JP4727365B2 - Ventilation system design method and building ventilation system - Google Patents

Description

  The present invention relates to a ventilation system design method and a building ventilation system, and more particularly, to a ventilation system design method for ventilating an interior of a building using an air supply means and an exhaust means in a building in which a heating element is housed. Relates to the ventilation system.

Conventionally, as a building ventilation facility (ventilation system) that houses various heat generating devices (heating elements) such as a garbage melting furnace, an air supply means having an air supply fan (blower) and an air supply duct, and an exhaust such as an exhaust monitor A device using an exhaust means having an opening (exhaust port) is known (for example, see Patent Document 1).
In the ventilation facility described in Patent Document 1, an air blower is connected to an air supply pipe opened on the outer wall of a building, and outside air sucked through the air blower is sent to an air supply duct, and an outside air outlet of the air supply duct. It is comprised so that external air may be supplied toward a heat generating body from. The air supply duct is disposed so as to surround the heating element at a position below the heating element, and the outside air outlet is provided so as to blow outside air upward toward the heating element. The heated air can be efficiently raised and exhausted from the exhaust port.
Such conventional ventilation equipment is based on the heat transfer due to the temperature difference between the surface temperature of the heating element and the room temperature under the condition that the room temperature of the building is fixed to a predetermined value (for example, 30 ° C.). The calorific value is calculated, and based on the calorific value, the temperature difference inside and outside the building is designed to be a predetermined value (for example, 15 ° C.) or less. In the conventional ventilation equipment, the room temperature and the surface temperature of the heating element are fixed, so that the ventilation volume is constant, that is, constant air volume ventilation, regardless of changes in the outside air temperature (seasonal or daytime / nighttime temperature difference). A general design method is common.

JP 11-248219 A

However, in the conventional ventilation equipment, since the air supply means is configured with a blower and an air supply duct, the equipment cost for installing these and the construction cost for securing the installation space are enormous. There is a problem of becoming. Furthermore, since electric power for driving the blower is required, there is a problem that energy saving is hindered and the running cost of the ventilation facility is disadvantageous.
Furthermore, in the conventional ventilation equipment design method, the calorific value is calculated under the condition that the room temperature is fixed, so it is difficult to properly evaluate the calculated calorific value and the buoyancy due to the temperature distribution of the inside air. There is also a problem that a reasonable ventilation volume cannot always be set.

  An object of the present invention is to provide a ventilation system design method and a building ventilation system capable of rationally setting the facility cost, the construction cost, the running cost, and the ventilation amount.

The ventilation system design method according to claim 1 of the present invention is a ventilation system design method for ventilating an interior of a building using an air supply means and an exhaust means in a building in which a heating element is housed. The air means is constituted by an air supply opening provided at the lower part of the building, and the exhaust means is constituted by an exhaust opening provided at the upper part of the building, and the opening area of each of the air supply opening and the exhaust opening is determined. Based on the included opening conditions and the temperature distribution of the inside air in the height direction of the building and the buoyancy calculated from the temperature distribution, the ventilation amount supplied from the supply opening and exhausted from the exhaust opening is calculated. a method of, and inside air temperature distribution assumed temperature distribution assumption instructions on the height direction of the building, based on the temperature distribution of the inside air, to calculate the calorific value distribution regarding the height direction inside the building A calorific value distribution calculating procedure, a total calorific value calculating procedure for calculating the total calorific value in the building based on the calculated calorific value distribution, and a required total ventilation required based on the calculated total calorific value The required total ventilation calculation procedure for calculating the temperature, the temperature distribution calculation procedure for calculating the temperature distribution of the inside air based on the calculated required total ventilation, and whether the temperature distribution of the inside air calculated by the temperature distribution calculation procedure has converged A first determination procedure for repeatedly executing the heat generation amount distribution calculation procedure, the total heat generation amount calculation procedure, the required total ventilation amount calculation procedure, and the temperature distribution calculation procedure; Based on the temperature distribution of the inside air determined to have converged in the procedure, the buoyancy calculation procedure for calculating the buoyancy generated in the inside air of the building, the driving force obtained by the buoyancy of the inside air calculated by the buoyancy calculation procedure, and the opening strip The actual ventilation volume calculation procedure for calculating the actual ventilation volume based on the above, and whether the calculated actual ventilation volume exceeds the required total ventilation volume calculated in the required total ventilation volume calculation procedure, And a second determination procedure for causing the actual ventilation volume calculation procedure to calculate the actual ventilation volume based on the reset opening condition when the required total ventilation volume is not exceeded .

