JPH0687325A - Control device for fluid flow blowout - Google Patents

Abstract

PURPOSE:To provide a control device for fluid flow blowout capable of realizing a collective blowoff to a necessary area, and consequently contributing to a reduction in power consumption. CONSTITUTION:A control device for fluid flow blowout is provided with a deflector plate 10 formed larger than an outlet part 1, separated from the outlet part 1, and arranged to interrupt the flow in the lower stream of the outlet part 1; a ceiling wall part 21 provided continuously to the circumferential outside from near the outlet part 1; and a guide member 20 having a cylindrical wall part 21 cylindrically formed toward the lower stream continuously to the ceiling wall part 21 and having a bore larger than the deflector plate 10, so that the flow blown from the outlet part 1 is guided by the deflector plate 10 and the guide member 10, and blown in rings. The speed of the blown ring air flow is fast on the outside and slow on the inside, and the air flow is rolled inside by entrainment effect. Thus, the expansion angle of the air flow is minimized, compared with free blown air flow.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid flow blow-out control device which is provided in the vicinity of an outlet where a fluid flows out and controls the fluid blown out from the outlet. It is effective when used for the blowout part of the air conditioner.

[0002]

2. Description of the Related Art Conventionally, for example, in an air conditioner for an automobile,
Air-conditioned air can be discharged toward the passenger compartment from the air outlet formed in the dash panel in the front of the passenger compartment.
As disclosed in Japanese Patent No. 463, there is known a vehicle seat in which a plurality of air-conditioning air outlets are formed so that the air-conditioned air is blown out from the surface of the vehicle seat.

[0003]

However, in the above-mentioned conventional example, the air outlets formed in the dash panel or the seat are simply configured as the openings of the nozzles, those formed in a lattice shape, or the wind direction. I just placed a louver etc. to change the. Therefore, from the outlet, the conditioned air is blown out into the entire passenger compartment as a so-called free-flowing air current and is convected, so that more power than is needed to give the seated passenger a comfortable feeling is consumed. This is enough to give a comfortable feeling to the occupants if only the seated occupants who are actually sitting can be air-conditioned, but in reality, the blown airflow is too wide, so the minimum required power is required. The above power is consumed.

[0004] Therefore, an object of the present invention is to provide a fluid flow blowout control device which realizes intensive blowout to a necessary area and eventually contributes to reduction of power consumption.

[0005]

In order to solve the above-mentioned problems, the fluid flow blow-out control device of the present invention according to claim 1 is provided in the vicinity of the outlet portion from which the fluid flows, and is surrounded by the outlet portion. A device for controlling a fluid blown out toward a space, the deflector plate being formed to be larger than the outlet portion, separated from the outlet portion, and arranged to block the flow downstream of the outlet portion, and the outlet portion. A guide having a ceiling wall portion that is continuously provided outward in the circumferential direction from the vicinity, and a tubular wall portion that is continuously provided to the ceiling wall portion and is formed in a tubular shape toward the downstream side and has an inner diameter larger than that of the deflector plate. And a member, the flow blown out from the outlet is guided to the deflector plate and the guide member and blown out in an annular shape.

According to this fluid flow blowout control device, the airflow blown out from the outlet collides with the deflector plate disposed downstream thereof and flows in the circumferential direction, and the ceiling wall portion and the tubular wall portion of the guide member are provided. And is blown in an annular shape from between the deflector plate and the tubular wall portion.

Since the annular airflow blown out along the cylindrical wall surface becomes a so-called wall surface jet flow by flowing out along the solid wall, the velocity near the wall surface is increased. Therefore, the annular airflow has a high velocity on the outside and a low velocity on the inside.
Further, in the vicinity of the downstream side of the deflector plate, there is a negative pressure region surrounded by the blown out annular air flow, so that the air flow is entrained inward by the so-called entrainment effect. Therefore, the development angle of the airflow is smaller than that of the free-blowing airflow.

As described above, the annular airflow blown out between the deflector plate and the tubular wall portion has a high speed on the outer side and a slow speed on the inner side, and the spread angle of the airflow is small, so that the reachability to the downstream side is low. Well, an air curtain-like area is formed. Therefore, for example, if it is used in the blowout part of an air conditioner for a seat, the cool air blown out during cooling will spread like an air curtain only around the occupant, and will also have the effect of blocking the cool air inside the air curtain from the warm air outside. Therefore, the temperature rise of the conditioned air also decreases.

A fluid flow blowout control device according to a second aspect of the present invention is a device which is provided in the vicinity of an outlet portion from which a fluid flows out and which controls the fluid blown out from the outlet portion, and is formed larger than the outlet portion. Moreover, it is separated from the outlet part and is arranged downstream of the outlet part so as to block the flow, and is formed in a cylindrical shape continuous to the ceiling wall part toward the outlet side and is larger than the outlet part. A guide member having a cylindrical wall portion having an inner diameter is provided, and the flow blown out from the outlet portion is guided to the guide member and blown out in an annular shape.

