CN1677006B - ventilation system - Google Patents

Abstract

The present invention provides a ventilation and ventilation system that performs ventilation by supplying low-temperature air (SA) into an air-conditioned space and exhausting (EA) heated air that rises in the air-conditioned space, wherein The air supply port of the air (SA) is equipped with a plurality of guide vanes (30) that impart rotational components to the low-temperature air blown into the air-conditioned space, and these multiple guide vanes (30) are arranged radially around the central axis of the air supply port. configuration, and these guide vanes (30) are inclined at the same angle with respect to the plane perpendicular to the central axis of the air supply port, and a plurality of guide fins (30) are formed around the air supply port. The central axis is the cylindrical inner wall surface of the central axis.

Description

ventilation system

technical field

The invention relates to a ventilation system.

Background technique

Ventilation systems are known as air conditioning systems capable of reducing the concentration of pollutants in living areas in conditioned spaces and maintaining comfort even at high cooling supply air temperatures. In this ventilation system, air with a temperature slightly lower than room temperature is supplied at a slow speed to the living area formed in the lower part of the air-conditioned space, and the air is heated by heat generating bodies (such as people) etc. present in the living area. An updraft is generated, thereby transporting pollutants such as dust and gas generated in the air-conditioned space to the upper side of the air-conditioned space. According to the reference (Yuan, X., 0, Chen and L.R.Gllcksman: Performance Evaluation and DesignGuideline for Displacement Ventilation, ASHRAE Trans., 105(1999), pp.308), regarding the air supply velocity in this ventilation system, From the viewpoint of reducing airflow discomfort and preventing thermal updraft agitation in residential areas, it is recommended to keep it below 0.2m/s. Furthermore, in the ventilation system, ventilation in the air-conditioned space is performed by exhausting pollutants together with heated air from an exhaust port provided on a ceiling or the like.

In this ventilation system, although there is an area with high temperature and high pollutant concentration above the air-conditioned space, it is pushed out sequentially by the low-temperature air supplied into the air-conditioned space, resulting in high temperature and high pollutant concentration. The air is discharged without being disturbed, so it has the advantage of ensuring a clean environment in the living area below the air-conditioned space, and even if the supply air temperature is lowered, the temperature of the living area can be maintained in a comfortable range. Thus, the ventilation system is expected as an air-conditioning system capable of saving energy and having high ventilation efficiency.

However, in such a ventilation system, in order to ensure comfort by suppressing the temperature difference between the feet and the head below, for example, 3° C. Performs high-volume operation with reduced temperature difference between supply and exhaust. Therefore, a large number of large air supply units had to be arranged in the air-conditioned space, and there was a problem that it was difficult to secure installation places for the air supply units. Moreover, in the case where pollutants are generated from a part accompanied by heat generation or its vicinity, since the pollutants are discharged from the living area to the ceiling due to the thermal updraft, although the concentration of pollutants in the living space can be kept low, However, in the absence of concomitant heating, the transport dilution of pollutants takes place, so that there is a risk that the occupants are exposed to high concentrations of polluted air.

Therefore, in order to ensure the installation place obtained by compacting the air supply unit, reduce the temperature gradient in the living area, and improve the pollutant dilution effect in the living area, the following ventilation system is proposed, that is, through a plurality of The guide fins impart a swirl component to the blown air, increase the induction amount near the air supply unit, and improve the diffusivity of the air supply (Japanese Laid-Open Patent Publication No. 2002-372268).

Contents of the invention

By diffusing the supplied air through the ventilation system, the uncomfortable feeling of the air flow can be reduced without increasing the equipment cost, and the temperature difference between the upper and lower sides of the living area can also be reduced. The present invention further improves the ventilation system. That is, an object of the present invention is to provide a ventilation system that can further enhance the swirl component of the blown air, increase the amount of swirl induction, and further improve the airflow attenuation characteristics than before.

According to the present invention, there is provided a ventilation and ventilation system for supplying low-temperature air into an air-conditioned space and exhausting the heated air that has been heated and risen in the air-conditioned space to perform ventilation, characterized in that the low-temperature air The air outlet is equipped with a plurality of guide fins that impart a rotational component to the low-temperature air blown into the air-conditioned space. These guide fins are radially arranged around the central axis of the air outlet, and these guide fins They are arranged obliquely at the same angle with respect to a plane perpendicular to the central axis of the air supply port, and a cylindrical inner wall surface with the central axis of the air supply port as the central axis is formed around these plurality of guide fins. The length of the inner wall surface along the central axis direction of the air supply port is at least half of the width of the guide fin along the central axis direction of the air supply port. The inner wall surface may be made of a sound-absorbing material. Moreover, a plurality of the above-mentioned air supply ports are arranged in a row, and a plurality of guide vanes that impart a rotational component to the low-temperature air are attached to each air supply port, and each air supply port is formed with a ring that surrounds the plurality of guide vanes. On the inner wall surface of the cylindrical shape, the inclination directions of the respective guide fins are formed to be opposite to each other at the adjacent air supply ports. Furthermore, a perforated plate may be provided in front of the air inlet. In this case, the opening ratio of the perforated plate is preferably 40% or more. Furthermore, the relationship between the opening diameter D of the air supply port and the distance M from the air supply port to the perforated plate is M/D≧0.07.

According to the present invention, by forming the cylindrical inner wall surface around the guide fins, it is possible to impart more rotational components to the low-temperature air blown into the air-conditioned space than without the cylindrical inner wall surface. Therefore, the induction amount (induction ratio) of the air in the air-conditioned space induced by the flow of blown low-temperature air can be further increased, and the velocity of the low-temperature air blown into the air-conditioned space can be rapidly decelerated and rapidly increased in temperature. Therefore, the upper and lower temperature differences in the air-conditioned space can be further reduced. Also, even pollutants that are not discharged from the living area to the ceiling portion by the thermal updraft can be diluted. According to the present invention, it is possible to manufacture a more compact air supply unit than conventional ventilation systems.

