Method for controlling air conditioning zone and air conditioning device

Abstract

To enable arbitrary setting of the height of an area to be air-conditioned while achieving energy conservation. [Solution] This is an air-conditioning area control method for setting an arbitrary height above the floor of an air-conditioning area 4, which is an area from the floor to a predetermined height that needs to be maintained within a predetermined temperature range by air conditioning. When the difference between the set temperature of the air-conditioning area 4 and the blown air temperature of an air conditioner 1 is defined as the supply air temperature difference, the ratio of the blown air volume to the maximum air volume of the air conditioner 1 is defined as the maximum air volume ratio, and the ratio of the occupied area of ​​a thermal load 2 installed in space 3 to the floor area of ​​space 3 is defined as the load area occupancy rate, a relationship between the load area occupancy rate and the floor height is obtained for each supply air temperature difference, with the maximum air volume ratio as a parameter, and the supply air temperature difference, maximum air volume ratio, and load area occupancy rate for obtaining an arbitrary floor height are determined from these relationships.

Description

[Technical field]

[0001] The present invention relates to an air conditioning area control method and air conditioning device that enable the height above the floor of an air conditioned area in a large space such as a factory, clean room, or data center to be set to any height. [Background technology]

[0002] In Patent Documents 1 and 2 listed below, the applicant has proposed an air-conditioning control method for large spaces, in which a height of approximately 2 to 4 m from the floor of the target space is maintained within a predetermined temperature range as the air-conditioned area, while in the space above the air-conditioned area (non-air-conditioned area), high-temperature air is pushed out from the air-conditioned area, thereby forming a horizontal temperature distribution in the height direction throughout the space. The applicant has proposed a control method and a control device for this air-conditioning control method. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Patent No. 6417458 [Patent Document 2] Patent No. 6622857 Summary of the Invention [Problem to be solved by the invention]

[0004] The height of the air-conditioned area controlled to a predetermined temperature range is set to different heights by the user, and it is desirable to be able to set it to any height. However, since the height of this air-conditioned area varies depending on the heat load placed in the room, it has been determined by measuring the temperature distribution in the height direction for each target room and adjusting the air volume, blowing air temperature, etc. through trial and error so that the air-conditioned area is within the predetermined temperature range.

[0005] The values ​​determined in this manner are the result of trial and error, and therefore little consideration is given to energy conservation, leaving room for improvement.

[0006] SUMMARY OF THE PRESENT DISCLOSURE OF THE PRESENT DISCLOSURE It is therefore a primary object of the present invention to provide an air conditioning zone control method and air conditioning device that enable the height of the air conditioned zone to be set arbitrarily while also achieving energy savings. [Means for solving the problem]

[0007] In order to solve the above problems, the present invention according to claim 1 provides a method for controlling an air-conditioning area, which defines an area from a floor to a predetermined height that needs to be maintained within a predetermined temperature range by air conditioning, and sets the height of the air-conditioning area above the floor to an arbitrary height, The difference between the set temperature of the air-conditioned area and the blown air temperature of the air conditioner is defined as the supply air temperature difference, the ratio of the blown air volume to the maximum air volume of the air conditioner is defined as the maximum air volume ratio, and the ratio of the occupied area of ​​the heat load installed in the space to the floor area of ​​the space is defined as the load area occupancy rate, A relationship between the load area occupancy rate and the height above the floor is obtained for each supply air temperature difference, with the maximum air volume ratio as a parameter; From these relationships, a method for controlling an air-conditioned area is provided, which is characterized by determining the supply air temperature difference, maximum air volume ratio, and load area occupancy rate for obtaining an arbitrary height above the floor.

[0008] In the invention described in claim 1, a relationship between the load area occupancy rate and the floor height is obtained for each supply air temperature difference from a simulation described below, with the maximum air volume ratio as a parameter, and the supply air temperature difference, maximum air volume ratio, and load area occupancy rate for obtaining an arbitrary floor height are determined from this relationship. Specifically, the supply air temperature difference is determined from the required temperature of the product to be placed in the air-conditioned area and the air conditioner's blowing temperature, and the air conditioner's maximum air volume ratio is set at this supply air temperature difference, and the floor height of the air-conditioned area is obtained by arranging the heat load at a predetermined area occupancy rate. Each value obtained in this way is not a value obtained by trial and error, but is obtained from a relationship obtained in advance, so that a value can be set that takes into account the energy efficiency of the air conditioner, thereby achieving energy conservation.

[0009] The present invention according to claim 2 provides a method for controlling an air-conditioning area, which defines an area from a floor to a predetermined height that needs to be maintained within a predetermined temperature range by air conditioning, and sets the height of the air-conditioning area above the floor to an arbitrary height, The difference between the set temperature of the air-conditioned area and the blown air temperature of the air conditioner is defined as the supply air temperature difference, the ratio of the blown air volume to the maximum air volume of the air conditioner is defined as the maximum air volume ratio, and the ratio of the occupied area of ​​the heat load installed in the space to the floor area of ​​the space is defined as the load area occupancy rate, A relationship between the load area occupancy rate and the height above the floor is obtained for each maximum air volume ratio, with the supply air temperature difference as a parameter; From these relationships, a method for controlling an air-conditioned area is provided, which is characterized by determining the supply air temperature difference, maximum air volume ratio, and load area occupancy rate for obtaining an arbitrary height above the floor.