According to the fluid flow blowing control device of the present invention, the air flow blown from the outlet collides with the ceiling wall portion of the guide member disposed downstream thereof and flows in the circumferential direction, and the ceiling wall portion and the continuous arrangement are provided. It is guided along the cylindrical wall portion and is blown out in an annular shape. Similar to the device of claim 1, the annular airflow blown out along the cylindrical wall surface is a so-called wall surface jet, so that the velocity in the vicinity of the wall surface becomes high. Therefore, the annular airflow has a high velocity on the outside and a low velocity on the inside. In addition, since there is a negative pressure area surrounded by the blown out annular airflow, the airflow is caught inside due to the entrainment effect, and the development angle of the airflow becomes smaller than that of the free-flowing airflow, and reaches the downstream. Good sex.

Therefore, similarly to the device according to the first aspect, an air curtain-like region is formed, the effect of blocking the internal cool air and the external warm air is exerted, and the temperature rise of the conditioned air is reduced.

[0012]

Embodiments of the fluid flow blowing control device of the present invention will be described below. In the present embodiment, the blowout control device is applied to the blowout part of the automobile air conditioner. First, the overall configuration of the air conditioner will be briefly described. FIG. 2 is a cross-sectional view schematically showing the front of the passenger compartment of the automobile, in which the ceiling 106,
A seat including a seat 50, a backrest 52, and a headrest 58 is fixed to a floor 114 of the vehicle in a vehicle interior space 126 surrounded by the windshield 108 and the like.

The first duct 62 has a seat 50 and a floor 114.
The blower fan 7 located in the space between the blower fan 7 and the first duct 62 is driven by the electric motor 76 at the center of the left and right sides.
4 are arranged. The rotation of the blower fan 74 generates an air suction force from the suction port 60.

The second duct 6 connected to the first duct 62
6 is fixed along the center pillar 150 and extends upward. A third duct 70 is connected to the second duct 66, and the third duct 70 has a ceiling 106.
Is disposed inside a heat insulating material 148 disposed between the seat and the lining plate 107, bends in an approximately L shape above the head of the seated person when seated on the seat, and is substantially orthogonal to the ceiling 106. It extends downward. The opening portion at the tip serves as the outlet portion 1 and blows air downward.

These first to third ducts 62, 66, 70
Is made of a resin material, and the first to third ducts 62, 6
Reference numerals 6 and 70 have a honeycomb structure in which a plurality of spaces are formed in the duct wall so as to extend in the longitudinal direction of the duct. Due to this space, the heat mass of the duct itself is reduced, and the cooling time during maximum cooling can be shortened.

Further, the space portion also has a heat insulating function, and particularly in the second duct 66 arranged in the backrest portion 52, the heat given to the seat itself by the solar radiation or the heat from the occupant is shut off. Great effect. First duct 6
A blower fan 74 driven by a fan motor 76 is arranged in the inside 2, and a conventionally known refrigerant evaporator 78 is arranged in the downstream of the blower fan 74.
By this evaporator 78, the heat of the air sucked from the suction port 60 is taken and cooled. Since the evaporator 78 is a part of a conventionally known refrigeration cycle, the evaporator 78 is
The description of the configuration of the refrigeration cycle and the like will be omitted.

In FIG. 2, reference numeral 110 is an automobile hood, and 112 is a steering wheel. Next, the third duct 7
The blow-out control device provided in the outlet portion 1 at the 0 tip will be described. FIG. 1A is a cross-sectional view of the blowout control device of the first embodiment, and FIG. 1B is a bottom view of the same. The blowout control device of this embodiment includes a deflector plate 10 and a guide member 20.

The deflector plate 10 is formed in a shallow dish shape having a diameter larger than the circular opening of the outlet portion 1, is separated from the outlet portion 1, and is arranged so as to block the flow downstream of the outlet portion 1. ing. The deflector plate 10 is fixed to the third duct by the deflector column 13.

Further, the guide member 20 is provided continuously to the outside in the circumferential direction from the vicinity of the outlet portion 1, and the ceiling wall portion 21 having a circular outer periphery, and the outer periphery of the ceiling wall portion 21 are provided continuously to the downstream side. It has a tubular wall portion 23 formed in a tubular shape toward the side. The tubular wall portion 23 has an inner diameter larger than that of the deflector plate 10, and an annular gap is formed between the deflector plate 10 and the tubular wall portion 23, and becomes the final blowout port 30. .

Next, the operation of the first embodiment will be described. When the seat occupant turns on a fan switch and an air conditioner switch (not shown), the blower fan 74 rotates. Then, the air in the vehicle interior space 126 is sucked through the suction port 60 by the suction force of the blower fan 74, and the evaporator 7
It is cooled by exchanging heat with No. 8. The operation of the evaporator 78 is a conventionally known operation. The cooled air is in the second duct 6
6, the air is blown from the outlet 1 through the third duct 70.