Description of drawings

FIG. 1 is a schematic configuration diagram for explaining a ventilation system according to an embodiment of the present invention.

Fig. 2 is a front view of the air supply unit.

Fig. 3 is an enlarged cross-sectional view along the Z-Z direction in Fig. 2 .

Fig. 4 is a perspective view of an air inlet to which a guide vane is attached to impart a rotation component in a counterclockwise rotation direction to low-temperature air when viewed from the indoor side of the air-conditioned space.

Fig. 5 is a perspective view of an air inlet to which guide fins are attached to impart a rotation component in a clockwise rotation direction to low-temperature air when viewed from the indoor side of the air-conditioned space.

FIG. 6 is an explanatory view of an air supply port in which the rotational components of low-temperature air blown from adjacent air supply ports are alternately in opposite rotational directions.

FIG. 7 is an explanatory diagram of an air supply port in which the rotation components of low-temperature air blown from adjacent air supply ports have the same rotation direction.

Fig. 8 is a diagram of an air supply port that is set so that the rotational components of the low-temperature air blown out from the adjacent air supply ports are in mutually opposite rotation directions between any of the air supply ports arranged up and down and the laterally arranged air supply ports. Illustrating.

9 is a graph showing changes in the maximum wind speed with respect to the distance from the air supply unit in the ventilation system of the present invention in which the guide fins are surrounded by a cylinder and in the ventilation system of a conventional example in which the cylinder is omitted. picture.

Fig. 10 shows the temperature difference between the air supply and exhaust air with respect to the distance from the air supply unit for the ventilation system of the present invention in which the guide fins are surrounded by a cylinder and the ventilation system of a conventional example in which the cylinder is omitted. to represent the graph of the non-dimensional temperature change under the feet.

Fig. 11 is a graph showing the relationship between the average airflow velocity and the length of the cylindrical inner wall surface (cylinder) surrounding the guide fins, for the case where the flow rate of low-temperature air is 90 m ³ /h.

Fig. 12 is a graph showing the relationship between the average airflow velocity and the length of the cylindrical inner wall surface (cylinder) surrounding the guide fins, for a case where the flow rate of low-temperature air is 150 m ³ /h.

Fig. 13 is a graph comparing the noise generated when the material of the good cylinder is changed.

Fig. 14 is an explanatory diagram of an embodiment of the present invention in which a porous plate having a plurality of air holes is arranged in front of the air supply unit in parallel with the front surface.

Fig. 15 is a graph showing the relationship between the opening ratio of the porous plate (the area of the ventilation holes) and the maximum wind speed of low-temperature air.

Fig. 16 is a graph showing the relationship between the separation distance from the air supply port to the perforated plate and the maximum wind speed of low-temperature air.

Fig. 17 is an explanatory diagram of an embodiment in which a cylinder is omitted when the front surface of the air supply unit has a sufficient thickness.

Fig. 18 is a perspective view of a guide fin formed by punching out a circular flat plate.

Fig. 19 is a plan view of the air-conditioned space according to the embodiment of the present invention and comparative examples 1 and 2, showing the arrangement of various devices and the like.

FIG. 20 is a table showing the operating state of the air conditioner when the Example of the present invention is compared with Comparative Examples 1 and 2. FIG.

FIG. 21 is a graph showing the upper and lower temperature distributions at a point D, comparing Examples of the present invention with Comparative Examples 1 and 2. FIG.

FIG. 22 is a graph showing the wind speed distribution at point A. FIG.

FIG. 23 is a graph showing the wind speed distribution at point B. FIG.

FIG. 24 is a graph showing the wind speed distribution at point C. FIG.

FIG. 25 is a graph showing the wind speed distribution at point D. FIG.

FIG. 26 is a graph comparing PMV and SET ^* of a floor 1 m at Site D. FIG.

FIG. 27 is a graph showing the concentration distribution at the point A when the tracer gas is released from the heat-generating device H3 in a non-dimensional manner by the concentration at the exhaust port.

FIG. 28 is a graph showing the concentration distribution at the point C in a case where the tracer gas is released from the heat-generating device H3 in a non-dimensional manner as the concentration at the exhaust port.

FIG. 29 is a graph showing the concentration distribution at the point D in the case where the tracer gas is released from the heat-generating device H3 in a non-dimensional manner as the concentration at the exhaust port.

30 is a graph showing the concentration distribution at point A in the case where the tracer gas is released from 1 m above the floor of point B where there is no heat generation, in a non-dimensional manner, in terms of the concentration at the exhaust port.

FIG. 31 is a graph showing the concentration distribution at point C in a case where tracer gas is released from 1 m above the floor of point B where there is no heat generation, in a non-dimensional manner, in terms of the concentration at the exhaust port.

32 is a graph showing the concentration distribution at point D in a case where tracer gas is released from 1 m above the floor of point B where there is no heat generation, in a non-dimensional manner, in terms of the concentration at the exhaust port.

33 is a graph comparing the upper and lower temperature distributions at point D when the air supply temperature is 30°C and the air-conditioning air volume is 4000m ³ /h and the warm air operation is performed when the outside air temperature is 10°C.

Detailed ways

Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a schematic configuration diagram illustrating a ventilation system 1 according to an embodiment of the present invention.

The air-conditioned space 10 is, for example, an office, a computer room, a reception room, a banquet hall, an amusement park, a printing room, a patient room, a toilet, a kitchen, a mechanical room, a boiler room, a factory, etc., and is distinguished by ceilings, floors, and side walls. In the example shown in FIG. 1 , in the residential area 11 formed below the inside of the air-conditioned space 10 , for example, a person 12 exists as a heat generating body. An air supply port 15 is provided at the bottom of one side (the right side of the air-conditioned space 10 in the figure) 17 in the air-conditioned space 10, and an exhaust port 16 is also provided at the top of one side 17 in the air-conditioned space 10. . In addition, the detailed structure of the air supply port 15 will be described below. An air supply unit 20 is arranged on the back side of the lower part of the side surface 17 of the air-conditioned space 10 . The front surface 21 of the air supply unit 20 is exposed at the lower part of one side surface 17 of the air-conditioned space 10 .