[0010] In the invention described in claim 2, the relationship between the load area occupancy rate and the height above the floor is obtained for each maximum airflow ratio, with the supply air temperature difference as a parameter, and from these relationships, the supply air temperature difference, maximum airflow ratio, and load area occupancy rate for obtaining an arbitrary height above the floor are determined. Here, the maximum airflow ratio is determined first, and then the other conditions are determined.

[0011] As a third aspect of the present invention, the air conditioner includes a cooling coil unit that adjusts the temperature of the air, a blower unit that compresses and blows the air, and a filter unit that purifies the air, The method for controlling an air-conditioned area according to claim 1 or 2 is provided, which is a lateral blow-out type air conditioner that blows conditioned air laterally from a side of the space.

[0012] In the invention described in claim 3 above, the air conditioner adjusts the temperature in the cooling coil section and cleans the air in the filter section, and then pressurizes and blows it out by the blower section. Since a horizontal blow-out type air conditioner is used that blows conditioned air horizontally from the side of the space, the air blown out from the air conditioner tends to flow into the lower part of the space, and a horizontal temperature distribution is easily formed in which the temperature gradually increases in the vertical direction from the lower part to the upper part of the space.

[0013] The present invention according to claim 4 provides a method for controlling an air-conditioned area according to any one of claims 1 and 2, wherein a hood is provided at the air conditioner outlet to suppress draft airflow forward and rectify the airflow downward.

[0014] In the invention described in claim 4 above, a hood is provided at the air conditioner's air outlet to suppress draft airflow forward and straighten the air in a downward direction, making it easier for the air blown out from the air conditioner to flow into the lower part of the space, and making it easier to form a horizontal temperature distribution in which the temperature gradually increases in the vertical direction from the lower part to the upper part of the space.

[0015] The present invention relates to claim 5, and provides a method for controlling an air-conditioned area as described in claim 1 or 2, in which the height of the air-conditioned area above the floor is set to 1.5 m or less when a product requiring a guaranteed temperature range is placed in the air-conditioned area.

[0016] In the invention described in claim 5 above, only the range below the height at which products requiring a guaranteed temperature range are placed in factories, clean rooms, etc. is controlled to a predetermined temperature or lower, thereby reducing the energy consumption of the air conditioner and achieving energy conservation.

[0017] The present invention according to claim 6 provides a method for controlling an air-conditioning zone according to either claim 1 or 2, wherein the supply air temperature difference is in the range of 8 to 12°C, the maximum air volume ratio is in the range of 50 to 100%, and the load area occupancy rate is in the range of 2 to 20%.

[0018] In the invention described in claim 6 above, the range of each parameter used in the simulation is shown.

[0019] According to a seventh aspect of the present invention, there is provided an air conditioner comprising a controller that uses the method for controlling an air conditioning zone according to any one of the first and second aspects. Effect of the Invention

[0020] As described above in detail, according to the present invention, the height of the area to be air-conditioned can be set arbitrarily while achieving energy conservation. [Brief description of the drawings]