The air flow blown out from the outlet portion 1 collides with the deflector plate 10 disposed downstream of the outlet portion 1 and changes its direction in the circumferential direction to flow along the ceiling wall portion 21 of the guide member 20 and further to the cylinder. The air outlet 3 between the deflector plate 10 and the tubular wall portion 23 is guided along the wall portion 23.
It is blown out in a ring shape from 0. The blown air flows down from the head of the seated occupant toward the feet, and is sucked into the suction port 60 again. This flow of air is shown by a broken line in FIG.

The annular airflow blown out along the cylindrical wall portion 23 becomes a so-called wall surface jet flow by flowing out along the solid wall, so that the velocity near the wall surface becomes high. Therefore, the blown out annular airflow has a high velocity outside and a slow velocity inside. Further, in the vicinity of the downstream side of the deflector plate 10, there is a negative pressure region surrounded by the blown out annular air flow, so that the air flow is entrained inside due to the so-called entrainment effect. Therefore, the development angle of the air flow becomes smaller than that of the free air flow.

As described above, the annular airflow blown out between the deflector plate 10 and the cylindrical wall portion 23 (hereinafter referred to as a guide annular flow including the meaning of being guided along the guide member 20). Is faster on the outside and slower on the inside,
Further, since the development angle of the air flow is small, the reachability to the downstream is good, and an air curtain-like region is formed. Therefore, the blown out cool air spreads like an air curtain only around the seated occupant, and exerts an effect of blocking cool air inside the air curtain and warm air outside the air curtain, so that the temperature rise of the conditioned air is reduced.

The formation state of the guide annular flow is influenced by the shapes of the deflector plate 10 and the guide member 20, and the result of studying the degree of the influence will be described. Experimental conditions are: outside air temperature 35 ° C, relative humidity 60%, solar radiation 500
Kcal / square m · h, the temperature of the air blown from the outlet 1 is 15 ° C., and the air velocity is 3 m / s. Further, elements that change the shapes of the deflector plate 10 and the guide member 20 are schematically shown in FIG.

The angle between the axial direction of the outlet portion 1 and the ceiling wall portion 21 of the guide member 20 is the first guide angle α, the length of the tubular wall portion 23 is the guide plate length L, and the axial direction of the outlet portion 1 is Is the second guide angle β, the diameter of the deflector plate 10 is the deflector length d, the distance from the end of the outlet 1 to the deflector plate 10 is the deflector position δ, and the axial direction of the outlet 1. The angle of the deflector plate 10 with respect to the orthogonal direction is defined as a deflector angle γ. In the case of this experiment, the inner diameter of the outlet portion 1 was set to 60 mm, and the inner diameter of the tubular wall portion 23 was fixed to 300 mm.

The experimental results and the examination results when the above-mentioned elements are changed will be described below. First, the guide plate length L will be described. If the guide plate length L is short, the annular guide flow largely extends outside the tubular wall portion 23 to the outside as in the case of L = 15 mm shown in FIG. Therefore, the guide annular flow zone spreads downstream, and the wind speed becomes slow.

On the other hand, in the case of L = 40 mm shown in FIG. 4 (B), the entrainment effect is strong, the guide annular flow is caught inward and the expansion angle becomes small, and the outer speed is high and the inner speed is high. It can be seen that since the air flow is slow, the reachability to the downstream is good and the air curtain-like region is well formed.

Next, the first guide angle α will be described. FIG. 4C shows the case of α = 90 degrees, and FIG. 4D shows the case of α = 75 degrees. When α = 75 degrees, the vortex is formed deeper in the air outlet, so that the entrainment effect is stronger and the spread of the airflow zone in the alternating current region is smaller.

For the deflector length d, see FIG.
When d = 200 mm, in FIG. 4 (F) d = 160 mm
The case of each is shown. As the deflector length d increases, the entrainment of the airflow in the area indicated by the arrow A in FIG. 3B decreases, and the vortex becomes smaller. As a result, the airflow zone downstream of the outlet 30 is expanded. Therefore, the air flow zone can be changed by the deflector length d.

The deflector position δ is shown in FIG.
Shows the case where δ = 20 mm, and FIG. 4 (H) shows the case where δ = 10 mm. The smaller the value of the deflector position δ, the higher the wind speed of the guide plate 20, especially in the portion of the flow along the cylindrical wall portion 23. That is, the tendency that the wind velocity in the portion near the outer side of the guide annular flow is high and the inner side becomes small becomes stronger.

Regarding the deflector angle γ, FIG. 4 (I) shows the case of γ = 0 degrees, and FIG. 4 (J) shows the case of γ = 40 degrees. From a relative perspective, it can be seen that the entrainment effect is slightly stronger when γ = 40 degrees.
As shown by the chain double-dashed line in FIG. 3 (B), the distances a1 to a3 between the deflector plate 10 and the ceiling wall portion 21 are the outlet portions 1
It may be made smaller as it goes away from the center line CL. In that case, the distances r1 to r3 from the center line CL
Make the aperture areas at the points equal or smaller (2π
・ R1 ・ a1 ≧ 2π ・ r2 ・ a2 ≧ 2π ・ r3 ・ a3)
It should be set to.