According to the design method of the ventilation system described above, the temperature distribution of the inside air in the height direction is appropriately evaluated in the building where large-capacity heating equipment such as a refuse melting furnace and incinerator is arranged, and the temperature distribution The substitution type gravity natural ventilation system that can calculate the buoyancy of the inside air due to the temperature stratification with high accuracy, and uses the driving force obtained by the buoyancy to supply the outside air from the supply opening and exhaust the inside air from the exhaust opening Can be built. Accordingly, it is not necessary to use a blower and an air supply duct as the air supply means as in the conventional ventilation equipment, and the equipment cost for installing these and the construction cost for securing the installation space can be reduced. since the power for driving the is not necessary, it is possible to promote and running cost of suppressing energy savings. In addition, by adopting a replacement gravity natural ventilation system, even if the heat generation amount increases due to changes in the specifications of the heating element, the temperature of the inside air increases as the heat generation amount increases, so the buoyancy increases and the ventilation amount increases. Therefore, the influence of a decrease in ventilation efficiency due to an increase in calorific value can be suppressed as compared with mechanical ventilation.
In the ventilation design, by setting the temperature distribution of the inside air, the actual temperature stratification state in the building can be simulated with high accuracy, and the ventilation amount based on the buoyancy of the inside air can be accurately calculated. . That is, according to the applicant's research, the total calorific value inside the building depends on the ambient temperature (outside temperature and room temperature), and this ambient temperature, that is, the temperature distribution of the inside air, is very important in calculating the buoyancy of the inside air. Because knowledge was obtained, buoyancy and ventilation volume can be calculated more accurately than when calorific value is calculated under the condition that the room temperature is fixed as in the design of conventional ventilation equipment, Natural ventilation system can be rationally designed.

Further , the first determination procedure repeatedly executes the calorific value distribution calculation procedure, the total calorific value calculation procedure, the required total ventilation rate calculation procedure, and the temperature distribution calculation procedure until the temperature distribution of the inside air converges. It is possible to accurately calculate the actual ventilation volume due to indoor temperature stratification and buoyancy. Here, the convergence of the temperature distribution of the inside air is that the difference or ratio with the temperature distribution of the inside air assumed in the temperature distribution assumption procedure is the first temperature distribution calculation procedure among the temperature distribution calculation procedures repeatedly executed. Judged by being within the predetermined value, or in the second and subsequent temperature distribution calculation procedures, the difference or ratio with the temperature distribution of the inside air calculated in the previous temperature distribution calculation procedure is within the predetermined value. It is judged by.
In addition, calculate the calorific value distribution and total calorific value from the temperature distribution of the inside air, calculate the required total ventilation, and set the opening condition so that the actual total ventilation exceeds the required total ventilation by the second judgment procedure. Thus, it is possible to set a reasonable opening condition, that is, the opening area of each of the supply opening and the exhaust opening while ensuring ventilation efficiency.

Furthermore, the ventilating system design method according to claim 2 of the present invention is the ventilating system design method according to claim 1, wherein the calorific value distribution in the height direction of the building interior and the total of the building interior The calorific value is calculated by the equation (1), where q _i is the calorific value of the building inside the i-th floor and Q is the total calorific value of the building, where subscript I represents the floor or hierarchy (i = 1, 2, 3...), T _j is the surface temperature of the heating element, t _hi is the temperature of the inside air at the i floor of the building, and a _ij is at the i floor. The surface area of the heating element at the surface temperature tj, α is the heat transfer coefficient, and c _i is a component that does not depend on the room temperature in the amount of heat generated in the i-th layer .