[0021] [Figure 1] FIG. 2 is a vertical cross-sectional view of a space 3 in which an air conditioner 1 is installed. [Diagram 2] FIG. 2 is a vertical cross-sectional view of the air conditioner 1. [Diagram 3] FIG. 2 is a cross-sectional view of the air conditioner 1. [Figure 4] FIG. 2 is a perspective view of an air conditioner 1 equipped with an air conditioning outlet 20. [Diagram 5] FIG. 2 is a front perspective view showing an air conditioning outlet 20. [Figure 6] FIG. [Figure 7] 1A, 1B, and 1C are views showing an air-conditioning outlet 20, in which (A) is a front view, (B) is a side view, and (C) is a top view. [Figure 8] 8 is a cross-sectional view taken along line VIII-VIII in FIG. 7. [Figure 9] 9 is a cross-sectional view taken along line IX-IX in FIG. 7. [Figure 10] 1A and 1B are diagrams showing airflow in a conventional air-conditioning outlet 50, in which (A) is a plan view and (B) is a side view. [Figure 11] 1A and 1B are diagrams showing the airflow of an air-conditioning outlet 20, in which (A) is a plan view and (B) is a side view. [Figure 12] 13 is a graph showing the relationship between the load area occupancy rate and height above the floor for each supply air temperature difference, with the maximum air volume ratio as a parameter. [Figure 13] 13 is a graph showing the relationship between the load area occupancy rate and height above the floor for each maximum air volume ratio, with the supply air temperature difference as a parameter. [Figure 14] FIG. 2 is a perspective view of a space 3 used in a simulation. [Figure 15] FIG. [Figure 16] FIG. 2 is a plan view showing an evaluation area. [Figure 17] 1 is an example of a graph showing a temperature distribution in a height direction. [Figure 18] 13 is an example of a graph showing the relationship between the maximum airflow ratio and the height above the floor of the air-conditioned area 4. [Figure 19] FIG. 11 is a spatial temperature distribution diagram showing the results of Comparative Example 1. [Figure 20] FIG. 11 is a temperature distribution diagram in the height direction showing the results of Comparative Example 1. [Figure 21] FIG. 11 is a front view of an air conditioner showing the conditions of the opening ratio in Comparative Example 2. [Figure 22] FIG. 11 is a spatial temperature distribution diagram showing the results of Comparative Example 2. [Figure 23] FIG. 11 is a temperature distribution diagram in the height direction showing the results of Comparative Example 2. [Figure 24] FIG. 1 is a perspective view of a space 3 showing conditions of a load area occupancy rate. [Diagram 25] FIG. 13 is a temperature distribution diagram of space 3 at a load area occupancy rate of 19.2%. [Figure 26] This is a temperature distribution diagram in the height direction at a load area occupancy rate of 19.2%. [Figure 27] 13 is a graph showing the relationship between maximum airflow ratio and height above floor when the load area occupancy rate is 19.2%. [Figure 28] 13 is a graph showing the relationship between supply air temperature difference and height above the floor when the load area occupancy rate is 19.2%. [Figure 29]This is a temperature distribution diagram of space 3 when the load area occupancy rate is 11.5% dispersion. [Diagram 30] This is a temperature distribution diagram in the height direction when the load area occupancy rate is 11.5%. [Diagram 31] 13 is a graph showing the relationship between maximum airflow ratio and height above floor when the load area occupancy rate is 11.5% dispersion. [Diagram 32] This is a graph showing the relationship between supply air temperature difference and height above the floor when the load area occupancy rate is 11.5%. [Diagram 33] This is a temperature distribution diagram of space 3 where the load area occupancy rate is 11.5%. [Diagram 34] This is a temperature distribution diagram in the height direction when the load area occupancy rate is 11.5%. [Diagram 35] 13 is a graph showing the relationship between maximum airflow ratio and height above floor when the load area occupancy rate is 11.5%. [Diagram 36] This is a graph showing the relationship between supply air temperature difference and height above the floor when the load area occupancy rate is 11.5%. [Figure 37] This is a temperature distribution diagram of space 3 at a load area occupancy rate of 7.7%. [Figure 38] This is a temperature distribution diagram in the height direction at a load area occupancy rate of 7.7%. [Figure 39] 13 is a graph showing the relationship between maximum airflow ratio and height above floor when the load area occupancy rate is 7.7%. [Diagram 40] 13 is a graph showing the relationship between supply air temperature difference and height above the floor when the load area occupancy rate is 7.7%. [Diagram 41] FIG. 13 is a temperature distribution diagram of space 3 at a load area occupancy rate of 3.8%. [Diagram 42] This is a temperature distribution diagram in the height direction at a load area occupancy rate of 3.8%. [Diagram 43] 13 is a graph showing the relationship between maximum airflow ratio and height above floor when the load area occupancy rate is 3.8%. [Diagram 44] 13 is a graph showing the relationship between supply air temperature difference and height above the floor when the load area occupancy rate is 3.8%. [Diagram 45]FIG. 13 is a temperature distribution diagram of space 3 at a load area occupancy rate of 2.6%. [Figure 46] This is a temperature distribution diagram in the height direction at a load area occupancy rate of 2.6%. [Figure 47] 13 is a graph showing the relationship between maximum airflow ratio and height above floor when the load area occupancy rate is 2.6%. [Figure 48] 13 is a graph showing the relationship between supply air temperature difference and height above the floor when the load area occupancy rate is 2.6%. [Figure 49] 13 is a graph showing the relationship between supply air temperature difference and height above floor for each maximum air volume ratio, with load area occupancy rate as a parameter. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0022] Hereinafter, an embodiment of the present invention will be described in detail with reference to the drawings.

[0023] The method for controlling an air-conditioned area according to the present invention is a method for dividing an air-conditioned area in which a heat load 2 such as manufacturing equipment or servers is installed in a large space 3 such as a factory, clean room, or data center, as shown in FIG. 1, into an air-conditioned area 4, which is the space from the floor to a specified height that needs to be maintained within a specified temperature range by air conditioning using an air conditioner 1, and a non-conditioned area 5, which is the space above this air-conditioned area 4, and for setting the height H above the floor of the air-conditioned area 4 to any desired height.

[0024] The space 3 is divided into an air-conditioned area 4 from the floor to a specified height, and a non-air-conditioned area 5 above it. In Fig. 1, the air-conditioned area 4 and the non-air-conditioned area 5 are shown as being adjacent to each other, but in reality there is a temperature transition area between them, and the temperature gradually increases in layers as you move from the air-conditioned area 4 to the non-air-conditioned area 5. The boundary between the air-conditioned area 4 and the non-air-conditioned area 5 exists virtually in the space 3, and is set as a design condition at the beginning of the air-conditioning design, and the various conditions of the air conditioner 1 are designed under this design condition.

[0025] For example, if the guaranteed temperature range required for products produced in a factory is 23°C ± 3°C, the air-conditioned area (task zone) where this temperature range is guaranteed by air conditioning is set to a height of 1.5 m or less above the floor, preferably at a height of about 1.2 to 1.5 m, and above that an area with a temperature range for personal air conditioning for workers (for example, 28°C or less) is set to a height of about 2 m as the work zone, and the area above that is set as the non-air-conditioned area 5.

[0026] (Air conditioner) First, the air conditioner 1 will be described. Any known air conditioner can be used as the air conditioner 1 without any restrictions, but it is particularly preferable to use a side-blow type air conditioner that blows conditioned air laterally from the side of the space 3. As such an air conditioner 1, as in the illustrated example, one that is manufactured as a single device and is unitized so that it can be installed at any position within the space 3 is used.