In this way, on the front surface 21 of the air supply unit 20 exposed at the lower part of the side surface 17 of the air-conditioned space 10, as shown in FIG. The low-temperature air SA produced by taking outside air OA into the air conditioner 22 is supplied to the air supply unit 20 through the air supply passage 23 . Therefore, the low-temperature air SA is supplied to the living area 11 below the inside of the air-conditioned space 10 from the plurality of air supply ports 15 formed on the front surface 21 of the air supply unit 20 . The air conditioner 22 is provided with a cooler 25 and a filter (not shown) for cooling the outside air 0A and making low-temperature air SA, and has a filter (not shown) for supplying the produced low-temperature air SA to the air conditioner through the air supply passage 23 and the air supply unit 20 . The blower fan 27 etc. in the space 10.

As shown in FIG. 3 , a plurality of guide fins 30 for imparting a swirling component to the low-temperature air SA blown out into the air-conditioned space 10 are respectively fixed to each air supply port 15 . A support member 31 is disposed on the central axis of each air outlet 15, and a plurality of guide fins 30 are mounted on the support member 31 at approximately equal intervals, so that the plurality of guide fins 30 surround the air outlet 15 radially. Central axis configuration.

The plurality of guide vanes 30 are obliquely arranged at the same inclination angle relative to the plane perpendicular to the central axis 15' of the air supply port 15 (for example, the front face 21 of the air supply unit 20). 4 and 5 are explanatory views of the inclination angles of the guide fins 30 . In FIGS. 4 and 5 , the inclination directions of the guide fins 30 are opposite. That is, in FIG. 4 , when the front surface 21 of the air-sending unit 20 is viewed from the indoor side of the air-conditioned space 10 with respect to the low-temperature air SA blown into the air-conditioned space 10 from the air-supplied port 15, in order to give a counterclockwise direction As a rotational component, each guide vane 30 is provided obliquely. On the other hand, in FIG. 5 , when the air supply unit 20 is viewed from the indoor side of the air-conditioning space 10 with respect to the low-temperature air SA blown into the air-conditioning space 10 from the air supply port 15 , in order to impart a clockwise rotation As a component, each guide fin 30 is provided obliquely.

In this way, by radially attaching the guide fins 30 in which the support member 31 is inclined toward the center to each air supply port 15, when the low-temperature air SA flowing into the air supply port 15 from the inside of the air supply unit 20 passes through the air supply port 15, it can be forcibly It flows along the surface of each guide fin 30 . Therefore, the low-temperature air SA blown into the air-conditioned space 10 from the air supply port 15 can be provided with a clockwise or counterclockwise rotation component about the central axis 15'.

As mentioned above, on the front surface (the surface on the inner side of the room forming the air-conditioned space 10 ) 21 of the air supply unit 20, although a plurality of air supply ports 15 are arranged vertically and horizontally, the low temperature blown out from the adjacent air supply ports 15 The rotational components of the air SA have a relationship of mutually opposite rotational directions. That is, as shown in FIG. 6, when four air supply ports 15a, 15b, 15c, and 15d arranged in the up-and-down direction are taken as an example to illustrate, at the uppermost air supply port 15a and the third air supply port 15c from the top, the guide fins The inclination direction of 30 is the state illustrated in FIG. 4 , and from these air supply ports 15a and 15c, blowing air is blown out in the case where the front surface 21 of the air supply unit 20 is viewed from the indoor side of the air-conditioned space 10, and the counterclockwise rotation direction is given. Composition of cryogenic air SA. On the other hand, at the second air supply port 15b and the fourth air supply port 15d from the top, the inclination direction of the guide fins 30 is the state illustrated in FIG. When the front surface 21 of the air supply unit 20 is seen from the indoor side, the low-temperature air SA provided with a rotation component in the clockwise rotation direction. In this way, low-temperature air SA rotating in opposite rotation directions is blown out between the adjacent air supply port 15a and air supply port 15b, air supply port 15b and air supply port 15c, air supply port 15c and air supply port 15d.

That is, as shown in FIG. 7, the low-temperature air SA (in the example shown in FIG. In the case of low-temperature air SA) rotating counterclockwise, between the air supply port 15a' and the air supply port 15b', between the air supply port 15b' and the air supply port 15c', and between the air supply port 15c' and the air supply port 15c' Between the blowing ports 15d', the low-temperature air SA is blown out in directions that cancel each other out. In this way, the swirling component of the low-temperature air SA blown out from the respective air outlets 15a', 15b', 15c', and 15d' is canceled out.

On the other hand, as illustrated in FIG. 6, if the rotation components of the low-temperature air SA blown out from the air outlets 15a, 15b, 15c, and 15d are alternately in opposite rotation directions, the air outlet 15a and the air outlet 15b Between the air supply port 15b and the air supply port 15c, and between the air supply port 15c and the air supply port 15d, the low-temperature air SA is also blown out along the same direction, so it is blown out from each air supply port 15a, 15b, 15c, 15d The rotational components of the low-temperature air SA are not cancelled, contributing to the mutual rotational motion.

In addition, in FIG. 6, although the relation of the air supply ports 15 arranged up and down has been described, as previously explained in FIG. Air port 15. In the illustrated form, as shown in FIG. 8 , the inclination direction of the guide vane 30 provided on each air supply port 15 is set so that, in the relationship between the air supply ports 15 arranged up and down, The rotation components of the low-temperature air SA blown out by 15 are in the relationship of opposite rotation directions, but the inclination direction of the guide vane 30 provided on each air supply port 15 is set so that, in the relation of the air supply ports 15 arranged left and right, from The rotational components of the low-temperature air SA blown out from the adjacent blowing ports 15 are in the same rotational direction as each other.