Furthermore, the ventilating system design method according to claim 3 of the present invention is the ventilating system design method according to claim 1 or 2 , wherein the ventilating system design method is provided outside the building via the air supply opening and the exhaust opening. A third determination procedure for determining whether or not the volume of the output sound is lower than a preset reference value, and the volume of the sound output outside the building in the third determination procedure is a reference value; If not lower, the ventilation volume is calculated based on the effective opening area calculated by the calculation condition including the reset opening condition and the air resistance of the silencer provided in at least one of the air supply opening and the exhaust opening. It is characterized by doing.
Here, calculation conditions for the effective opening area include, in addition to the opening condition and the air resistance of the silencer, air resistance by an opening element such as a wire mesh provided in the air supply opening and exhaust opening, and before and after the air supply opening and exhaust opening. Air resistance due to rapid contraction and rapid expansion of the air flow. Further, when the noise regulation value of the construction site is loose, or when the distance to the site boundary is large, the silencer need not be provided when the noise level is below the noise reference value without providing the silencer. Even if the silencer is not provided, air resistance is caused by sudden reduction and expansion of the air flow. Therefore, an effective opening area is calculated in consideration of the air resistance, and ventilation based on the effective opening area is performed. It is desirable to calculate the quantity. Further, the wire mesh provided in the air supply opening and the exhaust opening may be a normal wire mesh, or a bird netting (bird net) having a lattice interval of 15 to 20 mm, and further an insect repellent having a lattice interval of 6 mm or less. It may be a wire mesh for birds. However, if a wire net for insect and bird protection is provided, air resistance increases, so a wire net for bird protection is provided at the air supply opening and exhaust opening, and a low insect light that prevents insects from being recognized near the opening. It is desirable to prevent insects from entering by installing.
According to such a configuration, the silencing means is provided in the air supply opening and the exhaust opening, and the opening condition and the silencing means are set so that the sound output to the outside of the building falls below the reference value by the third determination procedure. By setting, the output of sound exceeding the reference value can be prevented. And even if the air passing through the air supply opening and the exhaust opening is subjected to resistance by the opening element such as the silencer and the wire mesh, sudden reduction and sudden expansion before and after the opening, based on the effective opening area in consideration of this air resistance By calculating the ventilation volume, a predetermined ventilation efficiency can be ensured.

On the other hand, the ventilation system for a building according to claim 4 of the present invention is a ventilation system for ventilating a building in which a heating element is housed, and according to the design method according to any one of claims 1 to 3 . It is a natural ventilation system designed.
According to the ventilation system of the building described above, the replacement type gravity that can reduce the equipment cost and the construction cost as well as the effect in the above-described design method, promote the energy saving, and suppress the running cost. Efficient ventilation can be implemented by natural ventilation system.

  According to the ventilation system design method and the building ventilation system of the present invention as described above, the facility cost, the construction cost, the running cost can be reduced, and the ventilation amount can be set rationally.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
FIG. 1 is a plan view showing a building 1 of a waste incineration facility that employs a ventilation system according to an embodiment of the present invention. FIG. 2 is a cross-sectional view of the building 1. FIG. 3 is a cross-sectional view showing air supply means provided on the outer wall 2 of the building 1.
1 to 3, the building 1 accommodates a melting furnace 4 that is a heating element inside an outer wall 2 and a roof 3, and a main space 1 </ b> A in which the melting furnace 4 is installed; It has a plurality of subspaces 1B such as partitioned machine rooms, electrical rooms, and various attached rooms. An air supply opening (air supply means) 5 for introducing outside air into the main space 1A is provided at the lower part of the outer wall 2, and an exhaust opening (exhaust means) 6 for exhausting the internal air of the main space to the outside is provided on the roof 3. An exhaust monitor 7 is provided. As shown in FIG. 3, a silencer 8 that is a silencer is installed on the indoor side of the air supply opening 5 through a partition plate 9, and outside air is introduced through the silencer 8, and sound in the building 1 is heard. It is difficult to output outdoors. Moreover, in the main space 1A of the building 1, as shown in FIG. 2, a plurality of hierarchies partitioned up and down by a flooring 10 such as a grating that can be ventilated are formed.