[0027] Specifically, as shown in FIG. 1, the system includes an air inlet section 11 that introduces air from the non-air-conditioned area 5, a cooling coil section 7 that adjusts the temperature of the air introduced into the air inlet section 11, a blower section 8 that pressurizes the air whose temperature has been adjusted by the cooling coil section 7, and a filter section 9 that purifies the air.

[0028] At least a portion of the high-temperature air in the non-air-conditioned area 5 flows laterally into the air introduction section 11 through an opening formed in the upper part of the side surface of the air conditioner 1. This forms an air circulation path for at least a portion of the conditioned air blown out from the air conditioner 1 into the space 3 to return to the air introduction section 11 of the air conditioner 1 from the air-conditioned area 4 through the non-air-conditioned area 5.

[0029] 2, the air introduced into the air inlet section 11 has its temperature adjusted (cooled) in the cooling coil section 7, and is then supplied to a chamber 13 formed in the rear portion of the air conditioner 1. Thereafter, the air in the chamber 13 passes through a blower section 8 (fan) and a filter section 9, and is then supplied to the room through the air outlet of the air conditioner 1.

[0030] As the filter for purifying the air provided in the filter section 9, a medium-performance filter or a coarse dust filter can be used when the target space 3 is used as a factory or a data center, and a high-performance filter can be used when the space 3 is used as a clean room.

[0031] The air blower unit 8 and the filter unit 9 may be formed separately, but it is preferable to use a general-purpose fan filter unit (FFU) that combines them. The fan filter units 8 and 9 may each be a single unit, but it is preferable to arrange multiple units in parallel vertically as shown in Fig. 3.

[0032] (Air conditioning outlet) There is no particular restriction on the blowing method of the air conditioner 1, and it may be blown out in a normal manner, but in the present invention, it is particularly preferable to use an air conditioning outlet provided on the blowing surface of the air conditioner 1, which is provided with a hood that suppresses draft airflow toward the front and rectifies the air flow downward. As such an air conditioning outlet, the one disclosed in JP 2023-152336 A is suitable. The air conditioning outlet will be described below by citing the description in the publication.

[0033] 4 to 9, the air conditioning outlet 20 is a flat plate covering the outer surface of the air conditioner 1, and is provided with a plurality of outlet openings 21, 21... for blowing out conditioned air into the room. The outer edge of this air conditioning outlet 20 is provided with a flange portion 20a (see FIG. 6) that protrudes toward the air conditioner 1 for fixing to the outer surface of the air conditioner 1.

[0034] The air-conditioning outlet 20 is provided with a hood 22 at each outlet opening 21 for rectifying the conditioned air that has passed through the outlet opening 21 in a fixed direction. In other words, the conditioned air that has passed through the outlet opening 21 and been blown out in a straight line forward perpendicular to the front surface of the air conditioner 1 is rectified by changing the airflow in a downward direction that is approximately perpendicular to the direction that the air previously traveled in a straight line perpendicular to the front surface of the air conditioner 1, by the hood 22 provided on the outside of the outlet opening 21.

[0035] 10 and 11, in the conventional air conditioning outlet 50, as shown in Fig. 10, an air flow that moves straight in a direction almost perpendicular to the front surface of the air conditioner 1 is formed in front of the air conditioner 1, and therefore the draft air flow may excessively hit the entire device or person X in front of the air conditioner 1, adversely affecting the device or person X. In addition, the conditioned air by the draft air flow blown out from the air conditioner 1 may be mixed with the indoor air in front of the air conditioner 1 over the entire height of the air conditioner 1, which may reduce the air conditioning efficiency.

[0036] 11, in the air-conditioning outlet 20, the hood 22 rectifies the conditioned air that has passed through the air-outlet opening 21 downward and flows along the floor surface, preventing the draft airflow from hitting the entire device or person X present in front of the air conditioner 1. In addition, since the draft airflow blown out from the air conditioner 1 flows along the floor surface of the air-conditioned area, a layered horizontal temperature distribution is formed in the height direction from the floor surface, making it easier to maintain a predetermined temperature range at a predetermined height above the floor in the target space as the air-conditioned area.

[0037] The principle by which the conditioned air that has passed through the air outlet opening 21 is rectified in the downward direction is that, as shown in Figure 11 (B), the downward airflow blown out from the hood 22 located on the upper side abuts against the outer surface of the hood 22 adjacent to it in the downward direction, forming a vortex V on the front side thereof, and this vortex V attracts the airflow flowing outside it toward the air outlet, making it easier to form a downward airflow along the front surface of the air outlet.

[0038] To explain the structure of the air conditioning outlet 20 in more detail, the planar shape of the outlet opening 21 is formed in an elongated shape that is long in a predetermined direction, and specifically, is formed in an elongated rectangular shape, oval shape, elliptical shape, or the like that is long in a direction perpendicular to the direction in which the conditioned air is rectified by the hood 22. In the illustrated example, it is formed in a rectangular shape that is long in the width direction perpendicular to the downward direction in which the conditioned air is rectified. The multiple outlet openings 21 formed on the front surface of the air conditioner 1 are all formed in the same shape and dimensions.