In FIG. 3 (B), the regions indicated by arrows a and c have regions where the flow stagnates. Therefore, it is conceivable to round these regions to make the flow smoother. . The rounded one is shown in FIG.
FIG. 5A shows an example in which the third duct 70 is not stored in the outlet 30, and FIG. 5B shows an example in which the third duct 70 is stored in the outlet 30. The center portion of the deflector plate 10 is formed in a substantially conical shape so that the degree of spread increases toward the hem so that the flow smoothly flows in the circumferential direction. Further, in the deflector plate 10 shown in FIG. 5, only the portion facing the outlet portion 1 is made horizontal, and the portion further than that is angled.

Next, an A type schematically shown in FIG. 6A, that is, a guide plate length L = 50 mm and a deflector length d = 100 mm, and a B type shown in FIG. 6B, that is, a guide The plate length L = 40 mm, the deflector length d = 160 mm, and the deflector plate 10 and the portion transitioning from the ceiling wall portion 21 to the tubular wall portion 23 are each formed with a radius of curvature of 20 mm. The result of detecting the temperature at a predetermined point in the vehicle compartment is shown in FIG.

The temperature inside the vehicle compartment is detected by disposing a thermocouple on the detection line DL shown in FIG. The detection line DL reaches the windshield 108 from the chin of the seated occupant P through the handle 112 and detects the temperature at a predetermined position therebetween.

In FIG. 6C, the horizontal axis represents the position of each detection point on the detection line DL, and the vertical axis represents the temperature at each detection point. The black circles are the A type and the white circles are the B type. Represent In the area indicated by the arrow F in the figure, the B type has a steeper temperature gradient than the A type. For example, at a certain detection point, the A type rises by 4 ° C, whereas at the same point, the B type rises by 7 ° C. It is considered that this is because the B type has a smaller guide annular flow spread and is superior in the ability to block the cold and warm air.

As described above, the cool air blown downward from the air outlet 30 can intensively air-condition only the periphery of the seated occupant P, and the guide annular flow has a wind speed at its outer portion. Since it is large, it also acts as an air curtain, which has an effect of blocking cold air from warm air outside. Therefore, it leads to power saving.

Next, another embodiment will be described. As described above, the airflow region can be changed by changing the first guide angle α, the guide plate length L, the second guide angle β, the deflector length d, the deflector position δ, and the deflector angle γ. Hereinafter, embodiments having a mechanism for changing the air flow region will be sequentially described. The same parts as those in the first embodiment are designated by the same reference numerals and detailed description thereof will be omitted.

First, an embodiment in which the guide plate length L is variable will be described. In the second embodiment shown in FIG. 7, a cylindrical auxiliary guide member 120 is slidably fitted to the outside of the cylindrical wall portion, and the screw gear 121 attached to the auxiliary guide member 120 is Drive side screw gear 12
3 is meshed. The rotation of the drive motor 125 is transmitted to the screw gear 121 by the gear 127, the worm gear 129, and the drive side screw gear 123, so that the auxiliary guide member 120 can be moved in the arrow direction of FIG. 7 (A). Has been done.

In the third embodiment shown in FIG. 8, the guide plate length L is manually variable. A screw portion 23a is formed on the outer periphery of the cylindrical wall portion 23, and the auxiliary guide member 120 is screwed into the screw portion 23a. A handle 120a is provided on the outer periphery of the auxiliary guide member 120, and the handle 120a is pinched and rotated in the arrow direction of FIG. 8B to move the auxiliary guide member 120 in the arrow direction of FIG. 8A. Can be moved to.

Next, an embodiment in which the deflector position δ is variable will be described. In the fourth embodiment shown in FIG. 9, the deflector plate 10 is supported by the shaft 130 without using the deflector column 13 in the first embodiment, and the shaft 131 thereof is provided.
The driving-side screw gear 133 is meshed with the screw gear 131 attached to the other end of the. Then, the rotation of the drive motor 135 is controlled by the drive side screw gear 1.
The deflector plate 10 can be moved in the direction of the arrow in FIG. 9A by transmitting to the screw gear 131 by 33.

In the fifth embodiment shown in FIG. 10, the deflector position δ is manually made variable. A screw portion 1 a is formed on the inner circumference of the outlet portion 1 of the third duct 70, and a deflector support member 140 attached to the deflector plate 10 is screwed into the screw portion 1 a. This deflector support member 140 is shown in FIG.
This will be described in more detail with reference to 0 (B).

The deflector support member 140 has a substantially cylindrical shape,
A threaded portion 140a is formed on the outer periphery thereof. Also,
A plurality of through holes 140b are formed at predetermined intervals in the circumferential direction to communicate the inside and outside of the deflector support member 140. A handle 10a is provided on the lower surface of the deflector plate 10, and the deflector support member 140 and the deflector plate 1 are gripped by rotating the handle 10a and the like.
0 can be moved in the arrow direction of FIG.