Such a building 1 uses outside air buoyancy (updraft) generated by heat generated by the melting furnace 4 as driving force to supply outside air from the supply opening 5 and exhausts the heated inside air from the exhaust opening 6. It is designed to be ventilated by a displacement gravity natural ventilation system.
Hereinafter, the design method of the ventilation system will be described with reference to FIGS.
FIG. 4 is a flowchart for explaining the design procedure of the ventilation system. FIGS. 5A and 5B are diagrams for explaining the heat generation from the melting furnace 4 and the temperature distribution of the inside air of the building 1, respectively. FIG. 6 is a diagram for explaining a procedure for calculating the temperature distribution of the inside air by repeated calculation. FIGS. 7A to 7C are diagrams illustrating a procedure for calculating the buoyancy of inside air.

First, in step 0 of FIG. 4 (hereinafter, step is expressed as S. S0), initial values related to various conditions and design of the building 1 and the melting furnace 4 are input. Here, the initial value to be input includes an assumption of the temperature distribution (t _hi ) of the inside air in the height direction in the building 1, that is, the “plant equipment condition input” S0 in FIG. The inventive temperature distribution assumption procedure is included. In addition, the initial value input in S0 includes the surface temperature (t _j ) and the surface area (a _ij ) of the melting furnace 4 for each level.
Next, in “total calorific value calculation” (total calorific value calculation procedure) of S1, the calorific value (calorific value distribution) inside the building 1 and the total calorific value (Q) inside the building 1 for each level are expressed by the following formula ( Calculated according to 1).

here,
q _i is the calorific value inside the building 1 of the i-th level,
Q shows the total calorific value inside the building 1. And
The subscript i indicates the floor or hierarchy (i = 1, 2, 3 ...). further,
t _j is the surface temperature of the melting furnace 4 (equipment surface temperature),
t _hi is the temperature of the inside air (the temperature in the furnace) on the i floor of Building 1,
a _ij is the surface area of the melting furnace 4 at the surface temperature tj on the i floor,
α is the heat transfer coefficient,
c _i denotes each component that is not dependent on the room temperature of the heating value of i.
Then, the surface temperature (t _j ) of the melting furnace 4 and the temperature (t _hi ) of the inside air are as shown in FIG. 5B when the surface temperature (t _j ) of the melting furnace 4 is constant. Temperature (t _hi ) shows a distribution property such that the upper floor becomes higher in temperature, and the area of the difference between the surface temperature (t _j ) of the melting furnace 4 and the temperature (t _hi ) of the inside air in this graph is the building 1 It is proportional to the amount of heat generated inside.

Next, in “Required Total Ventilation (M ₁ ) Calculation” (Required Total Ventilation Calculation Procedure) of S2, the required total ventilation (M ₁ ) required based on the total calorific value (Q) inside the building ₁ ) Is calculated by the following equation (2).
here,
C _p is the constant pressure specific heat of air,
Δt represents the target internal and external maximum temperature difference.
As this internal / external maximum temperature difference (Δt), for example, a predetermined value of 12 ° C. to 15 ° C. is set.