[0039] The blow-out openings 21 may be provided at least at a predetermined interval along the vertical direction in which the conditioned air is rectified, and need not necessarily be provided at a plurality of positions in the width direction perpendicular to the vertical direction. By providing a plurality of blow-out openings 21 in the rectified direction, a vortex V is formed on the outer surface of the hood 22 described above, and an air flow along the front surface of the blow-out opening is easily formed. In the illustrated example, the blow-out openings 21 are arranged at a predetermined interval along the vertical direction in which the conditioned air is rectified, and are also arranged at a predetermined interval along the width direction perpendicular to the vertical direction. More specifically, the blow-out openings 21 are formed at a total of 16 positions by arranging two rows of eight blow-out openings 21 arranged at a predetermined interval along the vertical direction in parallel in the width direction.

[0040] The hood 22 covering the outside of each blow-out opening 21 is disposed so as to cover the entire blow-out opening 21 in a front view of the air-conditioning outlet 20 shown in Fig. 7(A). In other words, when the front surface of the air-conditioning outlet 20 is viewed from the front, the entire blow-out opening 21 is covered by the hood 22, and the blow-out opening 21 is hidden by the hood 22 and cannot be seen. As a result, the conditioned air traveling straight and perpendicular to the opening surface of the blow-out opening 21 always comes into contact with the hood 22, and the hood 22 reliably changes the direction of the airflow.

[0041] 8 and 9 in detail, the hood 22 is composed of a top plate 23 and side plates 24, 24 that protrude from the outer edge of the outlet opening 21 or its vicinity almost perpendicular to the front plate of the air-conditioning outlet 20, and a curtain board 25 that faces the outlet opening 21 at a position spaced apart from the outlet opening 21, and forms a roughly rectangular box-shaped space on the outside that communicates with the outlet opening 21, the top and sides of which are surrounded by the top plate 23, side plates 24 and curtain board 25, respectively, and the bottom is open. As a result, the conditioned air that passes through the outlet opening 21 and flows into the hood 22 flows toward the open downward side.

[0042] The top plate 23 and the side plate 24 protrude almost perpendicularly to the opening of the blow-out opening 21 (the front plate of the air-conditioning outlet 20), and extend almost straight in the vertical direction without bending or inclining in the middle of the protruding direction. Therefore, the top plate 23 and the side plate 24 do not change the direction of the airflow of the conditioned air blown out from the blow-out opening 21, and the airflow proceeds almost straight to the curtain plate 25 facing the blow-out opening 21.

[0043] The flapboard 25 is connected to the protruding side ends of the top plate 23 and the side plates 24 almost perpendicularly, and is disposed almost parallel to the opening surface of the outlet opening 21 (the front plate of the air-conditioning outlet 20). The conditioned air blown out from the outlet opening 21 travels straight and comes into contact with the flapboard 25, changing the airflow in a perpendicular direction.

[0044] As shown in FIG. 7(A), the fascia 25 has a shape larger than the planar shape of the blow-out opening 21. The fascia 25 is formed with a dimension longer than the dimension of the blow-out opening 21 in the direction in which the airflow is straightened. That is, when the airflow is straightened downward as in the illustrated example, the lower end of the fascia 25 extends downward from the lower end of the blow-out opening 21. This prevents the airflow that travels straight from the blow-out opening 21 perpendicular to the opening surface from continuing straight, but can reliably abut against the fascia 25 to change the airflow direction. In addition, the airflow that flows downward from the adjacent blow-out opening 21 immediately above easily forms a vortex V on the outer surface side of the fascia 25, and the airflow that flows outside of the vortex V is easily attracted to the blow-out opening. The length of the fascia 25 in the airflow straightening direction is preferably 1.2 times or more, more preferably 1.5 to 3 times, and particularly preferably 1.5 to 2 times, the length of the blow-out opening 21 in the airflow straightening direction.

[0045] The corners between the top plate 23 and the skirting board 25 and the corners between the side plates 24 and the skirting board 25 may be slightly rounded, but it is preferable that they are connected at approximately right angles. By forming these corners at approximately right angles, the airflow that travels straight from the air outlet 21 and abuts against the skirting board 25 is more likely to change to a right angle thereafter. When rounding these corners, the radius should be 1 / 2 or less, preferably 1 / 10 or less, of the length that the top plate 23 and the side plates 24 protrude from the air outlet 21.

[0046] As shown in Fig. 5 and Fig. 7, it is preferable to dispose the hood inter-side plates 26 connecting the hoods 22, 22 on both sides between the hoods 22, 22 adjacent to each other in the direction of the airflow straightened by the hoods 22, because this makes it easier for the airflow straightened by the hoods 22 to flow toward the adjacent hoods 22. In the illustrated example, the hood inter-side plates 26 are provided between the hoods 22, 22 adjacent to each other in the vertical direction. The hood inter-side plates 26 connect the side plates 24 of the adjacent hoods 22, 22, and are formed to have approximately the same width as the side plates 24 of the hoods 22 (their protruding lengths from the front plate of the air-conditioning outlet 20 are approximately the same). It is preferable to similarly provide the hood inter-side plates 26 from the lowest hood 22 to the lower end of the air-conditioning outlet 20. The front side between these hood inter-side plates 26, 26 is open.

[0047] (Air conditioning area control method) Next, a method for controlling an air-conditioning zone according to the present invention will be described. Before describing the specific control method, definitions of terms used in the present invention will be described.

