WO2003031029A1 - Steam movement control device - Google Patents

Abstract

A steam movement control device capable of adjusting the movement directions and movement amounts of steam and air, preventing separating membrane rotating bodies from being clogged, and increasing a steam moving treatment capacity, wherein a first closed space (11) and a second closed space (21) are allowed to communicate with each other through a forward side ventilation passage (22) and a return side ventilation passage (23), a plurality of separating membrane rotating bodies (4) are axially arranged on a rotating shaft (5) parallel with each other in the second closed space, the separating membrane rotating bodies are formed by coaxially arranging, on the rotating shaft, tubular membranes (40), (41), and (42) with different diameters formed of membrane bodies having air permeability and moisture permeability and having different membrane hole diameters and different front and rear surface areas, a plurality of small chambers (61), (62), and (63) divided by the tubular membranes are formed in the separating membrane rotating bodies, suction fins (71), (72), and (73) are installed in the small chambers, a centrifugal fan (8) is installed on the rotating shaft, and the innermost small chambers in the separating membrane rotating bodies are allowed to communicate with the outside air (15) through an exhaust passage (51) formed in the rotating shaft.

Description

 Description Steam transfer control device

Technical field

 BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a water vapor transfer control device used as a humidity control device by controlling a moving direction of water vapor by a film having air permeability and moisture permeability and an arrangement thereof.

 Conventionally, as shown in FIG. 13, a plurality of small chambers 200, 201 partitioned by a membrane 100, 101, 102 having air permeability and moisture permeability are formed in a container 30 There is known a water vapor transfer control device formed between a closed space 301 formed inside a space 0 and outside air 302.

 Further, as a module using a hollow fiber membrane or the like, when schematically drawn to explain the basic principle, as shown in FIG. 14, cylindrical membranes 400 and 400 having different diameters are obtained. 2. Description of the Related Art Separation modules having a plurality of small chambers 50,000 and 501 divided by 1,402 are known.

 The water vapor transfer control device shown in Fig. 13 utilizes the permeation characteristics of water vapor and air during the separation process, adjusts the amount of water vapor movement in each of the small chambers 200, 201 to the fluctuation cycle of the outside air 302, and is sealed. The volume of the space 301 and the volumes of the small chambers 200 and 201 were determined to control the humidity of the closed space 301.

In the module structure shown in FIG. 14, a hollow fiber membrane is used so that the surface area of the membranes 400, 401, and 402 is not easily restricted in the process of separating water vapor. In this case, the gas to be separated must be pumped Yes, a separate pump was a necessary condition.

 The water vapor transfer control device having the basic structure as shown in Fig. 13 has the area of the membranes 100, 101, 102 with respect to the volume of the sealed space 301 to be humidified. However, it was more advantageous to set a smaller value for the purpose of temperature control.

 For this reason, there has been a limitation on the volume of the closed space 301 to be humidified. In addition, the condition of humidity control requires the temperature fluctuation of the outside air 302, and the pressure fluctuation of the enclosed space 301 utilizing the periodic fluctuation of the temperature and the rapid rise of the temperature is also used. In addition, there were restrictions on the humidity control time and the time during which the movement of water vapor could be controlled.

 The basic principle shown in Fig. 14 is based on the fact that hollow fiber membranes simply utilize the effect of ultra-separation, which forms a limit for water vapor separation, before and after the membrane as shown in Fig. 13. Because of the inferior temperature control capability, the concentration gradient utilizing the temperature fluctuation was pumped from the vent port 600 or suctioned from the vent port 61 from an externally installed pump, etc., and considered adiabatically. In some cases, the adiabatic cooling phenomenon or the adiabatic expansion phenomenon that occurred during these pressure fluctuations was used.

The present invention has been made in order to solve such a conventional problem. By rotating a separation membrane rotating body having a plurality of small chambers formed therein, water vapor transfer by the membrane body is performed by using a centrifugal pressure. By adjusting the angular velocity at that time, it is possible to adjust the moving direction and moving amount of water vapor and the moving direction and moving amount of air, and to prevent clogging of the separation membrane rotating body, and An object of the present invention is to provide a water vapor transfer control device capable of improving the water vapor transfer processing capacity by increasing the surface area of a membrane. Disclosure of the invention

 In order to solve the above-mentioned problems, the steam transfer control device of the present invention (Claim 1) is characterized in that the first closed space to be humidified and the second closed space formed inside the casing are on the outward side. Communicating through an airway and a return airway,

 In the second closed space, a plurality of separation membrane rotators are arranged axially on a rotation shaft,

 Each of the separation membrane rotators has air permeability and moisture permeability, and cylindrical membranes having different diameters formed by membranes having different pore diameters and different surface areas of the membrane on the front and back are arranged on the rotation axis. Formed with wicks arranged,

 A plurality of small chambers partitioned by each cylindrical membrane are formed in the separation membrane rotator, and a suction fin is attached to each of the small chambers.