As shown in FIG. 3 , a cylinder 32 is attached around a plurality of guide fins 30 attached to each air outlet 15 . The cylinder 32 is attached to each of the air outlets 15 in such a state that the central axis coincides with the central axis 15' of the air outlet 15. The inner diameter of the cylinder 32 is set to be substantially equal to the outer diameter of the plurality of guide vanes 30 attached to the respective air outlets 15 . Therefore, in each air supply port 15, the outer circumference of the plurality of guide fins 30 is surrounded by the inner wall surface 33 of the cylinder 32 (cylindrical inner wall surface 33 having the central axis 15' of the air supply port 15 as a central axis). . Therefore, as shown in Figure 4 and Figure 5, the low-temperature air SA blown into the air-conditioned space 10 from the inside of the air supply unit 20 through the air supply port 15 passes in the cylinder 32 installed on each air supply port 15. Since the inside of the cylinder 32 flows along the surface of each guide vane 30, the low-temperature air SA is forcibly given a rotation component in a clockwise rotation direction or a counterclockwise rotation direction.

Here, as shown in FIG. 3 , in each air supply port 15 , the length L of the cylinder 32 in the direction along the central axis 15 ′ of the air supply port 15 is set so as to be along the central axis 15 ′ of the same air supply port 15 . More than half of the width 1 of the guide fin 30 in the direction. Therefore, at least half or more of the width 1 of the guide fin 30 is surrounded by the inner wall surface 33 of the cylinder 32 in the direction along the central axis 15' of the air inlet 15. In addition, in the example shown in FIG. 3 , the length L of the cylinder 32 is set to be longer than the width 1 of the guide vane 30 , so that, in the direction along the central axis 15 ′ of the air supply port 15 , The entire width 1 of the guide fin 30 is surrounded by the inner wall surface 33 of the cylinder 32 .

As shown in FIG. 1 , an exhaust duct 41 including an exhaust fan 40 is connected to the exhaust port 16 arranged at the upper portion of the air-conditioned space 10 . Therefore, air stagnant in the upper portion of the air-conditioned space 10 (air heated by heat loads of people present in the air-conditioned space 10 or office machines) is discharged to the outside through the exhaust duct 41 .

In addition, in the ventilation system 1 configured as above, the low-temperature air SA produced by the air conditioner 22 is supplied into the air-conditioned space 10 from the air supply passage 23 and the air supply unit 20 through the air supply port 15 by the operation of the air supply fan 27 . When passing through the air supply port 15, the low-temperature air SA passes through the cylinder 32 installed on each air supply port 15. , forcibly imparts a clockwise or counterclockwise rotation component to the low-temperature air SA. In this way, the low-temperature air SA is sent out into the air-conditioned space 10 while rotating from each air-sending port 15 .

In this case, since the periphery of the guide vane 30 is surrounded by the cylindrical inner wall surface 33 on each air supply port 15, compared with the case where there is no cylinder 32 (inner wall surface 33), it is possible to reliably send air from The low-temperature air SA blown into the air-conditioned space 10 by each blower port 15 imparts a stronger swirl component.

Then, when the low-temperature air SA is blown into the air-conditioned space 10 while rotating from each air-supply port 15 , the air in the air-conditioned space 10 is induced to move together with the low-temperature air SA blown out from each air-supply port 15 . In this case, in the ventilation system 1 shown in the figure, since a swirling component is imparted to the low-temperature air SA blown out from the air inlet 15, the induced amount of air in the air-conditioned space 10 induced by the low-temperature air SA (Induction ratio) increases. Along with this, the velocity of the low-temperature air SA is rapidly decelerated after being blown out from each air outlet 15 according to the principle of conservation of the amount of motion.

Here, comparing the case where the periphery of the guide fin 30 is surrounded by the cylindrical inner wall surface 33 (cylinder 32 ) with the case where the cylinder 32 is omitted and the periphery of the guide fin 30 is open, the following results are obtained. opinion. That is, on the front 21 (height is 0.9m, width is 0.3m) of air supply unit 20, the circular air supply opening 15 of 12 places diameter D=94mm is set, when each air supply opening 15 is provided with guide vane 30, to by The airflow velocity with respect to the distance from the front face 21 of the air supply unit 20 in the case where the cylinder 32 surrounds the guide vane 30 and when the cylinder 32 is omitted (at any position away from the front face 21 of the air supply unit 20 The maximum wind speed in the air-conditioned space 10) was compared, and the results are shown in Figure 9. In the same case, the difference between the minimum air temperature and the air supply temperature was non-dimensionally compared with the difference between the air supply and exhaust air temperatures with respect to the distance from the front surface 21 of the air supply unit 20 , and the results are shown in FIG. 10 . In addition, the lowest non-dimensional air temperature on the vertical axis in FIG. 10 is represented by the following equation.

Minimum dimensionless temperature T _F ^* = (T _F -T _S )/(T _E -T _S )

T _F : the lowest temperature under the feet, T _S : the blowing temperature, _TE : the suction temperature.

By surrounding the guide fins 30 with the cylindrical inner wall surface 33 as in the present invention, it can be confirmed that the air velocity of the low-temperature air SA blown from the air supply port 15 decreases rapidly, and the low-temperature air SA blown into the living area 11 temperature rises rapidly. On the other hand, in the case where there is no cylinder 32, since the periphery of the guide fin 30 is open, the air around the guide fin 30 (the air supply unit 20) as shown by the dashed line SA' in FIG. The low-temperature air in the air) flows in from around the air supply port 15. Under this influence, a sufficient swirl component will no longer be given to the low-temperature air SA blown out from the air supply port 15, and the low-temperature air SA blown out from the air supply port 15 will be The induced amount of air in the air-conditioned space 10 (induction ratio) decreases, so the airflow attenuation characteristics cannot be improved. In this regard, by enclosing the periphery of the guide vane 30 with the cylindrical inner wall surface 33 as in the invention, this inflow from the periphery can be prevented, and more rotation can be imparted to the low-temperature air SA blown from the air supply port 15. Element.