[0048] In the present invention, the difference between the set temperature Te of the air-conditioned area 4 and the blowing air temperature Tb of the air conditioner 1 is defined as the supply air temperature difference T (T=Te-Tb). The set temperature Te of the air-conditioned area 4 is the temperature required for products placed in the air-conditioned area 4, and is a temperature that is arbitrarily set by the user. The blowing air temperature Tb of the air conditioner 1 is the temperature of air adjusted by passing through the cooling coil unit 7 of the air conditioner 1, and is the temperature of air blown out from the blowing opening 21 of the air conditioner 1. For example, when the blowing air temperature Tb of the air conditioner 1 is 16°C, if the set temperature Te of the air-conditioned area 4 is 20°C, the supply air temperature difference T is 4 deg (°C), if the set temperature Te is 24°C, the supply air temperature difference T is 8 deg (°C), if the set temperature Te is 26°C, the supply air temperature difference T is 10 deg (°C), and if the set temperature Te is 28°C, the supply air temperature difference T is 12 deg (°C).

[0049] In the present invention, the ratio of the airflow Wb to the maximum airflow Wmax of the air conditioner 1 is defined as the maximum airflow ratio W (W=W / Wmax×100%). The maximum airflow Wmax is obtained from the specifications of the air conditioner 1, and the airflow Wb can be adjusted by, for example, inverter control of the blower unit 8 (fan) provided in the air conditioner 1.

[0050] In the present invention, the ratio of the occupied area Ad of the heat load 2 installed in the space 3 to the floor area Ar of the space 3 is defined as the load area occupancy rate A (A=Ad / Ar×100%). The occupied area Ad of the heat load 2 is the area of ​​the heat-generating heat load 2 when viewed in a plan view, and when there are multiple heat loads 2, it is the total area of ​​all of them.

[0051] In the control method according to the present invention, a relationship between the load area occupancy rate and the height above the floor is obtained for each supply air temperature difference, with the maximum airflow ratio as a parameter, and the supply air temperature difference, maximum airflow ratio, and load area occupancy rate for obtaining an arbitrary height above the floor are determined from these relationships, as shown in Fig. 12. That is, the supply air temperature difference is determined from the required temperature of the product to be placed in the air-conditioned area 4 and the blowing air temperature of the air conditioner 1, and the height above the floor of the air-conditioned area 4 is obtained by setting the maximum airflow ratio of the air conditioner 1 at this supply air temperature difference and arranging the thermal load 2 at a predetermined load area occupancy rate.

[0052] Also, as shown in Fig. 13, a relationship between the load area occupancy rate and the height above the floor, with the supply air temperature difference as a parameter, may be obtained for each maximum air flow ratio, and the supply air temperature difference, maximum air flow ratio, and load area occupancy rate for obtaining an arbitrary height above the floor may be determined from these relationships. In the relationship diagram of Fig. 13, the maximum air flow ratio is determined first, and then the other conditions are determined.

[0053] The relationship between the load area occupancy rate and the height above the floor shown in FIG. 12 and FIG. 13 was obtained by a simulation which will be described in detail later.

[0054] In the relationship diagrams shown in Figs. 12 and 13, the relationship between the load area occupancy rate and the height above the floor shows a linear tendency, so that each value can be easily set from the line diagram and the tendency can be easily understood. Each value may be determined from these graphs, or each value may be determined from an approximation formula obtained from these graphs. In addition, since the relationship diagram in Fig. 12 shows the relationship between the height above the floor for each supply air temperature difference, and the relationship diagram in Fig. 13 shows the relationship between the height above the floor for each maximum air volume ratio, it is possible to deal with both cases where the temperature of the air-conditioned area 4 is determined in advance and cases where the air volume is determined in advance, and it is a control method that can flexibly deal with a wide range of air conditioning designs. Each value obtained from the relationship diagrams shown in Figs. 12 and 13 is not a value obtained as a result of trial and error, but is obtained from a relationship diagram obtained in advance, so that it is possible to set a value that takes into account the energy efficiency of the air conditioner 1, and it is possible to achieve energy saving.

[0055] The air conditioner according to the present invention includes a controller that uses the above-mentioned method for controlling the air conditioning zone. This controller may be built into the air conditioner 1, or may be provided separately from the air conditioner 1.

[0056] (simulation) An outline of the simulation for obtaining the relationship diagrams of FIGS. 12 and 13 will be described below.

[0057] In the simulation, as shown in Figs. 14 and 15, for a space 3 having a floor area of ​​7.2 m × 20.8 m and a height of 8 m, one side-blowing type air conditioner 1 having the above-mentioned air-conditioning outlet 20 on the blowing surface and a specification of a maximum air volume of 9000 CMH was installed near the wall in the center of one of the short sides, and the heat density was 250 W / m 2 Using a model in which multiple heat loads 2 are arranged in various patterns in the center of a room, the temperature distribution up to a height of 5 m above the floor was calculated when the airflow rate of the air conditioner 1 and the arrangement pattern of the heat loads 2 were changed.

[0058] The temperature measurement points were within a range of 1 m from both long walls as shown in Fig. 16, and the average temperature on the horizontal surface at each height above the floor in this evaluation area was obtained. An example is shown in Fig. 17. Fig. 17 is a graph showing the distribution of supply air temperature difference in the height direction when the air conditioner's supply air temperature and supply air volume are constant and the arrangement pattern of heat load 2 is arranged as shown in Figs. 16 and 17. As shown in Fig. 17, there is a transition region in the middle region in the height direction where the supply air temperature difference increases almost linearly as the height above the floor increases, and above and below this region the supply air temperature difference is almost constant or changes gradually.