 And a centrifugal fan is attached to the rotating shaft,

 The innermost chamber of the separation membrane rotator is configured to communicate with outside air via an exhaust passage formed inside the rotation shaft.

 In the water vapor transfer control device of the present invention, the separation membrane rotating body is formed by combining a plurality of rotating membrane members having different diameters, and each of the rotating membrane members is provided with an intake fin on the outer periphery of the disc-shaped frame. In addition, there is an aspect in which a cylindrical film is attached from above the intake fin (claim 2).

 Further, in the water vapor transfer control device of the present invention, there is a mode in which the intake fin is formed of a metal having a high heat conduction speed or a synthetic resin having a low heat conduction speed (claim 3).

Further, in the water vapor transfer control device of the present invention, a porous body formed of a metal having a high heat conduction speed or a synthetic resin having a low heat conduction speed is provided on the outer periphery of each cylindrical film between the cylindrical film and the porous body. There is a mode (Claim 4) in which the cable is stretched while maintaining an appropriate interval. Further, in the water vapor transfer control device of the present invention, there is a mode in which no accessory is attached to the outer surface of the casing (claim 5). BRIEF DESCRIPTION OF THE FIGURES

 FIG. 1 is a longitudinal sectional view showing a water vapor transfer control device according to one embodiment of the present invention.

 FIG. 2 is a schematic cross-sectional view of a separation membrane rotator provided in the water vapor transfer control device. C FIG. 3 is a schematic cross-sectional view showing a motion of steam in the rotator.

 FIG. 4 is a schematic cross-sectional view showing the movement of water vapor when an intake fin is provided. C FIG. 5 is a side view of a state where the membrane of the separation membrane rotator is cut and expanded.

 FIG. 6 is a schematic diagram showing pressure fluctuations as the rotation speed changes when a separation membrane rotator in which a third membrane is disposed in the innermost chamber and a second membrane is disposed in the middle chamber is rotated.

 FIG. 7 is a schematic diagram showing the temperature fluctuation when the rotation speed of the separation membrane rotating body in which the third membrane is disposed in the innermost chamber and the second membrane is disposed in the intermediate chamber is changed with the rotation speed.

 FIG. 8 is a schematic diagram showing the amount of movement of water vapor of the membrane arranged in each separation membrane rotator over time.

 FIG. 9 is a schematic diagram illustrating the theoretical value of the amount of water vapor transfer of the membrane over time when the amount of water vapor transfer of the membrane when each rotating body of the separation membrane is stationary is calculated from the actually measured values.

 FIG. 10 is a schematic diagram showing the amount of change in water vapor transfer of the three main films calculated over time, using the films as resistors.

 Fig. 11 shows the ratio of the water vapor permeation mass calculated over time with respect to the change in water vapor transfer of the three main membranes shown in Fig. 8, based on the small chamber in which the three main membranes are arranged as one resistor. FIG.

Fig. 12 shows the outermost part of the rotating body of the separation membrane from the innermost chamber when the rotating body is stationary. 5 is a schematic diagram showing a change in a water vapor transfer amount of a film to a small chamber with time.

 FIG. 13 is a schematic sectional view showing a conventional water vapor transfer control device.

 FIG. 14 is a schematic sectional view showing a conventional water vapor transfer control device. BEST MODE FOR CARRYING OUT THE INVENTION

 Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the specific configuration of the present invention is not limited to the following embodiment.

 FIG. 1 is a cross-sectional view showing a water vapor transfer control device according to one embodiment of the present invention, and FIG. 2 is a schematic cross-sectional view of a separation membrane rotator provided in the water vapor transfer control device. In the figure, reference numeral 1 denotes a box to be subjected to humidity control, and a first closed space 11 formed inside the box 1 and a second closed space formed inside a casing 20 of the steam transfer control device 2. The space 21 communicates with the outgoing air passage 22 and the return air passage 23.

 In the second closed space 21, a plurality (four in the drawing) of separation membrane rotators 4 are arranged axially on a rotation shaft 5.

 Each of the separation membrane rotators 4 is composed of a plurality of (three in the drawing) cylindrical membranes 40, 41, and 42 having different diameters formed of a membrane having air permeability and moisture permeability. As shown, it is formed concentrically on the rotating shaft 5 that is supported by the casing 20.