Further, the length of the cylindrical inner wall surface 33 (cylinder 32 ) surrounding the guide fin 30 was studied, as shown in FIGS. 11 and 12 . That is, on the circular air supply port 15 with diameter D=160 mm, according to the guide fins 30 with width 1=16 mm, it was investigated that the guide fins are surrounded by the inner wall surface 33 (cylinder 32 ) with a cylindrical inner diameter D=160 mm. The relationship between the length L of the inner wall surface 33 (cylinder 32 ) and the width 1 of the guide fin 30 in the case of the circumference of the guide fin 30 . The length L of the inner wall surface 33 (cylinder 32 ) was changed from half to three times the width 1 of the guide fin 30 , and the wind speed distribution at a position 200 mm from the front of the air supply unit 20 was compared. Furthermore, a comparison was also made with the case where the cylinder 32 was omitted (the length L of the inner wall surface 33 = 0). FIG. 11 shows the case where the flow rate of the low-temperature air SA blown out from the air outlet 15 is 90 m ³ /h, and FIG. 12 shows the case where the flow rate of the low-temperature air SA blown out from the air outlet 15 is 150 m ³ /h. In FIGS. 11 and 12 , the abscissa represents positions diametrically separated from the central axis of the air supply port 15 at a position 200 mm away from the front face 21 of the air supply unit 20, and the positions separated to one side (positive side) The respective average airflow velocities were measured and compared at the position away from the other side (negative side).

When the cylinder 32 is not attached, the wind speed near the center of the air inlet 15 is higher than that when the cylinder 32 is attached. In addition, in Fig. 11 and Fig. 12, the flow rate of low-temperature air SA was changed from 90m ³ /h to 150m ³ /h, and the measurement was carried out after changing the blown Reynolds number, and it was confirmed that the airflow velocity relative to the change of the cylinder 32 There is no large difference in distribution. Considering the practical situation, the width 1 of the guide fin 30 is about 13 mm, and the length L of the inner wall surface 33 (cylinder 32 ) is less than half of the width 1 , so the meaning of setting the inner wall surface 33 (cylinder 32 ) is not significant. It can be said that the length L of the inner wall surface 33 (cylinder 32 ) should be at least half of the width 1 of the guide fin 30 .

In this way, by surrounding the circumference of the guide fins 30 with the cylindrical inner wall surface 33, the low-temperature air SA blown into the living area 11 in the air-conditioned space 10 can be compared with the case where the cylinder 32 is not provided. More rotation components are given, so the induction amount (induction ratio) of the air in the air-conditioned space 10 induced by the blown low-temperature air flow can be further increased, and the speed of the low-temperature air SA blown into the air-conditioned space 10 can be quickly decelerated, Heat up quickly. Furthermore, the low-temperature air SA supplied into the air-conditioned space 10 flows downward in the air-conditioned space 10 due to the temperature difference, and fills the living area 11 below the air-conditioned space 10 at a low speed, thereby maintaining a comfortable environment for the living area 11. Down.

On the other hand, in the living area 11 in the air-conditioned space 10, for example, there are people who are heat generating bodies, so the low-temperature air SA supplied to the living area 11 and in thermal contact with the people 12 or other heat-generating devices is destroyed. Heat while rising slowly. Pollutants such as dust and gas generated around the people 12 in the living area 11 in the air-conditioned space 10 can be transported upward in the air-conditioned space 10 by the updraft.

Moreover, the air (heated air) staying in the upper part of the air-conditioned space 10 will not be disturbed, that is, the temperature layer of the living area 11 formed in the lower part of the air-conditioned space 10 will not be disturbed, and the air will be exhausted through the air outlet 16 and the air. The channel 41 discharges to the outside of the exhaust fan 40 . In this way, by supplying low-temperature air SA to the living area 11 below the air-conditioned space 10, and discharging pollutants such as dust and gas from the upper portion of the air-conditioned space 10 together with the heated air, ventilation in the air-conditioned space 10 is performed, and the air-conditioned space The living area 11 in the lower part of 10 is kept under the environment of clean low-temperature air SA.

According to such a ventilation system 1 , the people 12 in the living area 11 in the air-conditioned space 10 can hardly feel the air current. And, with respect to the low-temperature air SA blown out from the air supply port 15, the amount of induction of higher-temperature surrounding air (air in the air-conditioned space 10) increases, and the temperature difference between the low-temperature air SA and the surrounding air decreases rapidly, and can be further reduced. The upper and lower temperature differences in the living area 11 in the air-conditioned space 10 . In this way, the air in the air-conditioned space 10 can be efficiently air-conditioned with as small an air volume as possible, and it is possible to contribute to energy saving.

An example of a preferred embodiment of the present invention has been described above, but the present invention is not limited to the illustrated form. For example, in each air supply port 15, the cylindrical inner wall surface 33 surrounding the guide fin 30 may be comprised with the sound absorbing material. In this case, the cylinder 32 itself attached to each air supply port 15 may be made of a sound-absorbing material, or a sound-absorbing material may be arranged on the inner wall surface of the cylinder 32 .

FIG. 13 is a diagram comparing noises generated when the material of the cylinder 32 is changed. That is, comparing the case where the cylinder 32 is made of foamed polyurethane having a good sound-absorbing effect and a plywood, the relationship between the blowing wind speed of the low-temperature air SA and the noise generation is shown. It was confirmed that when the cylinder 32 is made of foam-molded polyurethane having a high sound-absorbing effect, the generated noise is suppressed.

As shown in FIG. 14 , a perforated plate 51 formed with a plurality of ventilation holes 50 may also be arranged parallel to the front surface 21 in front of the front surface 21 of the air supply unit 20, and a porous plate 51 is provided with a predetermined gap M in front of each air supply port 15. plate 51. In this way, since the low-temperature air SA jetted from each air supply port 15 is supplied into the air-conditioned space 10 through the air holes 50 formed in the perforated plate 51 , the airflow attenuation characteristic can be further improved.