[0059] As another example, Fig. 18 is a graph showing the height above the floor at which 95% of the horizontal area of ​​the evaluation area satisfies the specified supply air temperature difference when the maximum air volume ratio is changed. In the range of maximum air volume ratio 50 to 90%, the height above the floor of the supply air temperature difference tends to increase linearly as the maximum air volume ratio increases.

[0060] <Comparative Example 1> As Comparative Example 1, initially, an air conditioner 1 was used in which FFUs were arranged on the upper and lower levels, and the air blowing volume could be changed between the upper and lower FFUs, with the idea that by changing the air blowing volume between the upper and lower levels, it might be possible to arbitrarily change the height above the floor of the air-conditioned area 4, and a simulation was performed. The conditions of the blowing air temperature and maximum air volume ratio of the air conditioner 1 at this time are shown in Table 1. The air volume ratio between the upper and lower levels was adjusted so that the total air volume ratio of the entire air conditioner was 140% in each case. [Table 1]

[0061] The results are shown in Figures 19 and 20. Figure 19 is a diagram showing the temperature distribution in the vertical cross section of space 3, with the thick lines in (A) to (D) being isothermal lines showing the same temperature. Figure 20 is a graph showing the supply air temperature difference in the height direction in each case. As shown in Figures 19(A) to (D), the thick lines showing the same temperature are in roughly the same region in each case, and as shown in Figure 20, the temperature distribution in the height direction is also roughly the same in each case, with no significant differences apparent.

[0062] Therefore, even if the air volumes of the upper and lower stages of the air conditioner 1 are changed, the height above the floor of the air-conditioned area 4 cannot be changed.

[0063] <Comparative Example 2> Next, as Comparative Example 2, as shown in Fig. 21, eight air outlets 21 with openable and closable shutters are arranged on each of the upper and lower stages, and a simulation was performed under the assumption that the height above the floor of the air-conditioned area 4 may be arbitrarily changed using an air conditioner 1 equipped with air-conditioning outlets 20 that can change the aperture ratio of the outlets on the upper and lower stages by opening and closing the shutters. In Fig. 21, the air outlets 21 filled in black have their shutters closed, and the other air outlets 21 have their shutters open. The upper and lower stages have the same air volume, so the air speed of an opening ratio of 50% is about twice that of an opening ratio of 100%.

[0064] The results are shown in Figures 22 and 23. As shown in Figures 22(A) to (D), the thick lines indicating the same temperature are present in approximately the same region in each case, and as shown in Figure 23, the temperature distribution in the height direction is also approximately the same in each case, with no significant differences apparent.

[0065] Therefore, even if the opening ratio of the air outlet is changed, the height above the floor of the air-conditioned area 4 cannot be changed.

[0066] <Example> Based on the results of Comparative Example 1 and Comparative Example 2, the air volumes of the upper and lower stages were set to the same 1:1, and the opening ratio of the air outlets was also set to 100% fully open for both the upper and lower stages. Under these conditions, the maximum air volume ratio was changed in the range of 50% to 100% as shown in Table 2, and the load area occupancy rate was changed by the arrangement of the heat load 2 as shown in Figure 24. The temperature of the air-conditioned area 4 relative to the height above the floor was calculated. As mentioned above, the heat density was 250 W / m for all load area occupancy rates. 2 The load area occupancy rate is constant at 11.5°C. In other words, the smaller the load area occupancy rate, the higher the heat load 2 per unit, and the stronger the updraft that will be generated. The total number of heat load 2 units is the same at 27 units for a distributed load area occupancy rate of 11.5% and a concentrated load area occupancy rate of 11.5%; however, the layout is different. In the "distributed" case, nine units are spaced apart, while in the "concentrated" case, 27 units are placed together. The air supply temperature of air conditioner 1 was kept constant at 17°C. [Table 2]

[0067] The results when the load area occupancy rate is 19.2% are shown in Figs. 25 to 28. In Figs. 25(A) to 25(F), when attention is paid to the isotherms of the same temperature (26°C, supply air temperature difference 9°C) shown by the thick lines, when the maximum airflow ratio is gradually reduced from 100%, the height of the isotherm (supply air temperature difference) below a certain temperature tends to gradually decrease. This shows that the height above the floor of the air-conditioned area 4 can be adjusted by adjusting the maximum airflow ratio. This tendency is also seen in the temperature transition region of the intermediate area (area sandwiched between dotted lines in Fig. 26) where the temperature gradient changes relatively linearly as shown in Fig. 26(F). Note that the isotherm of 26°C when the maximum airflow ratio is 100% in Fig. 25(F) is present outside the margin above the upper limit of the vertical axis.

[0068] Figure 27 shows the relationship between the height above the floor and the maximum airflow ratio to satisfy each supply air temperature difference (8, 9, 10, 12 deg) when the horizontal area ratio is 95% or more. From this graph, it can be seen that the height above the floor increases by increasing the maximum airflow ratio, and that this relationship shows a linear relationship. It can also be seen that the height above the floor of the air-conditioned area 4 can be adjusted by adjusting the supply air temperature difference.

[0069] Figure 28 shows the relationship between supply air temperature difference and floor height, with the maximum airflow ratio as a parameter. From this graph, it can be seen that the floor height increases as the supply air temperature difference increases, and that the relationship is linear.