Next, in the “calculation of the temperature distribution of the inside air” (temperature distribution calculation procedure) of S3, the temperature distribution (t _hi ) of the inside air inside the building 1 is expressed by the following equation (3) based on the required total ventilation (M ₁ ). calculate.
here,
t ₀ is the outside air temperature,
q _k represents the calorific value of the k-th floor, respectively.
The temperature distribution (t _hi ) of the inside air is calculated on the assumption of temperature stratification for each level. Then, based on the calculated temperature distribution (t _hi ) of the inside air, the calorific value distribution (q _i ) is calculated by the above formula (1) (“calorific value distribution calculation” S4, calorific value distribution calculating procedure).

When the temperature distribution (t _hi ) of the inside air is calculated as described above, the calculated temperature distribution is compared with the temperature distribution of the inside air assumed in S0 described above, and depending on whether or not the difference is within a predetermined value. It is determined whether the temperature distribution (t _hi ) of the inside air has converged (S5, first determination procedure).
If it is determined that the temperature distribution (t _hi ) of the inside air has converged, the next step (S6) is executed. If it has not converged, the process returns to the “total calorific value calculation” S1, and the building 1 The internal total heat generation amount (Q) is calculated based on the heat generation amount distribution (q _i ) calculated in S4, and S2 to S4 are executed again. As a result, a new temperature distribution (t _hi ) of the inside air is calculated, and in S5 again, the calculated new temperature distribution is compared with the previously calculated temperature distribution of the inside air, and the temperature distribution (t _hi ) of the inside air is calculated. Whether or not has converged.

Such steps of S1 to S4 are repeated until the temperature distribution (t _hi ) of the inside air converges as shown in FIG. That is, the total calorific value, the calorific value distribution, the required total ventilation are each represented by a function of the inside air temperature distribution (t _h), the inside air temperature distribution (t _h) to itself is represented by a function of the temperature distribution From the above, by repeatedly executing S1 to S4, the temperature distribution (t _h ) of the inside air converges, and at the time of convergence, the required ventilation amount that balances the heat generation amount is calculated, and the temperature distribution (t t of the inside air in the balanced state (t _h ) will be calculated.
When the temperature distribution (t _h ) of the inside air is calculated as described above, based on the specific air weight (γ _hi ) calculated from the temperature distribution (t _h ) of the inside air, the “buoyancy calculation of the inside air” of S6 is performed. "(Buoyancy calculation procedure), the buoyancy (F) of the inside air in the building 1 is calculated by the following equation (4).

here,
G is the acceleration of gravity,
h _i is the height of each floor (furnace chamber height),
γ ₀ is the outside air specific weight,
gamma _hi shows air ratio by weight in the floor height h _i (the furnace chamber air ratio by weight) respectively.
That is, as shown in FIG. 7A, if the temperature distribution (t _hi ) of the inside air is calculated as described above, the air of the inside air that is inversely proportional to the temperature distribution as shown in FIG. 7B. The specific weight (γ _hi ) can be calculated. Then, the buoyancy (F) of the inside air calculated by the equation (4) is drawn by a difference between the outside air specific weight (γ ₀ ) and the inside air specific weight (γ _hi ) as shown in FIG. 7C. It corresponds to the area of the graph (the shaded area in the figure).

Then, based on the internal air buoyancy calculated (F), in the S7 "real ventilation (M ₂₎ calculation" (actual ventilation calculation procedure), but it calculates the actual ventilation (M _2), before it In the “opening condition input” (opening condition input procedure) of S8, the opening conditions (opening area, local resistance coefficient by the silencer 8, etc.) of the air supply opening 5 and the exhaust opening 6, and the local resistance coefficient of passage between each layer Enter. And the ventilation circuit calculation formula shown to following Formula (5) is materialized from the pressure loss calculated from each of these conditions, and the buoyancy (F) of inside air.