In this case, the separation membrane rotator 4 includes a plurality of small chambers partitioned by the cylindrical membranes 40, 41, and 42, that is, an outer small chamber 61, an intermediate small chamber 62, and an innermost small chamber 63. The suction fins 7 1, 7 2, 7 3 are formed in each of the small chambers 6 1, 6 2, 6 3 in such a direction that air (including water vapor) is sucked in from the outside to the inside by the rotation ( (In the direction from the outer chamber 61 to the innermost chamber 63). It is sufficient that the number of the small chambers is at least one. In the case of one chamber, the small chambers are divided using two cylindrical membranes having different diameters.

 In addition, the protrusion width of the intake fins 71, 72, 73 may be formed so as to completely divide the inside of each of the small chambers 61, 62, 63, or may be incompletely defined. It may be formed.

 Each of the separation membrane rotators 4 is composed of a large-diameter rotary membrane member 4 a and a medium-diameter rotary membrane in a state where disc-shaped frames 45 a, 45 b, and 45 c having different diameters are stacked via a packing 49. The member 4 b and the small-diameter rotating film member 4 c are combined to be concentrically arranged on the rotating shaft 5. In this case, when compression in the axial direction is applied to the packing 49, the packing 49 is deformed in the axial direction, so that the center for the concentric arrangement can be easily obtained. Alternatively, a circular flat packing may be sandwiched between the disc-shaped frame members 45a, 45b, and 45c. In this case as well, if it is inclined toward the center, the center for the concentric arrangement is obtained. Is easy to take. Also, an O-ring can be used instead of the packing.

 These rotating membrane members 4a, 4b, 4c are provided with suction fins on the outer periphery of the disc-shaped frame bodies 45a, 45b, 45c, which are the partition walls between the separation membrane rotating bodies 4, 4. 7 1, 7 2, 73 are attached, and cylindrical membranes 40, 41, 42 are attached from above the intake fins 71, 72, 73.

 The frame structure of the large-diameter rotary membrane member 4a (the same applies to the medium-diameter rotary membrane member 4b and the small-diameter rotary membrane member frame structure) is provided on the outer periphery of the disc-shaped frame 45a (see FIG. 2). (2 pieces) of intake fins 71 are attached, and the intake fins 71 have a skeleton structure in which the front ends of the intake fins 71 are connected to each other. This frame structure may be formed in a taper shape.

The intake fins 71, 72, 73 are made of metal or heat having a high heat conduction speed. It is formed of a synthetic resin having a low conduction speed.

 Since each of the membranes forming the tubular membranes 40, 41, and 42 has a low density, the heat transfer from the membrane to the air (water vapor) is small with respect to the heat conduction efficiency. Therefore, it is possible to adjust the heat conduction speed by forming the intake fins with high density (high heat conduction speed) metal or low density (low heat conduction speed) synthetic resin.

 Since the thermal conductivity and the electrical conductivity are almost the same, for example, metal deposition (measurement) is performed on the disc-shaped frames 45 a, 45 b, and 45 c of each separation membrane rotor 4. Processing may be considered.

 In addition, a centrifugal fan 8 is attached to the rotating shaft 5. In this case, the centrifugal fan 8 is attached to a side surface of the separation membrane rotor 4 facing the outward ventilation path 22 and the return ventilation path 23. I have.

 Due to the rotation of the centrifugal fan 8, air is circulated between the first closed space 11 and the second closed space 21 through the outward ventilation path 22 and the return ventilation path 23, The pressure is applied within 1. For this reason, the diameter of the return side ventilation path 23 is formed smaller than the diameter of the outward side ventilation path 22. In addition, the diameter of the return-side ventilation path 23 and the diameter of the outward-side ventilation path 22 are the same, and a flow-restriction valve (for example, a pinch valve or a needle valve) is provided in the return-side ventilation path 23. By making the outgoing side ventilation path 22 and the returning side ventilation path 23 common in this way, the cost of parts can be reduced.

The pressurization due to the rotation of the centrifugal fan 8 is limited by the compression capacity obtained by the rotation (angular velocity) of the centrifugal fan 8. And it is necessary to set the diameter of the return side ventilation path 23. The rotating shaft 5 has both ends supported by bearings 24 and 25 in a casing 20 and an electric motor 50 for driving is connected to one end thereof. The bearing 24 provided on the other end of the rotating shaft 5 is screwed into the casing 20 with a screw 26, and by applying a pulling force to the rotating shaft 5 by the movement of the screw 26, The radius of the rotating shaft 5 is prevented.

 It should be noted that a magnetic fluid can be used for the seal between the rotating shaft 5 and the dual bearings 24 and 25 so as to achieve airtightness.

 Further, an exhaust passage 51 is formed inside the rotary shaft 5, and the exhaust passage 51 is communicated with the innermost small chamber 63 of the separation membrane rotator 4 through a communication hole 52, and is rotated. The shaft 5 communicates with the outside air 15 through an exhaust port 53 opened at the end. Incidentally, the invasion of dust and insects into the inside of the device has a large effect on the water vapor transfer ability, such as causing clogging of the membrane. Air filters 17 are attached to 23 and insect repellent nets 18 are attached to the exhaust port.