The opening ratio of the porous plate 51 (the area of the ventilation holes 50 ) was examined for the case where the porous plate 51 was installed in front of the air inlet 15 in this way. Furthermore, the relationship between the opening diameter D of the air supply port 15 and the distance M from the air supply port 15 to the perforated plate 51 was also examined. In the air supply unit 20 with the air supply port 15 of the diameter D=188mm installed with the guide fins 30 respectively, the front 21 of the height 600mm×width 600mm is arranged on four places, and the isothermal air supply of 400m ^/ h is carried out, and the hole diameter is changed to The opening ratio of the perforated plate 51 with the ventilation holes 50 of 6 mm was compared with the maximum wind speed of the low-temperature air SA. The distance M between the perforated plate 51 and the gas supply port 15 is 25 mm. On the position of the distance X=100mm, 400mm, 700mm, 1000mm apart from the surface of the perforated plate 51, the relationship between the aperture ratio (the area of the ventilation hole 50) of the perforated plate 51 and the maximum wind speed of the low-temperature air SA was investigated respectively, as shown in Figure 15 as shown. In addition, the maximum wind speed V _MAX is dimensionless with the average blowing speed V ₀ at the position of the air supply port 15. If the opening ratio of the perforated plate 51 is more than 40%, the effect of the present invention will not be impaired, especially at X=1m It is confirmed that the maximum wind speed V _MAX can be minimized when the opening ratio of the perforated plate 51 is about 60%.

For the same situation, make the aperture ratio of perforated plate 51 58% (opening diameter is 6mm), change the interval distance M from air supply port 15 to perforated plate 51, distance X=100mm, 400mm apart from the surface of perforated plate 51 , 700mm, and 1000mm, the relationship between the distance M from the air supply port 15 to the perforated plate 51 and the maximum wind speed of the low-temperature air SA was investigated, as shown in FIG. 16 . In addition, in FIG. 16 , the horizontal axis represents the ratio (M/D) of the distance M from the air supply port 15 to the perforated plate 51 to the opening diameter D of the air supply port 15 . When the distance M from the air supply port 15 to the perforated plate 51 is 7% or more of the opening diameter D of the air supply port 15, it can be confirmed that the maximum wind speed is at a position of distance X=1000 mm from the surface of the perforated plate 51. The difference decreases.

In FIG. 3 and the like, the ions surrounding the guide vane 30 through the inner wall surface 33 of the cylinder 32 attached to each air supply port 15 have been described, but as long as the inner wall surface surrounding the guide vane 30 is provided 33, not necessarily the cylinder 32. That is, as shown in FIG. 17 , the front surface 21 of the air supply unit 20 has a sufficient thickness, and when the circular air supply port 15 is formed, the length L of the cylindrical inner wall surface 33 is equal to the width of the guide fin 30 . In the case of half or more of 1, the cylinder 32 can be omitted. For example, if the front surface 21 of the air supply unit 20 is made of glass fiber or the like having an excellent sound-absorbing effect with a sufficient thickness, not only the cylinder 32 can be omitted, but also noise generation as described in FIG. 13 can be suppressed.

In FIGS. 4 and 5 , a mechanism in which a plurality of guide fins 30 are radially attached to the support member 31 has been described, but the structure of the blowing member attached to each air outlet 15 is not limited to this. For example, a structure such as a swirl flow forming plate disclosed in Japanese Patent Application Laid-Open No. Hei 9-250803 previously filed by the present applicant may be used. That is, as shown in FIG. 18, a circular support member 31 is left at the center of the circular flat plate 55, and the periphery of the support member 31 is punched into fan-shaped guide fins 30. By bending and inclining each guide fin 30, Formed easily at a predetermined angle. In any case, any guide vane 30 capable of imparting a rotational component may be formed.

In the mode shown in FIG. 8 , it was set so that between the air supply ports 15 arranged up and down, the rotational components of the low-temperature air SA blown out from the adjacent air supply ports 15 are in opposite rotational directions. Between the laterally arranged air outlets 15 , the rotational components of the low-temperature air SA blown from adjacent air outlets 15 have the same rotational direction, but the inclination of the guide fins 30 provided on each air outlet 15 The direction does not have to be set this way. For example, although not shown in the figure, it may also be arranged so that the rotation components of the low-temperature air SA blown out from the adjacent air outlets 15 are in a relationship of opposite rotation directions between the air outlets 15 arranged in the horizontal direction, and arranged vertically. Between the air supply ports 15 of each, the rotational components of the low-temperature air SA blown out from the adjacent air supply ports 15 have the same rotational direction relationship. Moreover, it is also possible to set the inclination direction of the guide vane 30 provided on each air supply port 15 so that between any one of the air supply ports 15 arranged up, down, left, and right, the temperature of the low-temperature air SA blown out from the adjacent air supply ports 15 The rotation components all have a relationship of rotation directions opposite to each other. In addition, it is also possible to set such that the rotation components of the low-temperature air SA blown out from all the air outlets 15 have the same rotation direction. Furthermore, it is also possible to set so that the rotational components of the low-temperature air SA blown out from the respective air outlets 15 are irregularly in the same rotational direction or in opposite rotational directions. The rotational direction of the rotational component of the low-temperature air SA blown out from each air outlet 15 can be set arbitrarily.

Moreover, the circular air supply port 15 can be directly opened on the air supply channel 23, and the low-temperature air SA is blown out from the air supply port 15 into the air-conditioned space 10, and a plurality of guide vanes for imparting a rotational component to the low-temperature air SA are installed here. sheet 30 and cylinder 32. In this way, the air supply unit 20 can be omitted. In addition, it is also possible to install guide fins, cylinders, or perforated plates on the air supply unit constructed on the building to ventilate and supply air into the air supply unit. Air supply units are available with walls or double floors.