here,
ΔP _S indicates the pressure loss due to the air supply opening 5,
ΔP _S = 1/2 · γ ₀ · (ζ ₀ + ζ _Sk ) · V _Sk ² .
ΔP _R indicates the pressure loss due to the passage inside the building 1,
ΔP _R = 1/2 · Σ _{(n = 1)} γ _Rn · ζ _Rn · V _Rn ² Also,
ΔP _E indicates the pressure loss due to the exhaust opening 6,
ΔP _E = 1/2 · γ _E · ζ _E · V _E ² . Also,
ζ _Sk is the total local resistance coefficient of each element of the k-th supply opening 5,
ζ ₀ is the local resistance coefficient of the simple aperture,
ζ _Rn is a local resistance coefficient passing through the n-th layer in the building 1,
ζ _E is the local resistance coefficient of the exhaust opening 6,
V _Sk is the wind speed passing through the kth air supply opening 5;
V _Rn is the wind speed passing through the nth floor,
V _E is the air velocity passing through the exhaust opening 6,
γ ₀ is the outside air specific weight,
γ _Rn is the air specific weight in the nth _floor ,
γ _E indicates the specific weight of the exhaust air.

The actual ventilation amount (M ₂ ) is expressed by the following equation (6) from the continuous equation, and the actual ventilation amount (M ₂ ) is calculated by solving the equations (5) and (6). .
here,
p _Sk is the effective opening ratio of the kth supply opening 5;
p _Rn is the effective opening ratio of the n-th floor in the building 1;
p _E is the effective opening ratio of the exhaust opening 6;
A _Sk is the opening area of the kth supply opening 5;
A _Rn is the floor area of n layers,
A _E indicates the opening area of the exhaust opening 6.

In this equation (6), the floor area (A _Rn ) of each layer and its effective aperture ratio (p _Rn ) are determined by the plant equipment layout, and the local resistance coefficient (ζ _Rn ) passing through the n layer is determined by grating or the like. It becomes a specific value depending on the flooring 10. Moreover, the local resistance coefficient (ζ _E ) of the exhaust opening 6 of the exhaust monitor 7 is an eigenvalue of the exhaust monitor 7, and the opening area (A _E ) and the effective opening ratio (p _E ) of the exhaust opening 6 are calculated as required total ventilation ( If it is set based on M ₁ ), the factor that determines the actual ventilation volume (M ₂ ) in equation (6) is the opening area (A _Sk ) that is the opening condition of the air supply opening 5, The effective opening ratio (p _Sk ) and local resistance coefficient (ζ _Sk ) are obtained, and the actual ventilation volume (M ₂ ) is calculated by the following equation (7).
In this equation (7),
ζ _km indicates the local resistance coefficient of the m-th component resistor (such as the silencer 8) of the k-th air supply opening 5, and the air resistance of the silencer 8 or the like as the local resistance coefficient (ζ _Sk ) of the exhaust opening 6 The local resistance coefficient (ζ _km ) determined from

It is confirmed in S9 (second judgment procedure) that the actual ventilation volume (M ₂ ) calculated as described above exceeds the required total ventilation volume (M ₁ ). If the actual ventilation volume (M ₂ ) exceeds the required total ventilation volume (M ₁ ), the “noise simulation” (third judgment procedure) of S10 is executed, and the sound in the building 1 exceeds the reference value. Confirm that the data is not output to the outside. If the actual ventilation volume (M ₂ ) does not exceed the required total ventilation volume (M ₁ ) in S9, or if the sound output to the outside exceeds the reference value in S10, the “opening condition input” in S8 ”, The number of the air supply openings 5, the opening area (A _Sk ), and the specifications of the silencer 8 are input again, and S7, S9, and S10 are executed. At this time, based on the above equation (7), the total equivalent opening area (A _eq ) is defined as the following equation (8).

In this equation (8), the total equivalent opening area (A _eq ) is a simple opening area (effective opening ratio p _S = 1.0, local resistance coefficient) in which all the air supply openings 5 can be supplied with the same amount of natural air. ζ ₀ = 1.0) is the total area converted, and the plant equipment layout, noise conditions, etc. are changed, and it is necessary to change the opening area, opening ratio, and local resistance coefficient of the supply opening 5 This is the value that should be maintained. For example, when the noise conditions become severe (No in S10) and the local resistance coefficient increases with the sound reduction performance of the silencer 8, the opening area of the air supply opening 5 is increased, or a separate air supply opening 5 is provided. The total equivalent opening area (A _eq ) is used as an index at the time of calculation. By defining such an equivalent opening area total (A _eq ), it becomes a guide when re-inputting the opening condition, and re-input can be easily executed.