Next, an embodiment in which the deflector length d is variable will be described. In the sixth embodiment shown in FIG. 11, four auxiliary deflector plates 151 are provided on the edge of the deflector plate 10 as shown in FIG.
It is attached so as to be rotatable in the direction of the arrow 1 (A).
Each of these four auxiliary deflector plates 151 is hung by a wire 153 (only two are shown in FIG. 11A), and the wire 153 is rotated by rotating the corresponding wire winding 157 by the drive motor 155. Can be rolled up or unrolled.

Therefore, when the wire 153 is paid out, the auxiliary deflector plate 151 moves downward as shown by the chain double-dashed line in the figure, and the deflector length d becomes smaller. If the wire 153 is wound up from that state, the auxiliary deflector plate 15
1 moves upward and returns to the position indicated by the solid line in the figure, and the deflector length d increases.

In the seventh embodiment shown in FIG. 12, the shaft 160 is fixed to the deflector plate 10, and the screw gear 161 attached to the other end of the shaft 160.
A drive-side screw gear 163 is meshed with this. Then, by transmitting the rotation of the drive motor 164 to the screw gear 161 by the drive side screw gear 163, the deflector plate 10 can be moved in the arrow direction of FIG. Further, as shown in FIG. 12 (B), the deflector plate 10 of the present embodiment has a rubber film 167 provided between frames of a plurality of metal shafts 165, and has a structure similar to a general umbrella. Is.

Therefore, if the shaft 160 is lowered,
The metal shaft 165 and the rubber film 167 are recessed inward, and as a result, the deflector length d is reduced. vice versa,
When the shaft 160 is raised, the deflector plate 10 is expanded and the deflector length d is increased. In the case of the seventh embodiment, the deflector angle γ also changes at the same time.

In the eighth embodiment shown in FIG. 13, the deflector length d is manually variable. The deflector plate 10 of this embodiment has a substantially rectangular shape and has a sliding space 170 formed therein. The two substantially rectangular auxiliary deflector plates 171 are inserted into the sliding space 170. The auxiliary deflector plate 171 has a locking portion 173 at one end and a handle 175 at the other end. Since the auxiliary deflector plate 171 is provided, the auxiliary deflector plate 171 does not completely enter the sliding space portion 170 or, on the contrary, completely exit. And two auxiliary deflector plates 1
By sliding 71 in opposite directions, the deflector length d can be shortened or lengthened.

Next, an embodiment in which the second guide angle β is variable will be described. In the ninth embodiment shown in FIG. 14, the tubular wall portion 2
3 has a second guide angle β of a predetermined angle (for example, about 40 degrees) from the beginning. A substantially cylindrical auxiliary guide member 180 is slidably arranged inside the tubular wall portion, and the driving side screw gear 183 meshes with the screw gear 181 attached to the auxiliary guide member 180. Has been done. The rotation of the drive motor 185 is transmitted to the screw gear 181 by the gear 187, the worm gear 189, and the drive side screw gear 183, so that the auxiliary guide member 180 can be moved in the arrow direction in the drawing. .

Therefore, when the auxiliary guide member 180 is lowered to the state shown in FIG. 14, the second guide angle β becomes 0 degrees, while when the auxiliary guide member 180 is raised, the cylindrical wall portion 23 is removed. It can be changed to the second guide angle β which is about 40 degrees from the beginning. In the tenth embodiment shown in FIG. 15, the tubular wall portion 23 is divided into a plurality of pieces, and each is attached to the ceiling wall portion 21 so as to be swingable outward. A first shaft 191 is fixed to each divided portion, and the first shaft 191 is rotatably supported near the middle thereof. On the other hand, the other end of the first shaft 191 is connected to the second shaft 193 via the joint portion 192, and the other end of the second shaft 193 is connected to a disc 195 arranged near the center of the guide member 20 and above. Engaged. The disk 195 is rotatable by a drive motor 197.

The disc 195 is rotated and the second shaft 19 is rotated.
When the joint part 192 is moved to the center side through the third part, the first shaft 191 swings with the supporting part near its middle as a fulcrum, as shown by the chain double-dashed line in the figure, and the divided cylindrical wall The parts 23 are each swung outward. Therefore, the second guide angle β can be changed.

In the eleventh embodiment shown in FIG. 16, the tubular wall portion 23 is made of a rubber material and has elasticity. In this embodiment, the wires 201 are attached to the four points at the lower end of the tubular wall portion 23, and the four wires 201 are bundled at the center and locked by the stopper 203. By pulling the wire 201 and changing the position where the wire is locked by the stopper 203, as shown by the chain double-dashed line in FIG.
3 inclines inward so that the second guide angle β can be changed.

