airtight in order to improve heating and cooling effects, the importance of ventilation has been increasingly recognized. An effective method for ventilation without impairing the heating and cooling effect is to exchange heat between exhaust air and supply air. At this time, if temperature (sensible heat) and humidity -'<latent heat) can be exchanged at the same time, the effect will be significant. As a response to this request.

Conventionally, there is a stationary total heat exchanger C Patent No. 9, which exchanges total heat between supply air and exhaust air through a partition plate, as shown in the perspective view of Fig. 1.
No. 30986). As shown in Figure 1, this static total heat exchanger consists of a flat partition plate (1) and a corrugated spacer plate (1).
2) are alternately stacked, and the directions of the spaced plates are orthogonal to each other every other step, thereby forming an air supply flow path (3) and an exhaust air flow path (4). (A) indicates the flow of intake air, and ① indicates the flow of exhaust air. At this time, it is preferable to narrow the interval between the partition plates because the number of stages increases and the total heat exchange area increases.
Bolted ones are commercially available. It is preferable that the pitch of the waveform of the spacer plate be narrower, since this increases the heat transfer coefficient between the air flow and the partition plate, and 4 ram types are currently on the market.

Due to its structure, this static total heat exchanger cannot have the supply air and exhaust air flow paths facing each other, but the efficiency of temperature and humidity exchange is better with counterflow than with orthogonal or oblique flow. Therefore, the present inventors developed a static total heat exchanger with a large area density of total heat transfer surface area t.

We have conducted intensive research to develop a total heat exchanger that preferably has air supply and exhaust air flow paths facing each other, achieving high total heat exchange efficiency and miniaturization of the total heat exchanger.

This invention was made as a result of the above object.

Bundle porous hollow H・ν1tft with pores on the wall,
Both ends are sealed leaving a hollow part, and the primary gas is introduced from one end through the hollow part and discharged from the other end, and passes through the hollow C/ν combination gap from the other end. Secondary gas is introduced so that the temperature (sensible heat) and humidity (latent heat) of the primary gas and secondary gas are
By doing so, we aim to provide a static total heat exchanger that can increase the area density of the total heat transfer area, achieve good total heat exchange efficiency, and achieve a small size. be.

In addition, the secondary gas is introduced from the other end side, flows through the hollow fiber gaps, and is discharged to the one end side, so that the primary gas flow and the secondary gas flow are opposed to each other. The present invention aims to provide a static total heat exchanger that can achieve a high total heat exchange rate.

Hereinafter, embodiments of the present invention will be explained based on the drawings.

Fig. 2 is a prayer view showing a state in which the hollow fiber bundle is housed in a container f. In the figure, (5) is a porous hollow fiber with pores on the wall surface, the pore diameter is 50 to 1000 A, and the inner diameter is 0 to 1.
Porous hollow fibers made of polyethylene, polypropylene, cellulose acetate, or the like and having a wall thickness of 10 to 100 tirne are used. (Hereinafter referred to as "hollow fiber") Hollow fiber (5) As the micropores on the wall become larger, not only water vapor but also air will migrate, so u+oo
Up to X is the practical limit, and holes below 50A are actual η
It is thought that there are no holes. And from the standpoint of total heat transfer ratio or heat transfer coefficient, it is better to make the inner diameter 6 cm smaller.
511. If the total heat transfer surface is more than mrn, the area density of 1t becomes too small, so the upper limit is 5 mm, and if it becomes too thin, the pressure loss increases, so the lower limit is 01 mrn.Furthermore, the wall thickness should be within the range allowed by mechanical strength. Thinner is preferable and practical [10 μm to 100 μm is used. (
6) is a resin layer that fixes the hollow fiber (5) to the container and separates the primary gas from the secondary gas; the resin used is polyurethane, epoxy resin, etc. that hardens at room temperature.

(7) is both; t: @ (8), (9) is opening this 1
Entrance tJ camphor and exit (11
) and is a cylindrical container.Since the pressure does not change in the container, a general-purpose plastic container is used. The secondary gas inlet (10 D is provided with 1 inlet channel (secret, (1 armor) at the top and bottom in Figure 1, and 1 outlet channel is provided at the top and bottom in Exit I in the figure.