  Further, as shown in FIG. 1, the main space 1A is forced from an opening 11 provided with a transfer flow that flows into the main space 1A via the mechanically ventilated subspace 1B, a blower that is a forced flow introducing means, and the like. The forced flow to be introduced can be input in the “forced flow / transfer flow input” (forced flow / transfer flow input procedure) of S11. When a forced flow or a transfer flow is input, although not described in detail in the present embodiment, the forced flow or the transfer is corrected by appropriately correcting the above formulas (1) to (3) and (5). The influence of the flow can be evaluated, and calculation accuracy of buoyancy and actual ventilation can be improved.

According to this embodiment, there are the following effects.
(1) That is, by adopting a substitution type gravity natural ventilation system that performs air supply and exhaust using the driving force obtained by the buoyancy (F) of the inside air, only the air supply opening 5 is required as the air supply means. It is not necessary to use a blower or an air supply duct, and the equipment cost for installing them and the construction cost for securing the installation space can be reduced, and the power for driving the blower becomes unnecessary , so energy saving And the running cost can be reduced.

(2) Further, in the ventilation design, the actual ventilation volume (M ₂ ) based on the buoyancy (F) of the inside air is accurately calculated by simulating the temperature distribution (t _hi ) of the inside air with high accuracy by repeated calculation. And natural ventilation systems can be rationally designed. Further, by setting the opening condition so that the actual ventilation volume (M ₂ ) exceeds the required total ventilation volume (M ₁ ), the opening condition, that is, the opening area of the supply opening 5 and the silencer 8 Specifications etc. can be set rationally and economically.

In addition, this invention is not limited to the said embodiment, Including other structures etc. which can achieve the objective of this invention, the deformation | transformation etc. which are shown below are also contained in this invention.
For example, in the above-described embodiment, the waste incineration facility is described, and the refuse melting furnace 4 is adopted as a heating element. However, the heating element is not limited to the melting furnace 4, and any furnace or combustion facility can be applied.
In the above embodiment, S1 to S4 are repeatedly executed so that the temperature distribution (t _hi ) of the inside air converges. However, the determination of whether or not it converges in S5 is not limited to the temperature distribution of the inside air. Alternatively, the determination may be made based on the heat generation amount, or a variable different from the temperature distribution or the heat generation amount may be defined, and it may be determined whether or not the convergence is made based on the variable.

In addition, the best configuration, method and the like for carrying out the present invention have been disclosed in the above description, but the present invention is not limited to this. That is, the invention has been illustrated and described with particular reference to certain specific embodiments, but without departing from the spirit and scope of the invention, Various modifications can be made by those skilled in the art in terms of material, quantity, and other detailed configurations.
Therefore, the description limiting the shape, material, etc. disclosed above is an example for easy understanding of the present invention, and does not limit the present invention. The description by the name of the member which remove | excluded the limitation of one part or all of such restrictions is included in this invention.

It is a top view which shows the plant | facility which employ | adopted the ventilation system which concerns on embodiment of this invention. It is sectional drawing of the said facility. It is sectional drawing which shows the air supply means provided in the outer wall of the said facility. It is a flowchart explaining the design procedure of the said ventilation system. (A), (B) is a figure explaining the heat distribution from a heat generating body in the design of a ventilation system, and the temperature distribution of inside air. It is a figure explaining the procedure which calculates the temperature distribution of inside air by a repetitive calculation. (A)-(C) is a figure explaining the procedure which calculates the buoyancy of inside air.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Building, 4 ... Melting furnace which is a heating element, 5 ... Air supply opening (air supply means), 6 ... Exhaust opening (exhaust means), 8 ... Silencer which is a muffling means, S1 ... Total calorific value calculation procedure, S2 ... required total ventilation amount calculation procedure, S3 ... temperature distribution calculation procedure, S4 ... heat generation amount distribution calculation procedure, S5 ... first determination procedure, S6 ... buoyancy calculation procedure, S7 ... actual ventilation amount calculation procedure, S9 ... second determination procedure , S10: Third determination procedure.