 Further, the water vapor transfer control device of the present invention does not require auxiliary equipment such as a pump as in the prior art (FIG. 14), and therefore, the auxiliary equipment is attached to the outer surface of the casing 20. Absent. Therefore, there is no adverse effect due to noise or vibration from ancillary equipment such as a pump, and it is possible to provide a low-energy, low-energy water vapor transfer control device that saves energy.

 The casing 20 is provided with a heat insulating layer 20a. The heat insulating layer 20a insulates the outside air temperature and prevents dew condensation inside the apparatus due to a temperature change of the outside air 15.

It is also possible to form the casing 20 from a synthetic resin having a low heat conduction rate, using PE, PVC, other thermoplastic resin or thermosetting resin. Alternatively, it can be formed in a laminate structure.

 Each of the cylindrical membranes 40, 41, 42 constituting the separation membrane rotator 4 is formed by stretching a membrane on the intake fin. In order to prevent the cylindrical films 40, 41, and 42 from sagging, the outer periphery of 41, 42 was formed of a metal having a high heat conduction rate or a synthetic resin having a low heat conduction rate. A porous body 9 (mesh plate) is stretched between the tubular membranes 40, 41, and 42 with a slight space therebetween.

 It is preferable to reduce the mass of the membrane in order to increase the heat exchange efficiency, but in this case, the heat conduction efficiency is hardly affected by the material.

 Therefore, as a supplement to the adjustment of the surface temperature, the surface temperature is adjusted by using a porous material 9 made of a high-density (high heat conduction speed) metal or a low-density (low heat conduction speed) synthetic resin. At the same time, dripping of the tubular membranes 40, 41, and 42 is prevented.

 Nylon-based nonwoven fabric, polyolefin-based nonwoven fabric, PE porous membrane, polyurethane-based nonwoven fabric, and the like are used as the membrane used for each of the tubular membranes 40, 41, and 42, and the outer and inner surfaces thereof are used. One having a different surface area from the side surface is used.

 In this case, the cylindrical membrane 42 between the innermost chamber 63 and the intermediate chamber 62 and the cylindrical membrane 41 between the intermediate chamber 62 and the outer chamber 61 have a small inner surface area. A smooth surface (water-repellent surface) is used, the outer surface is used as a raised surface with a large surface area, and the outermost cylindrical film 40 is a smooth surface with a small outer surface and a surface with an inner surface. It is used with a large brushed surface.

When the outer side surface is formed as a brushed surface having a large surface area as in the case of the tubular film 42 and the tubular film 41, the brushed surface has a large surface area, so that the evaporation rate is increased and the temperature is reduced. This draws in water vapor, increasing the water vapor concentration and reducing And the movement of water vapor from the outside to the inside is promoted.

 Since the outermost cylindrical film 40 is likely to be clogged due to the adhesion of dust, the outer surface is made a smooth surface (water-repellent surface) having a small surface area to prevent the adhesion of dust.

 The shape of the pores of the membrane may be straight or tapered, and the amount of water vapor transfer depending on the moisture permeability or air permeability may be arbitrarily determined. is there. However, when considered adiabatically, when adiabatic compression occurs in the direction of movement and a temperature rise is obtained, water vapor is not easily condensed, so movement is difficult to suppress, but conversely, in the direction of movement. Adiabatic cooling occurs, dew condensation tends to occur due to temperature drop (due to dew point drop), and movement is easily suppressed. The water vapor movement control device of the present invention rotates the separation membrane rotator 4 to accelerate the water vapor movement of the membrane (cylindrical membrane) by using pressure increase by centrifugal force, and adjusts the angular velocity at that time. The main point is to adjust the moving direction and the moving amount of the water vapor and the moving direction and the moving amount of the air by performing the following. The relationship between the angular velocity of the separation membrane rotor 4 and the movement of the water vapor is described below. This will be described with reference to FIGS.

 The formula for calculating the pressure and temperature of the rotating body is as follows (see Fig. 3)

1) Conversion of rotation speed and angular velocity of mass point B

 Angular velocity: [r a d / s]

 Revolution N: [r pm]

 N [r p s] = Nx27r [r a d / s]

 2) Centrifugal force of constant velocity circular motion of mass point B in rotating system

F = m _v r ω ²

Centrifugal force of steam Β F: [m · kg · s one ^2] Mass of water vapor B m _v : [k]

 Radius r of rotating system: [m]

 Angular velocity: [rad / s]

3) Pressure generated by the centrifugal force of constant velocity circular motion Pressure is the force applied to a unit area, so the pressure in a small chamber is the centrifugal force per unit area.