[0070] Similarly, the results for a load area occupancy rate of 11.5% dispersion are shown in Figures 29 to 32, the results for a load area occupancy rate of 11.5% concentration are shown in Figures 33 to 36, the results for a load area occupancy rate of 7.7% are shown in Figures 37 to 40, the results for a load area occupancy rate of 3.8% are shown in Figures 41 to 44, and the results for a load area occupancy rate of 2.6% are shown in Figures 45 to 48. These results also show the same trends as above.

[0071] From the above results, the relationship between supply air temperature difference and height above floor for each maximum airflow ratio, with load area occupancy rate as a parameter, is summarized as shown in Figure 49. As shown in Figures 49(A) to (F), it can be seen that when the load area occupancy rate is reduced, the height above floor at which a constant temperature is achieved tends to increase. This is thought to be because in this simulation, in which the heat density was constant, a lower load area occupancy rate generates a larger amount of heat per unit area and generates a stronger updraft. Therefore, it can be seen that the height above floor of the air-conditioned area 4 can be adjusted by adjusting the load area occupancy rate.

[0072] Furthermore, from the above results, the relationship between the load area occupancy rate and the height above the floor for each supply air temperature difference, with the maximum air volume ratio as a parameter, is found as shown in Figure 12. As described above, from the relationship diagram shown in Figure 12, the supply air temperature difference, maximum air volume ratio, and load area occupancy rate for obtaining an arbitrary height above the floor can be determined.

[0073] Furthermore, from the above results, the relationship between the load area occupancy rate and the height above the floor for each maximum air flow ratio, with the supply air temperature difference as a parameter, is found as shown in Figure 13. Note that in Figure 13, the horizontal axis showing the load area occupancy rate is expressed in logarithmic scale. As described above, the supply air temperature difference, maximum air flow ratio, and load area occupancy rate for obtaining an arbitrary height above the floor can be determined from the relationship diagram shown in Figure 13.

[0074] [Other examples] In order to maintain the space 3 at a positive pressure, an outside air introduction path (duct) may be provided to introduce outside air into the space 3. It is preferable that the air supplied to the room through this outside air introduction path is outside air whose temperature, humidity, and cleanliness have been adjusted by an outside air treatment device. The outside air introduction path is configured to blow air from the ceiling or wall surface of the space 3 toward the side (horizontal direction) of the non-air-conditioned area 5. [Explanation of symbols]

[0075] 1...air conditioner, 2...heat load, 3...space, 4...air-conditioned area, 5...non-air-conditioned area, 6...outdoor air processor, 7...cooling coil section, 8...blower section, 9...filter section, 11...air introduction section, 13...chamber, 20...air-conditioning outlet, 21...outlet opening, 22...hood

Claims

1. A method for controlling an air-conditioning area for setting a height above a floor of an area to be air-conditioned that needs to be maintained within a predetermined temperature range by air conditioning to a predetermined height, the method comprising the steps of: The difference between the set temperature of the air-conditioned area and the blown air temperature of the air conditioner is defined as the supply air temperature difference, the ratio of the blown air volume to the maximum air volume of the air conditioner is defined as the maximum air volume ratio, and the ratio of the occupied area of ​​the heat load installed in the space to the floor area of ​​the space is defined as the load area occupancy rate, A relationship between the load area occupancy rate and the height above the floor is obtained for each supply air temperature difference, with the maximum air volume ratio as a parameter; A method for controlling an air-conditioning area, characterized in that the supply air temperature difference, maximum air volume ratio and load area occupancy rate for obtaining an arbitrary height above the floor are determined from these relationships.

2. A method for controlling an air-conditioning area for setting a height above a floor of an area to be air-conditioned that needs to be maintained within a predetermined temperature range by air conditioning to a predetermined height, the method comprising the steps of: The difference between the set temperature of the air-conditioned area and the blown air temperature of the air conditioner is defined as the supply air temperature difference, the ratio of the blown air volume to the maximum air volume of the air conditioner is defined as the maximum air volume ratio, and the ratio of the occupied area of ​​the heat load installed in the space to the floor area of ​​the space is defined as the load area occupancy rate, A relationship between the load area occupancy rate and the height above the floor is obtained for each maximum air volume ratio, with the supply air temperature difference as a parameter; A method for controlling an air-conditioning area, characterized in that the supply air temperature difference, maximum air volume ratio and load area occupancy rate for obtaining an arbitrary height above the floor are determined from these relationships.

3. The air conditioner includes a cooling coil unit that adjusts the temperature of the air, a blower unit that compresses and blows the air, and a filter unit that purifies the air.

3. The method for controlling an air-conditioned area according to claim 1, wherein the air conditioner is a lateral blow-out type that blows conditioned air laterally from a side of the space.

4. 3. The method for controlling an air-conditioned area according to claim 1, wherein a hood is provided at the air outlet of the air conditioner to suppress a draft airflow in a forward direction and to straighten the airflow downward.

5. 3. The method for controlling an air-conditioned area according to claim 1, wherein a height of the air-conditioned area above a floor is set to 1.5 m or less when a product requiring a guaranteed temperature range is placed in the air-conditioned area.

6. 3. The method for controlling an air-conditioning zone according to claim 1, wherein the supply air temperature difference is in the range of 8 to 12°C, the maximum air volume ratio is in the range of 50 to 100%, and the load area occupancy rate is in the range of 2 to 20%.

7. 3. An air conditioning system comprising a controller using the method for controlling an air conditioning zone according to claim 1 or 2.

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