The connection of the air supply unit to the channel can take place both from above or from the side of the air supply unit, as well as from below. Moreover, it is also possible to ventilate and supply air into the double-layer floor, and supply air to the air supply unit. In this case, the air supply channel to the air supply unit can be omitted. In addition, the air supply unit can also be arranged around the pillar.

For example, it may be a structure in which a part of the exhaust gas EA is returned to the air conditioner 22 for reuse by setting the return passage 45 shown by the dotted line in FIG. The low-temperature air SA below pushes out the heated air staying in the upper part of the air-conditioned space 10 sequentially. Furthermore, the exhaust port 16 may also be formed on the ceiling of the air-conditioned space 10 . In addition, the ventilation system of the present invention is not limited to the living room, but can also be applied to various air-conditioned spaces where people or various instruments exist as mentioned above.

In addition, the ventilation system of the present invention may be configured to supply low-temperature air into an air-conditioned space, but such a ventilation system may also be used in a heating air conditioner for supplying high-temperature air into an air-conditioned space to generate heat.

In addition, in the ventilation system of the present invention, when high-temperature air is supplied from the air supply port into the air-conditioned space, the air in the air-conditioned space is induced to move together by the supplied high-temperature air. In this way, when high-temperature air is supplied from the air-supply port to the living area formed below in the air-conditioned space, a swirling component is added to the high-temperature air supplied by the guide mechanism, thereby increasing the induced amount of air in the air-conditioned space induced by the amount of high-temperature air. (induction ratio). Moreover, as the amount of induction increases, according to the law of conservation of motion, the velocity of high-temperature air decelerates rapidly after it is fed into the air-conditioned space. Therefore, the uncomfortable feeling of air flow accompanying the supply of high-temperature air to the living area hardly occurs.

Furthermore, as the induction amount increases, the low-temperature air in the living area formed below in the air-conditioned space can be mixed with the supplied high-temperature air to rapidly raise the temperature. Therefore, the air (air) heated by mixing the low-temperature air in the living area and the high-temperature air supplied into the air-conditioned space from the air-supply port quickly rises in the air-conditioned space after being supplied by heating, and reaches the vicinity of the ceiling. In this way, pollutants etc. generated in the living area can be effectively diluted and moved to the vicinity of the ceiling.

And, the air that goes up to the vicinity of the ceiling is cooled by the wall surface that becomes low temperature after being cooled by the outside air due to thermal contact with the wall surface of the air-conditioned space, and then descends to the living area again. After that, it mixes with the high-temperature air supplied from the air supply port to raise the temperature again and rise to the vicinity of the ceiling. In this way, the air in the living area and the air near the ceiling in the air-conditioned space are circulated, and the air in the living area is sequentially replaced by fresh air descending from the vicinity of the ceiling, thereby heating the living area without discomfort caused by drafts.

On the other hand, the air in the air-conditioned space is exhausted from the exhaust port while circulating the air in the living area in the air-conditioned space and the air near the ceiling, and the indoor air is sequentially replaced with fresh high-temperature air supplied from the air supply port. In this way, pollutants and the like generated in residential areas and the like can be removed, and deterioration of indoor air can be avoided. The ventilation system of the present invention can also be well applied to a heating air conditioner that heats a living area in an air-conditioned space by means of ventilation.

Example

As shown in Fig. 19, the air supply unit is arranged on a floor of 15m x 16m in plan view, and a partition (non-air-conditioned space) of 7.1m x 7.2m is formed on a part of the interior. The floor area is 190m ² and the ceiling height is 10m. In the air-conditioned space (mechanical working room) 10 of the company, nozzles with a diameter of 500 mm that blow out the air horizontally were installed at a height of 4 m, and the air conditioning by these air supply units and nozzles was performed. The air supply unit of the embodiment of the present invention was compared with the air supply unit of the conventional comparative example 1. The air supply unit of the present invention has an air supply port formed on the front of the width of 0.6m and a height of 2.1m, and is installed on each air supply port. In the air supply unit with a plurality of guide vanes that impart a rotational component to the low-temperature air SA, the circumference of the guide vanes is surrounded by a cylinder, and the air supply unit of Comparative Example 1 has a width of 1 m and a height of 2.1 m. Air inlets are formed, and only a plurality of guide fins for imparting a swirling component to the low-temperature air SA are attached to each air outlet. Moreover, the case where the low-temperature air SA was horizontally supplied from the nozzle installed in the position of height 4m was made into comparative example 2. As shown in FIG.

In the air-conditioned space 10 , as shown in FIG. 19 , machine tools H1 to H8 are arranged, and heat loads generated in the air-conditioned space 10 are generated by the machine tools H1 to H8 and mercury lamps arranged on the ceiling. The heat load generated by these operating machines H1 to H8 and the mercury lamp corresponds to approximately 80 W/m ² . At each of the points A to F shown in FIG. 19 , the temperature, wind speed distribution, and spatial distribution of pollutants were measured and compared. Point A is near the front of the air supply unit, point B is a position closer to the front of the air supply unit than point A, and point C is a position further away from point B in front of the air supply unit. Point D indicates a location not in front of the plenum unit, but around the partition. Both the points E and F are the surfaces of the inner side walls of the air-conditioned space 10 . Also, tracer gas is supplied as a pollutant at the site B and the position of the work machine H3.

FIG. 20 (Table 1) shows the operating state of the air conditioner when comparing the embodiment of the present invention with Comparative Example 1 and Comparative Example 2. FIG. Exhaust is performed from a pressurized fan installed on the ceiling, and the exhaust air volume is adjusted to be the same as the air supply air volume. The comparison was performed under the same conditions where the air volume of the air conditioner was adjusted to 4000m ³ /h, the supply air temperature was 18°C, and the outside air temperature was 30°C. The tracer gas for simulating pollutants uses a mixed gas of SF ₆ and He whose density is adjusted to be the same as that of air, and flows from directly above the heating machine (H3) or a non-heating place (on the floor at point B) at a certain flow rate. 1m) Release, the actual measurement of the steric concentration in the case of each of the examples of the present invention and comparative examples 1 and 2 was performed.