S Pressure per unit membrane area P: [P a] = [m " ¹ ■ kg · s' ² ]

Film area S: [m ² ]

 Membrane height h: [m]

From 1), 2), 3), the relational expression between the pressure due to the centrifugal force and the rotation speed is m ,, rω 2

次に、状態方程式による圧力と温度の関係は、以下のような計算式になる 4) 状態方程式による圧力と温度の関係 P =

Next, the relationship between pressure and temperature by the equation of state is calculated as follows: 4) Relationship between pressure and temperature by the equation of state

 P V = nR T

The pressure P per unit membrane area: [P a] = [m- 1 · kg · s one ^2]

1 [atm] 2 1 0 13 2 5 [P a] Small chamber volume V: [m ³ ]

ν = πτ ² Ε

Molar number of water vapor η: [mo m _v

 n =

M, steam mass m _v : [kg]

Molar mass of water _{M v = 1 8. 0 1 5} 2 8 x 1 0 - 3 [k - mo one 1 gas constant R = 8. 3 14 5 1 0 [J ■ mo l "1 · K- 1]

 Temperature T: [Κ]

From 1), 2), 3), 4), the relational expression of temperature Τ, pressure Ρ, and rotation speed で in the rotating body of the separation membrane is as follows.

 PV = nRT

 PV

 T

 nR

M _v PV

 : —— -x

 R

 M,

上式により遠心力による回転数、 圧力、 温度の関係を示したが、 フィ ンを 組込んだ小室では、 フィンの係数 Kが上式で考慮され、 圧力、 温度に関する 値が変わってくる （図 4参照） 。 ^ x—xP

The above equation shows the relationship between rotation speed, pressure, and temperature due to centrifugal force. In small chambers that incorporate fins, the fin coefficient K is taken into account in the above equation, and the values for pressure and temperature change. 4).

In FIG. 5, the first film, the second film, and the third film indicate the type of the film, Three

S ₁ S ₂ and S ₃ indicate the membrane surface area of the compartment.

For example, in the case where three chambers are combined, as shown in FIG. 5, the surface area of the membrane can have a relationship of S i <S ₂ <S ₃ as shown in FIG. Also, the movement of water vapor in the film is determined by the area ratio,

The amount of water vapor transfer S xm _v S ₂ xm _v2 , S ₃ xm _v3 is obtained when m _v3 > m _v2 from the relationship between the fin coefficient K and the pressure due to centrifugal force by rotating the small chamber with the intake fin. To

S a xm _v 2 '> S! xm _v2 , S 3 xm _v3 '> S ₁ Xm _v3 .

 Also, three small chambers do not necessarily have to be arranged. For example, in a separation membrane rotator in which a third membrane and a second membrane are arranged in the innermost chamber and the middle chamber, the surface area and the water vapor mass have the following relationship.

S! = 27Γ r [m ² ]

S ₂ = 27rr ₂ h ₂ [ni ² ]

Water vapor mass of the second film: m _v2 [kg]

Water vapor mass of the third film: m _v3 [kg]

 Then

S ₁ xm _V 3 = 27rr ₁ h ₁ xm _v3 [kgXm ² ]

_{S 2 X m v 2 = 27Tr} 2 li 2 xm v 2 [kg Xm2]

 Or

S! Xm _v 2 = 2 K r _x h _l xm _v2 [kg xm ² ]

S 2 xm _v 3 = 2 Γ r 2 h 2 xm _v3 [kg xm ² ]

Also, m _v2 ≥m _v3 , S! ≤ S 2

Therefore, the condition that the water vapor mass of the second film and the third film becomes equal (no water vapor transfer)

m _v2 _27Γ r ₂ h ₂

m _v3 27Γ

が上式 を満たす際に、 第 2膜と第 3膜の水蒸気質量が等しくなり、 水蒸気の移動が とまりやすくなる。 And the water vapor mass m _v2 , m _v3 and the membrane surface area 27Γ r ₂ h ₂ , S

When satisfies the above expression, the mass of water vapor in the second film and the third film becomes equal, and the movement of water vapor is easily stopped.

In addition, when the separation membrane rotator is rotating, the pressure applied to the membrane is:

_{m v3 r 1 (6 0xNx2 ^} [m _, kg. s _ 2]

 27Γ

 Ρ! : Pressure applied to the third membrane

 r! : Innermost chamber radius

m _v3 : Third membrane water vapor mass

 hi: Height of the third membrane

 N: Number of rotations

Becomes

When the second membrane is placed in the intermediate cell,

_{m v2 r 2 (6 0xNx2 ^} [m _, kg. s _ 2]

2 it r ₂ h ₂

P ₂ : Pressure applied to the second membrane

r ₂ : middle chamber radius m _v2 : Second membrane water vapor mass

h ₂ : Height of the second membrane

 N: Number of rotations

As shown in FIG. 6, the pressure of the third membrane and the second membrane increases as the rotation speed of the separation membrane rotator increases.