When making a total heat exchanger according to an embodiment of this invention, first cut the porous 'U hollow' +p fiber (5) having pores on the wall to a predetermined length. @L,! After heat-sealing the ends of 1Iiii and closing them, treat 1c7n from both ends with resin. 2
Make it thicker. At least 1,000 hollow fibers (5) made of thickened 7i, I, and 4 are bundled together and stored in a container (7), and both ends of the fibers are soaked in a monomer solution of t, l# fat. Let it harden. After curing, the circular end face is cut at one place (at the position indicated by the dashed line in the figure) to open the hollow part of the hollow fiber (5). Next, at both ends of the container (7), there are inlets and outlets for the primary gas that pass through the hollow part of the hollow fiber (5) +14), fl! 9
The static total heat exchanger shown in the cross-sectional view of Fig. 3 is obtained by joining the lid (lli) and (Iη) with adhesive or by cutting a screw groove. Flow to the other end, CB) represents the flow of the secondary gas from the other end to the one end f. The secondary gas passes through the gaps between the hollow fibers, and these gaps can be adjusted depending on the degree of thickening when both ends of the hollow fibers are treated with resin. Entrance passage Q2+
The secondary gas entering from , az enters the cylindrical container (7) from the inlet Q (e) provided around the entire curved end of the cylindrical container (7), and passes through the gaps between the hollow fibers in the longitudinal direction of the hollow fibers. Outlet Q provided all around one end of the flow 2 cylindrical container (7)
l) Exit through [1 passage and 0 lines. The entrance and exit (Ill) were provided all around the cylindrical container was 2.
This is to allow the flow of the secondary gas from the other end to the one end to flow along the longitudinal direction of the hollow wire 41F as much as possible, and to face the primary gas as much as possible.

In this way, cold and dry air from outside in winter is passed as a primary gas through the counterflow type static total heat exchanger, and as a secondary gas, for example, warm and humid air from a heated room is passed. When air is passed through, temperature (sensible heat) and moisture (latent heat) are exchanged simultaneously through the walls of the porous hollow Kasumi fibers, and the primary gas is warmed, humidified, and supplied into the room. In the summer, the 11th-grade air is cooled, dehumidified, and then supplied into the room.In addition, at this time, not only water vapor but also secondary gas is exhausted through minute holes in the wall. Next, we move on to gas supply.

Push the primary gas side using the primary gas blower fan r.

By using a suction method on the secondary gas side using a secondary gas blowing fan, the static fF and f on the primary gas side can be raised by slightly π to suppress the transfer of defecation, and only fresh outside air is supplied into the room. be done. In addition, water vapor is hardly affected because the wave number changes due to the difference in water vapor partial pressure.

The present invention will be described below with reference to examples and examples.

Example 1 A porous hollow fiber made of polyethylene (5) with an inner diameter of 2 mtn and an outer diameter of 2.2 bar, which has countless fine pores of about 5 mm in the vertical direction and 100 χ in the horizontal direction on the wall surface, is made in length. 21m
After cutting it into sections and heat-sealing both ends, 1 cm from the end was immersed in a resin solution to make it slightly thicker. Approximately 1,000 of these hollow fibers (5) are bundled into a shape with a diameter of 10C as shown in Figure 2.
m, length 20C1n container (stored in force. Depth 2cn
One end of the container (7) was immersed in a Petri dish containing a stock solution of polyurethane at room temperature for 1 hour. Tighten the other end in the same way. The end of the hollow fiber (5) was opened by cutting 1 m from the end with a cutter. Next, as shown in Fig. A counterflow type static total heat exchanger was fabricated by joining the lids (11, 07) with adhesive.

Example 2 Wall surface - Vertical direction is sea
A 2 mm polypropylene medium fiber f5 of 21'L was cut into lengths 2 (lcrn), both ends were heat-sealed, and about 1 m from the end was immersed in a resin solution to make it slightly thicker.

Approximately 5 ounces of these porous hollow fibers (5) were bundled and stored in a container (7) K having a diameter of 10 cm and a length of 20 cm as shown in FIG. One end of the container (7) was immersed in a Petri dish containing a polyurethane stock solution to a depth of about 2 m and hardened at room temperature for 1 hour. The other end was also opened in the same manner.The end of the hollow fiber (5) was opened by cutting 1 (Ill) with a cutter from the end surface.Next, as shown in Figure 3, By attaching the plastic lids (16) and Q7) that form the air inlet and outlet at both ends with adhesive, a chain counterflow type static exchanger was created (
J I did.

Example 3 A large hole F with an average pore diameter of about 100 A + y on the wall surface
Holding K, inner diameter 1): Q, 5'11. iii, the outer diameter is Q, 5 rrc-n A hollow f-no.

Both ends were heat-sealed and immersed in a 4al') It'i bath solution to make the 11th section slightly thicker. This porous trading hollow book &
1tifA (one bundle of about 5AAA, 20 crury with a diameter of 5 crn and a length as shown in Fig. 2) was stored in a container (1i Vc. 2 cm deep, 8 Vc). One end was soaked and cured for 1 hour at room temperature.The other end was squeezed out in the same manner.

Or 25-10 Theoretically, the temperature exchange efficiency should be the same no matter which formula is used, but in reality they differ somewhat, so the average value was calculated. The humidity exchange rate is calculated through the following steps 1jjq. Saturated water vapor pressure (P'
). Relative humidity RHVC Water vapor pressure (Pl is expressed by the following formula.

H (m7nH9) 100 By measuring atmospheric pressure (π), absolute humidity (X) is calculated from the following formula.

X =, 0.622 X (/'9-H2°
'Icg-dry a 1r) π-P If the atmospheric pressure is 760 gLmH9, the primary gas and
The absolute humidity of the following gases is 3.19×10 and 1.60×10, respectively.

The absolute humidity (Xl and X2) at the outlet of the primary gas and secondary gas was determined from the above-mentioned method 1ilfi K, and the humidity exchange efficiency was calculated using the linear equation.