Next, a twelfth embodiment in which the width of the zone of the guide annular flow blown out is made variable will be described. As shown in FIG. 17, a first guide member 20 having a ceiling wall portion 21 and a tubular wall portion 23 is provided with a second ceiling wall portion 221 and a second tubular wall portion 223 inside the first guide member 20. The second guide member 220 is disposed, and the second guide member 220 includes
It is fixed to the guide member 20.

The deflector plate 10 has a cylindrical support member 2
30 is fixed, and this support member 240 penetrates the ceiling wall portion 221 of the second guide member 220 and is fitted inside the outlet portion 1 of the third duct 70. A sealing material 243 is interposed between a portion of the second guide member 220 that penetrates the ceiling wall portion 221 and a portion that fits with the outlet portion 1.

The threaded portion 230 is provided near the upper end of the support member 230, that is, in the portion fitted inside the outlet 1.
a is formed and meshes with the screw gear 241. Then, by rotating the screw gear 241 by the drive motor 240, the support member 230
The deflector plate 10 can be moved in the direction of the arrow in FIG. 17 (A). On the other hand, the support member 230
17B, a plurality of through holes 230b are formed in the circumferential direction in the vicinity of the lower end of the support member, that is, in the vicinity of being fixed to the deflector plate 10, so that the inside and outside of the support member 230 communicate with each other. is doing.

The operation of the twelfth embodiment will be described with reference to FIGS. 18 to 20, the drive mechanism such as the drive motor 240 and the screw gear 241 is omitted. First, when the support member 230 and the deflector plate 10 are lowered to the state of FIG. 18, the support member 23
The upper part of 0 is the first guide member 20 and the second guide member 220.
Block the passage between and. Then, the third duct 70 communicates only with the second guide member 220 side via the through hole 230b. Therefore, it is blown out as a guide annular flow from the second guide member 220. Thus, the second guide member 220
If it is blown out more, the air-conditioning range becomes narrower, and the vicinity of the head can be intensively cooled during so-called cooldown, which is very effective.

On the other hand, as shown in FIG. 19, the deflector plate 10 is raised to raise the ceiling wall portion 22 of the second guide member 220.
When the first duct 70 is brought into contact with the first guide member 2,
The second guide member 20 side is not connected to the first guide member 20 side through the through hole 230b. Therefore, the second guide member 220 functions as a deflector, and is blown out from the first guide member 20 as a guide annular flow. In this way, blowing out from the first guide member 20 widens the air conditioning range, and is convenient when, for example, cooldown is completed and it is desired to cool the entire human body and its vicinity.

As shown in FIG. 20, the through hole 230b
Is located so as to communicate with both the first guide member 20 side and the second guide member 220 side, which is convenient when a wind is required near the human body rather than in the case of FIG. This 12th
An example of control when varying the size of the zone of the guide annular flow to be blown out will be described using an embodiment. In FIG. 2, a temperature sensor (not shown) is provided in the suction port 60 and in the outlet portion 1 of the third duct 70 to detect the suction temperature and the blowout temperature and input them to a control unit (not shown). Then, when the temperature difference between the suction temperature and the blowout temperature is equal to or greater than a predetermined set value, the drive motor 240 is driven to lower the deflector plate 10 to narrow the air conditioning range and cool intensively. When the temperature difference becomes smaller than the set value, the deflector plate 1
Increase 0 to widen the air conditioning range.

In the twelfth embodiment, the deflector plate 10 is used.
Although it is arranged to move itself, as in the thirteenth embodiment shown in FIG. 21, the deflector plate 10 is fixed to the second guide member by the column 250, and is attached to the lower end of the support member 230 in the eleventh embodiment. A disk-shaped portion 251 having the same diameter may be provided to form the air passage switching duct 253 in the same manner.

Specifically, if the disk-shaped portion 251 is at the same position as the second ceiling wall portion 221, the communication with the second guide member 220 side is cut off, and the third duct 70 is passed through the through hole 230b. It communicates only with the first guide member 20 side. On the other hand, FIG.
As shown in FIG. 1, when the disk-shaped portion 251 is placed on the deflector plate 10, the communication with the first guide member 20 side is cut off, and the third duct 70 passes through the through hole 230b. It communicates only with the 1 guide member 220 side.

Next, a fourteenth embodiment of manual switching will be described with reference to FIG. Only the drive motor 240 and the screw gear 241 are omitted, and the other basic configurations are the same, and the same reference numerals are used. A screw portion 260 is formed on the upper portion of the support member 230 and is screwed into the inside of the outlet portion 1. Then, the deflector plate 10 is rotated in the direction of the arrow in the drawing by a hand or the like, so that the deflector plate 10 is rotated.
The position of can be raised or lowered.

Another embodiment will be described. In the fifteenth embodiment shown in FIG. 23, a small hole 270 is formed in the deflector plate 10.
A large number of holes are formed, and air is also ejected from the holes 270. By doing so as well, a weak wind can be blown into the inside of the wall surface jet along the guide member 20.