 Also, when the separation membrane rotator is rotating, the temperature of the membrane is as follows when the third membrane is placed in the innermost chamber.

 -X

[,

P! : Pressure applied to the third membrane

 r! : Innermost chamber radius

m _v3 : Third membrane water vapor mass

 hi: Height of the third membrane

 N: Number of rotations

 Hj: Height of innermost compartment

_Mv : molar mass of water

7Γ: Pi T !: Temperature of the third film

 : The innermost chamber volume.

 When the second membrane is placed in the intermediate cell,

P ₂ V ₂ = n, RT ₂

Τ P ₂ V ₂

n ₂ R

 M,

XP _{2 2}

 m v2 R

 M, V

² , 'P

m _v2 R

M _v „7T r ₂ ² H ₂ m _v2 r ₂ (60χΝχ2; τ) ² []

X

m _v2 R 27Γ r ₉ h ₂

P 2 Pressure on the second membrane

 Γ 2 Middle chamber radius

m _v2 : Second membrane water vapor mass

 2: Height of the second film

 N: Number of rotations

H ₂ : Height of the middle compartment

_Mv : molar mass of water

 7: Pi

Τ _2: temperature of the second film

V ₂ : Middle chamber volume As shown in Fig. 7, the pressure of the third and second membranes rises as the rotating body of the separation membrane is raised.

 The dew point of water vapor decreases as the temperature decreases, and increases when the temperature increases. The pore size of the membrane that forms the boundary of water vapor movement is affected by the water absorption state of the membrane itself as the temperature changes. That is, when the temperature decreases, the film absorbs water, and when the temperature increases, the possibility that the film absorbs water decreases.

 When the film is thin, the temperature change due to the movement of water vapor is affected by the temperature relationship before and after the film, which is the boundary of movement.

When the moving water vapor is considered adiabatically, the dew point rises when it is compressed in the moving direction, and decreases when it is decompressed in the moving direction. When considered adiabatically, the above P and P ₂ are diagrams showing the change in pressure due to rotation (Fig. 6). With this change, T _{l 5} Τ ₂ (Figure 7).

 Therefore, when promoting the movement, the movement from the lower temperature to the higher temperature is superior, and in the case of the pressure, the movement from the higher pressure to the lower temperature is superior. The time change of the moving water vapor is controlled by the elongation of the membrane or the arrangement of the porous body that suppresses the elongation. The tension in the direction in which the centrifugal force is applied is suppressed, and the thermal conductivity of the porous body and the small chamber structure (rotating membrane member) is reduced. Consideration will be given to promoting the movement of water vapor.

In FIG. 1, the pressure in the space 21 is increased by the centrifugal fan 8, and at the same time, the pressure in each of the small chambers increases as the rotation speed increases, as described above. Therefore, the rise due to the centrifugal force and the mass of water vapor that can move are formed by the membrane that forms the boundary of the movement and the porous body and the small chamber structure (rotating membrane member), so the water vapor in the space 21 is compressed. The relational expression that promotes movement to the small room is considered adiabatically, 8 expression can be approximated calculated as equation shown in _{P 13 P 2, T 13 T} 2. (Reference: Pump Handbook, 2nd Edition, p 30, ISBN 4—8052—0 574—1 C 3053, Turbo Blower and Compressor p 144, I SBN4-33 9-04279-X)

 In Fig. 8, the vertical axis is the amount of water vapor transfer, the horizontal axis is the passage of time,

S i xm _v2 is the amount of water vapor transfer when the second membrane is used in the innermost chamber of surface area S, and S ₃ xm _v2 'is the water vapor transfer when the second membrane is used in the outermost chamber of surface area S ₃

S 丄 xm _v3 is the amount of water vapor transfer when the third membrane is used in the innermost chamber of surface area S i, and S 3 xm _v3 ^/ is the amount of water vapor transfer when the third membrane is used in the outermost chamber of surface area S ₃ Is shown.

Here, when steam moves from S ₃ xm _v2 ′ to S xm _v2 , the pressure in the small chamber changes as the small chamber rotates, and the temperature changes accordingly. Water vapor moves from higher energy to lower energy. In other words, there is a possibility that the pressure and temperature change depending on the degree of rotation of the small chamber, and the change determines the direction of water vapor movement.

 When the chamber is not rotating, the water vapor transfer mass of the membrane is, as shown in Fig. 9, the water vapor transfer amount of the film from 95% RH to 65% RH, and the water vapor transfer amount of the film from 50% RH to 65% RH. The difference in the amount of water vapor transfer is determined from the measurement results of, and the amount of water vapor transfer of the film from 65% RH to 65% RH is calculated from the transfer ratio calculation.