Claims (4)

A method for designing a ventilation system for ventilating an interior of a building using an air supply means and an exhaust means in a building containing a heating element therein,
The air supply means includes an air supply opening provided in a lower part of the building, and the exhaust means includes an exhaust opening provided in an upper part of the building. Each of the air supply opening and the exhaust opening is provided. Based on the opening condition including the area and the buoyancy calculated from the temperature distribution and temperature distribution of the inside air in the height direction of the building, the ventilation amount supplied from the supply opening and exhausted from the exhaust opening Is a method of calculating
A temperature distribution assumption procedure that assumes the temperature distribution of the inside air in the height direction of the building;
A calorific value distribution calculation procedure for calculating a calorific value distribution in the height direction of the building based on the temperature distribution of the inside air;
Based on the calculated calorific value distribution, a total calorific value calculation procedure for calculating the total calorific value of the inside of the building,
Based on the calculated total calorific value, the required total ventilation calculation procedure for calculating the required total ventilation required,
A temperature distribution calculation procedure for calculating the temperature distribution of the inside air based on the calculated required total ventilation,
It is determined whether or not the temperature distribution of the inside air calculated by the temperature distribution calculation procedure has converged. If the temperature distribution does not converge, the heat generation amount distribution calculation procedure, the total heat generation amount calculation procedure, the required total ventilation amount calculation procedure, and the temperature distribution A first determination procedure for repeatedly executing the calculation procedure;
A buoyancy calculation procedure for calculating the buoyancy generated in the inside air of the building based on the temperature distribution of the inside air determined to have converged in the first determination procedure;
An actual ventilation amount calculation procedure for calculating an actual ventilation amount based on the driving force obtained by the buoyancy of the inside air calculated in the buoyancy calculation procedure and the opening condition;
Judge whether the calculated actual ventilation exceeds the required total ventilation calculated in the above required total ventilation calculation procedure, and if the actual ventilation does not exceed the required total ventilation, the newly set opening condition A second determination procedure for causing the actual ventilation volume calculation procedure to execute calculation of the actual ventilation volume based on:
A ventilation system design method characterized by comprising: The method for designing a ventilation system according to claim 1,
The calorific value distribution in the height direction of the building interior and the total calorific value of the building interior are each calculated by equation (1),

In this equation (1),
q _i  Is the calorific value inside the i-th floor building,
Q is the total calorific value inside the building,
Where the subscript i indicates the floor or hierarchy (i = 1, 2, 3 ...)
t _j  Is the surface temperature of the heating element,
t _hi Is the temperature of the inside air on the i floor of the building,
a _ij Is the surface area of the heating element at the surface temperature tj on the i-th floor,
α is the heat transfer coefficient,
c _i  Is the component that does not depend on the room temperature of the heat generation of the i-th layer
A method for designing a ventilation system, characterized in that In the designing method of the ventilation system according to claim 1 or 2,
A third determination procedure for determining whether or not the volume of sound output to the outside of the building through the air supply opening and the exhaust opening is lower than a preset reference value; In the case where the volume of sound output outside the building does not fall below a reference value, the reset opening condition and the air resistance of the silencer provided in at least one of the air supply opening and the exhaust opening are included. A design method of a ventilation system, characterized in that a ventilation amount is calculated based on an effective opening area calculated according to a calculation condition. A ventilation system for ventilating a building containing a heating element inside,
A building ventilation system, which is a natural ventilation system designed by the design method according to any one of claims 1 to 3.

Images