The deflector plate 10 is not provided in the sixteenth embodiment shown in FIG. In this embodiment, the third
The outlet portion 1 of the duct 70 is opened upward, and the ceiling wall portion 301 of the guide member 300 is formed larger than the outlet portion 1 and is separated from the outlet portion 1 so as to block the flow from the outlet portion. It is arranged. The tubular wall portion 303 is connected to the ceiling wall portion 301, is formed in a tubular shape toward the outlet portion 1 side, and has a larger inner diameter than the outlet portion 1.

The flow blown out from the outlet portion 1 collides with the ceiling wall portion 301 and flows in the circumferential direction, and is guided along the ceiling wall portion 301 and the cylindrical wall portion 303 which is connected to the outlet wall 305. It is blown out more annularly. Therefore, the first
Similar to the examples and the like, the guide annular flow blown out has a high speed on the outside and a low speed on the inner side, and since the development angle of the air flow is small, the reachability to the downstream is good and an air curtain-like region is formed. . Therefore, the blown out cool air spreads like an air curtain only around the seated occupant, and exerts an effect of blocking cool air inside the air curtain and warm air outside the air curtain, so that the temperature rise of the conditioned air is reduced.

Next, an embodiment in which the deflector position δ is variable will be described. The variable deflector position δ (= the distance from the end of the outlet portion 1 to the deflector plate 10) has been described in the above-described fourth and fifth embodiments (see FIGS. 9 and 10) and the like. In the seventeenth embodiment shown in (7), the deflector position δ is automatically changed only by hardware, not by automatic control by a computer or the like.

In the seventeenth embodiment, the deflector plate 10
However, the deflector column 13 in the first embodiment is not used and the spring 3 is used.
It is supported by 11. A damper 313 is also provided to absorb the vibration of the spring 311. Therefore, it can be seen that the deflector position δ increases as the force applied to the deflector plate 10 increases, that is, the wind speed V (unit: m / s) blown out from the outlet 1 increases.

The degree of wind speed at which the deflector position δ becomes is mainly determined by the spring constant of the spring 311. Therefore, how is the spring constant of the spring 311
One consideration is whether to use. FIG. 26 schematically shows a result of an experiment on how the formation state of the guide annular flow changes depending on the deflector position δ and the blowing air velocity V.

In FIG. 26A, the deflector position δ = 2.
The airflow formation state in the case of 5 (mm) and the blowing velocity V = 0.35 (m / s) is shown. In this case, the guide annular flow exceeds the cylindrical wall portion 23 and largely protrudes to the outside. Therefore, the guide annular flow zone spreads downstream, and the wind speed becomes slow.

On the other hand, when the deflector position δ = 25 (mm) shown in FIG. 26 (B) and the blowing air velocity V = 1.0 (m / s), the entrainment effect is strong and the guide annular flow is inward. It can be seen that the expansion angle becomes small due to being caught in the vehicle and the outside speed is high and the inside speed is slow, so that the downstream reachability is good and an air curtain-like region is well formed around the occupant P. .

Further, in FIG. 26 (C), the blowout air velocity V is V = 1.0 (m / s) which is the same as in FIG. 26 (A), but the deflector position δ is δ = 10 (mm). Shows the state of air flow formation. In this case, the deflector position δ is made small, that is, the distance from the end of the outlet portion 1 to the deflector plate 10 is shortened, even though the blowing air velocity is the same as in FIG.
It can be seen that the guide annular flow is caught inward and the expansion angle becomes small, and an air curtain-like region is well formed around the occupant P.

Therefore, for example, the blowing air velocity V = 1.0 (m /
spring 311 having a spring constant such that the deflector position δ = 25 (mm) in the case of s) and the deflector position δ = 10 (mm) in the case of the blowing air velocity V = 0.35 (m / s). Is adopted, at least at these two types of blown wind speeds (V = 1.0 m / s, 0.35 m / s), the deflector position such that an air curtain-like region is favorably formed around the occupant P. It is possible to realize a configuration in which δ changes automatically. Incidentally, FIG. 27 shows an experimental result for considering the relationship between the deflector position δ and the range of the occupant section (airflow corresponding thereto). The curve indicated by the white circle "○" is the blowing air velocity V = 1.0 (m
/ S), the curve shown by the white square “□” is the blowing air velocity V
= 0.5 (m / s), the curve indicated by the white triangle “Δ” is the case where the blowing air velocity V = 0.35 (m / s). The target value of the range of the occupant section (corresponding to the air flow) is 300 mm, and the upper and lower sides are 50 mm, that is, 250 mm to 350 m.
Let m be the target range. It can be seen that in order to achieve the target value, it is necessary to reduce the deflector position δ as the blowing air speed is lower.