 In this way, the amount of water vapor transfer of the film from 65% RH to 65% RH where the water vapor concentrations before and after the movement of the first, second, and third films obtained by the water vapor transfer ratio are equal is obtained.

As a result, the permeation of the membrane itself due to the difference in surface area between the water repellent surface and the nonwoven fabric surface of the membrane Sex can be evaluated.

 The results are measured at 21 ° C and atatm in addition to the equivalent water vapor concentration.

 Therefore, in the case of a small chamber, a prestress is applied, so that a porous body can be used so that the permeation characteristics are hardly changed by the extension of the membrane.

In FIG. 8, the initial value was set to 0, and the amount of water vapor transfer was calculated as m _vi , m _{v 2} , and m _{v 3} for each film.

The values of m _vl , m _{v 2} , and m _{v 3 obtained} are shown in Fig. 10, where the vertical axis indicates the amount of fluctuation in water vapor movement, and the horizontal axis indicates the passage of time.

 When a porous body is used, if a substance with a high heat conduction rate is placed in an insulated space, it acts as a cooling body, and conversely, a substance with a low heat conduction rate is placed in the insulated space. It is known that when placed, it acts as a heat insulator.

 Therefore, a metal mesh such as a copper mesh and a stainless steel mesh can be considered as a substance having a high heat conduction speed, and it is known that the heat conduction speed is approximately proportional to the electric conduction speed. In addition, in order to suppress the growth of microorganisms, a method using oligo dna, a fungicide, or an artificial resin having fungicide may be used.

 Therefore, the charging phenomena due to oil, dust, sea salt particles, and other airborne particles in the exhaust gas mainly as water, steam, and impurities contained in the air due to the movement of the small chambers are caused by these porous materials. This can be prevented by electrically grounding.

Also, if a porous body made of a material with a high heat conduction rate is placed near the membrane, the amount of water vapor permeation can be suppressed, so that the movement by the partial pressure as shown below The inclination of each characteristic can be arbitrarily adjusted and set according to the arrangement of the porous body.

 When a highly water-absorbing substance, such as nylon, is used for the nonwoven fabric, it absorbs water, elongates the fiber, and the mass of the permeated water vapor decreases rapidly with the water absorption. On the other hand, substances having low water absorption, such as polyolefin-polyethylene and vinyl chloride, are unlikely to generate this water absorption, so that the permeation mass of water vapor is hardly changed by water absorption generated with a change in surface temperature. Therefore, considering the efficiency of heat transfer in a small room, in a building where steam is considered as a carrier for calorific value, a temperature drop occurs depending on the moving direction, and the steam changes into water as the small room rotates. It is possible.

 This method can be used for a place where a drain (drainage channel) can be secured, but the amount of movement depends on the centrifugal force accompanying rotation.

 Therefore, when it is not possible to secure a drainage channel, it is desirable to discharge water vapor as it is. In this case, it is necessary to arrange a substance having low water absorption in the constituent membrane of the small chamber.

First layer, second layer, and a third chamber of the steam moving amount m _vl array of film, m _v2, m _{v 3} m _vl values were calculated by combining _{+ 2 + 3} value reference, m a diagram was calculated as the water vapor transmission mass ratio ratio values _{vl + 2 + 3} m _v had respect m _v2, m _v3 shown in Fig 1.

Here, the vertical axis indicates the water vapor transmission mass ratio, and the horizontal axis indicates the passage of time. Steam passage weight ratios shown in Figure 1 1, between the U have U ₃ from the initial value, also U _{l 3} U ₃ from U _2, U _4, and in U _2, U ₄ and subsequent sections, the transfer characteristics There rows synthesis of entailment _{m v i / m v i +} 2 + 3, m v2 / m vl + 2 + 33 m v 3 / m v丄+ _{2 + 3} value, the first film, second film, The water vapor transmission coefficient of the small chamber in the arrangement of the third membrane is used. By using this water vapor transmission coefficient, it is possible to evaluate the permeability of the membrane itself due to the difference in the surface area between the water repellent surface and the nonwoven fabric surface of the membrane.

 FIG. 12 shows a case where the first, second, and third membranes are used in the small chamber, and is in a stationary state without rotating.

In the small chamber composed of the second and third membranes, pressure distribution occurs as shown in Fig. 12, and the separation effect changes due to the increase in pressure due to the aforementioned rotational force. Here, in the interval of X from the initial value, the energy relation of S ₃ xm _{v 2} ′ is higher than that of S xm _{v 3} . Therefore, the movement of the stationary state is changed in a time manner via the Y ₂ from X to Y _6. This is the case not consider the temperature change accompanying the rotation, if the temperature changes with the rotation, S ₃ xm _v pressure of the small chamber when performing steam movement is changed to S IXM _{v 2} from However, the temperature changes accordingly.