Alternatively, in the case of a total heat exchanger that exchanges temperature (sensible heat) and humidity (latent heat) at the same time, these can also be collectively expressed as the Nckleby exchange efficiency. The enthalpy of the primary gas and the secondary gas are 41 and 15.8 K cal/lc9-, respectively, by determining the temperature and absolute humidity of the cloudy air.
The enthalpy exchange efficiency (total heat exchange efficiency) was calculated from the quadratic formula by determining the enclaves (11 and 12) at the outlet of the primary gas and secondary gas with d ry a i r o + i + a-, '4. .

Alternatively, in the case of humidity exchange efficiency and enthalpy exchange efficiency, the average value of the above two equations was taken. In order to make the measurement conditions the same, in the reference example, the air volume of the primary gas and secondary gas was set to 1'OO
m"/fi, and in the case of the example, the air volume was proportional to the ventilation cross section. The measurement results of air volume and each exchange efficiency are shown in Table 2.
Shown below.

Table 2 As is clear from Table 2, the temperature exchange efficiency obtained in the example of the present invention is superior to 80 or more, compared to 15% in the reference example. The humidity exchange efficiency was also improved by 1 to 5% compared to 65% in the reference example.

As a result, the enthalpy exchange efficiency was found to be improved by 4 to 8 times compared to the reference example of 72 times.

From Table 1, it can be seen that as the inner diameter of the hollow orange fiber decreases, the area density of the total heat transfer area increases, so each exchange efficiency improves greatly.However, as the inner diameter becomes smaller, the pressure loss during air blowing increases. Practically speaking, it is preferable that the inner diameter is one diameter or more.

The static total heat exchanger according to this invention has a unique structure.

It is not limited to a cylindrical shape, but can also be a rectangular parallelepiped.

In particular, the performance of the total heat exchanger does not change even if the cross-sectional shape of the ventilation section is a narrow rectangular parallelepiped, so it is possible to reduce the thickness required for recent ventilation systems, and the total heat exchanger container can be used as a blower or It can also be integrated with the ventilation duct, making the ventilation system thinner.

It is also very effective in miniaturization.

As explained above, according to the present invention, porous hollow fibers having pores on the wall are bundled, both ends are sealed leaving a hollow part, and secondary gas is introduced from one end to pass through the hollow part. The areal density of the total heat transfer area is increased by introducing and discharging from the one end side to exchange temperature (sensible heat) and humidity (latent heat) between the primary gas and the secondary gas. Therefore, it is possible to provide a static total heat exchanger that can realize high total heat exchange efficiency and miniaturization. Also, a secondary gas is introduced through the blade on the other end, and flows through the hollow fibers in the gaps between the hollow Kasumi fibers, and the above-mentioned - 1f! Since the primary gas flow and the secondary gas flow can be made to oppose each other by discharging the gas to 11, it is possible to provide a stationary total heat exchanger with an even higher total heat exchange coefficient.

[Brief explanation of the drawing]

FIG. 1 is a perspective view showing the structure of a conventional cross-flow type static total heat exchanger, and FIGS. 2 and 3 show a counter-flow type static total heat exchanger according to an embodiment of the present invention. This is a cross-sectional view, and Figure 2 shows a state in which two bundles of hollow fiber bundles are stored in a container in the middle of the manufacturing process, and a third one.
The figure shows the completed state. In the figure, (1) is a partition plate, (2) is a spacing plate, (3)
is the supply air flow path, (4) is the exhaust flow path, (a) is the supply air flow (9) is the exhaust flow, (5) is the porous hollow fiber with pores in the wall, ( 6) is a resin layer, (7) is a container, f
lFl+, tl++ are secondary gas inlets and outlets;
Reference numeral 51 represents the inlet and outlet of the primary gas, (16), f+7) represents the lid, (A) represents the flow of the primary gas, and (B) represents the flow of the secondary gas. Agent Masao Futaiwa

Claims (1)

[Claims] fi+ A bundle of porous hollow fibers containing pores on the wall surface. Both ends are sealed leaving a hollow part, and the primary gas is introduced from one end and discharged from the other end, and the second gas is passed through the gap between the hollow fibers from the other end. A static total heat exchanger in which temperature (sensible heat) and humidity (latent heat) exchange is performed between the primary gas and the secondary gas by introducing secondary gas and discharging it from the one end side. (2) In the matter described in item 1 of the scope of patent 8rj. A static total heat exchanger in which the diameter of the pores is 50 to 1000 A. A static total heat exchanger in which the introduced secondary gas flows in the longitudinal direction of the hollow fibers through the gaps between the hollow fibers and is discharged from the one end side. (4) Claim No. 1jn The hollow fiber has an inner diameter of 0.1 to Q
, 5 mm, and a static total heat exchanger with a wall thickness of 10 μm to 100 μm. (5) In the product described in any one of claims 1f and 4, the hollow portion! A static total heat exchanger whose fiber material is polyethylene, polypropylene, or cellulose acetate.