FIG. 21 shows the upper and lower temperature distributions of a point D surrounded by heat-generating working machines H2 to H6 at a long distance from the air supply port. Compared with the case of operating the nozzle (comparative example 2) as a hybrid system, in the examples of the present invention and comparative example 1, it can be confirmed that the air temperature in the residential area is low, and the air temperature in the ceiling part of the non-residential area is high. . Compared with Comparative Example 1, the upper and lower temperature differences in the living area of the Example of the present invention are smaller, and a more comfortable state can be maintained.

22 to 25 show the wind velocity distributions at the respective points A to D, respectively. In Comparative Example 1, although the operation was performed at a slower blowing wind speed (0.3 m/s) than the Example of the present invention, it was confirmed that the wind speeds at the feet of the points A to C were faster than the Examples of the present invention. Moreover, at the point D away from the air supply unit, the wind speed in the residential area of the embodiment of the present invention is faster than that of the comparative example 1 as a whole. Since the example of the present invention has a larger blowing induction amount than Comparative Example 1, it can be said that the amount of blowing air expected to reach a remote place is large.

Figure 26 is a graph comparing PMV and SET ^* for 1 m above the floor at site D. The comparison was performed so that the amount of metabolism was 1.2 met and the amount of clothing was 0.6 clo. In the three ways, it was judged that the embodiment of the present invention can improve the thermal comfort at the farthest point.

FIGS. 27 to 29 show the concentration distributions at the respective points A, C, and D when the tracer gas is released from the heat-generating device H3 in a non-dimensional manner using the concentration at the exhaust port. The concentration at 1 m above the floor of the residential area was the lowest in Comparative Example 1, but it was confirmed that the concentration of the residential area in the example of the present invention was about half of that in the case of the nozzle.

FIGS. 30 to 32 non-dimensionally show the concentration distributions at the points A, C, and D when the tracer gas is released from 1 m above the floor of the point B where there is no heat generation, using the concentration at the exhaust port. It is judged that the average concentration of the living area 1m on the floor is the lowest in the embodiment of the present invention. The indoor air of Comparative Example 1 is activated only at the foot of the air supply flow and the place where the thermal updraft due to heat generation occurs. Therefore, in the case where pollutants are generated in a place where no buoyancy is generated, the pollutants are not diluted to generate a high-concentration portion in the residential area. Embodiments of the present invention that induce the air in the living area by swirling flow effectively dilute the pollutants due to the air movement within the living area.

Fig. 33 is a diagram showing actual measurement and comparison of the upper and lower temperature distributions at point D when the heating operation is performed with the supply air temperature at 30°C and the air-conditioning air volume at 4000m ³ /h when the outside air temperature is 10°C. When heating is performed, the blown air rises to the ceiling part due to buoyancy, and is cooled by the wall surface to descend. In the embodiment of the present invention, since the air in the living area is induced by the swirling flow, mixing of the ceiling air and the air in the living area is promoted during heating. Therefore, compared with the case of comparative example 1 and comparative example 2, the upper and lower temperature differences in the residential area are large. The temperature at the foot of 0.1m increased by about 2°C, and the temperature difference between the upper and lower areas in the living area decreased. In addition, the temperature of the living area 1 m above the floor was about 1° C. higher than that of Comparative Example 1 and Comparative Example 2 in the embodiment of the present invention. Comparing the three, it can be confirmed that the embodiment of the present invention can generate heat most effectively.

Claims (7)

1. A ventilation and ventilation system for ventilation by supplying low-temperature air into an air-conditioned space and exhausting the heated air that has been heated and raised in the air-conditioned space, and is characterized in that, A plurality of guide vanes that give rotation components to the low-temperature air blown into the air-conditioned space are installed on the air supply port of the low-temperature air. These guide vanes are radially arranged around the central axis of the air supply port. The guide fins are arranged obliquely at the same angle with respect to a plane perpendicular to the central axis of the air inlet, A cylindrical inner wall surface with the central axis of the air inlet as the central axis is formed around these plurality of guide fins, The length of the inner wall surface along the central axis direction of the air supply port is at least half of the width of the guide fin along the central axis direction of the air supply port. 2. The ventilation system according to claim 1, wherein the inner wall surface is made of sound-absorbing material. 3. The ventilation system as claimed in claim 1, characterized in that, A plurality of the air inlets are arranged in a row, and a plurality of guide vanes that impart a rotational component to the low-temperature air are attached to each air outlet, and a circle surrounding these plurality of guide fins is formed on each air outlet. cylindrical inner wall, On adjacent air inlets, the inclination directions of the guide vanes are opposite. 4. A ventilation and ventilation system for ventilation by supplying low-temperature air into an air-conditioned space and exhausting the heated air that has been heated and risen in the air-conditioned space, and is characterized in that, A plurality of guide vanes that give rotation components to the low-temperature air blown into the air-conditioned space are installed on the air supply port of the low-temperature air. These guide vanes are radially arranged around the central axis of the air supply port. The guide fins are arranged obliquely at the same angle with respect to a plane perpendicular to the central axis of the air inlet, A cylindrical inner wall surface with the central axis of the air inlet as the central axis is formed around these plurality of guide fins, A perforated plate having an opening ratio of 40% or more is provided in front of the air inlet. 5. The ventilation system according to claim 4, wherein the inner wall surface is made of sound-absorbing material. 6. ventilation system as claimed in claim 4, is characterized in that, A plurality of the air inlets are arranged in a row, and a plurality of guide vanes that impart a rotational component to the low-temperature air are attached to each air outlet, and a circle surrounding these plurality of guide fins is formed on each air outlet. cylindrical inner wall, On adjacent air inlets, the inclination directions of the guide vanes are opposite. 7. The ventilation system according to claim 4, wherein the relationship between the opening diameter D of the air supply port and the distance M from the air supply port to the perforated plate is M/D≥0.07.

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