 Water vapor moves from higher energy to lower energy. In other words, the pressure and temperature change according to the degree of rotation of the small chamber, and the change determines the direction in which the water vapor moves. In addition, the effect of the fins in the small room promotes emission.

 Therefore, according to this water vapor transfer device, the gas that has entered the second enclosed space 21 from the outgoing air passage 22 by the rotation of the centrifugal fan 8 receives centrifugal force by the centrifugal fan 8 While pressurizing 21, it circulates from the return air passage 23 to the closed space 11 of the box 1 while encountering the rotation of the separation membrane rotor 4. Therefore, the higher the airtightness of the first enclosed space 11, the higher the circulation efficiency.

Then, in the separation membrane rotating body 4, each of the small chambers 61, 62, 63 is fractionated by the cylindrical membrane 40, 41, 42, so that the pressure can be increased by the centrifugal fan 8 rather than pressurized by the centrifugal fan 8. In the case of a low-speed rotation lower than that, since the movement of water vapor occurs from the outside to the inside (from the outer small chamber 61 to the innermost chamber 63), the innermost small chamber 63 and the exhaust passage 51 are formed. Decompression can occur. As the rotation fluctuates from low speed (small angular velocity) to high speed (high angular velocity), the surface of the separation membrane rotor 4 is cooled, and adiabatic cooling is performed in the order of the outer small chamber 6 1 → middle small chamber 6 2 → innermost small chamber 6 3. Occurs.

 Also, when the pressure increase in the second enclosed space 21 reaches a moderate angular velocity sufficient to exceed the pressure reduction in the exhaust passage 51, the water vapor flows from the outside to the inside rather than from the inside to the outside. Since the flowing one rises in dew point and is free from factors that hinder the passage of the membrane, the movement from the outer small chamber 61 to the innermost small chamber 63 gradually increases, and water vapor is released from the exhaust passage 51 to the outside air 1 5 can be discharged.

 Further, in the second closed space 21, the plurality of separation membrane rotators 4 are arranged side by side in the axial direction on the rotation shaft 5. Is improved.

 It is most appropriate that the water vapor transfer control device of the present invention be installed with the electric motor 50 side down. This is because when the water vapor changes into water in the process of moving the water vapor, This is to prevent the separation membrane rotating body 4 from being submerged. Note that the steam movement control device may be installed sideways, and in this case, the return side ventilation path 23 is installed so as to face down. Industrial applicability

As described above, according to the water vapor transfer control device of the present invention, since the configuration is as described above, by adjusting the angular velocity of the rotating body of the separation membrane, the moving direction and the moving amount of the water vapor can be adjusted, and the air can be adjusted. The direction and amount of movement can be adjusted. In addition, since a plurality of separation membrane rotating bodies are used and arranged in the axial direction on the rotating shaft, it is possible to improve the water vapor transfer capacity by enlarging the surface area of the membrane body. it can

Claims

The scope of the claims 1. The first sealed space to be humidified and the second sealed space formed inside the casing are communicated via an outgoing air passage and a return air passage,  In the second closed space, a plurality of separation membrane rotators are arranged axially on a rotation shaft,  Each of the separation membrane rotators has air permeability and moisture permeability, and cylindrical membranes having different diameters formed by membranes having different pore diameters and different surface areas of the membrane on the front and back are arranged on the rotation axis. Formed with wicks arranged,  A plurality of small chambers partitioned by each cylindrical membrane are formed in the separation membrane rotator, and a suction fin is attached to each of the small chambers.  And a centrifugal fan is attached to the rotating shaft,  A water vapor transfer control device, wherein the innermost chamber of the separation membrane rotator communicates with outside air via an exhaust passage formed inside the rotation shaft. 2. The steam transfer control device according to claim 1, wherein the separation membrane rotating body is formed by combining a plurality of rotating membrane members having different diameters, and each of the rotating membrane members has a suction hole on an outer periphery of the disc-shaped frame. A water vapor transfer control device in which fins are attached and a tubular membrane is attached from above the intake fins.  3. The water vapor movement control device according to claim 1 or 2, wherein the intake fin is formed of a metal having a high heat conduction speed or a synthetic resin having a low heat conduction speed. 4. The water vapor transfer control device according to claim 1, 2, or 3, wherein a porous body formed of a metal having a high heat conduction rate or a synthetic resin having a low heat conduction rate is provided on the outer periphery of each cylindrical film. With a slight distance between Motion control device.  5. The water vapor transfer control device according to claim 1, 2, 3 or 4, wherein no accessory is attached to the outer surface of the casing.