The eighteenth embodiment of FIG. 28 is the wind speed sensor 31.
5, the blowout wind speed is detected, and the deflector position δ is automatically controlled based on the detected wind speed. In this embodiment, the deflector plate 10 has the shaft 320.
The drive side screw gear 323 is meshed with the screw gear 321 attached to the other end of the shaft 320. Then, the rotation of the drive motor 335 is changed by the gear 327, the worm gear 329, and the drive side screw gear 323 to the screw gear 32.
28, the deflector plate 10 can be moved in the direction of the arrow in FIG. 28 to change the deflector position δ.

The wind speed sensor 315 is arranged at the outlet 1, and the detection signal thereof is input to the amplifier 337. The amplifier 337 drives the motor 335 based on the wind speed detected by the wind speed sensor 315 to move the deflector plate 10 up and down. In addition, when the unpleasantness of the wind is desired to be reduced, the "fluctuation" button 339 is manually pressed to perform a certain period (for example, 10 seconds) of the deflector plate 1.
Allows fluctuations in air volume by raising or lowering 0.

As an example of automatically controlling the deflector position δ, when there are a plurality of outlets at positions corresponding to the respective seating positions in the vehicle, for example, the seating sensor determines whether or not the seats are seated, and the outlets that are not seated. For the deflector plate 1
It is also conceivable that 0 is pulled up to the uppermost portion, that is, to the position where the deflation plate 10 comes into contact with the ceiling wall portion 21 to close the air outlet.

In the seventeenth and eighteenth embodiments, the spring 311 is used.
Although the example in which the deflector position δ is made variable by driving the motor or the motor, the second guide angle β (= the angle of the cylindrical wall portion 23 with respect to the axial direction of the outlet portion 1) and the deflector angle γ shown in FIG. As for (= angle of the deflector plate 10 with respect to the direction orthogonal to the axial direction of the outlet portion 1), the deflector position δ
It can be implemented in the same manner as in the case of.

In the case of the second guide angle β, it may be set by a spring or motor drive so that the cylindrical wall portion 23 expands outward when the blowing air velocity is high, and contracts inward when it is small. On the other hand, the deflector angle γ can also be set by a spring or a motor drive so that the deflector angle γ also changes depending on the blowing wind speed. Further, for example, when the window becomes cloudy, it may be possible to control the deflector angle γ so that the airflow is directed toward the window so as to clear the window.

Although all of the above-described embodiments are examples in which the present invention is used as an air conditioner for automobiles, the present invention is not limited to automobiles or seats, and convection is not necessary. It is applicable as long as it has an outlet part for blowing out.

[0077]

As described above, the annular airflow blown out by the fluid flow blowing control device of the present invention reaches the downstream because the outer speed is fast and the inner speed is slow, and the expansion angle of the airflow is small. Good properties and an air curtain-like area is formed. Therefore, for example, if it is used in the blowout part of an air conditioner for a seat, the cool air blown out during cooling will spread like an air curtain only around the occupant, and will also have the effect of blocking the cool air inside the air curtain from the warm air outside. Therefore, the temperature rise of the conditioned air also decreases. Further, by realizing the intensive blowout to the necessary area, it is possible to contribute to the reduction of power consumption.

[Brief description of drawings]

FIG. 1 shows a first embodiment of a fluid flow blowout control device of the present invention, (A) is a sectional view thereof, and (B) is a bottom view thereof.

FIG. 2 is a schematic cross-sectional view schematically showing the front of a vehicle compartment of an automobile.

FIG. 3 is an explanatory view schematically showing elements that change the shapes of the deflector plate and the guide member.

FIG. 4 is a diagram showing experimental results and showing a flow of air by streamlines.

FIG. 5 is a sectional view showing a modification of the first embodiment.

6A and 6B show experimental results, where FIG. 6A is an explanatory view showing an experimental condition type A, FIG. 6B is an explanatory view showing a type B similarly, and FIG. 6C is a graph showing a temperature at each detection point on the detection line DL. FIG.

7A is a sectional view showing the second embodiment, and FIG. 7B is a bottom view of the same.

8A is a sectional view showing a third embodiment, and FIG. 8B is a bottom view of the same.

9A is a sectional view showing a fourth embodiment, and FIG. 9B is a bottom view of the same.

FIG. 10A is a sectional view showing a fifth embodiment, and FIG.
FIG. 6 is a perspective view of a deflector support member.

11A is a sectional view showing a sixth embodiment, and FIG.
Is also a bottom view.

FIG. 12A is a sectional view showing a seventh embodiment, and FIG.
[Fig. 4] is a bottom view of the deflector plate.

13A is a sectional view showing an eighth embodiment, and FIG.
Is also a bottom view.

FIG. 14 is a sectional view showing a ninth embodiment.

FIG. 15 is a sectional view showing a tenth embodiment.

FIG. 16A is a sectional view showing an eleventh embodiment,
(B) is a bottom view of the same.

FIG. 17A is a sectional view showing a twelfth embodiment,
(B) is a perspective view showing a deflector and a supporting member.

FIG. 18 is a sectional view showing the operation of the twelfth embodiment.

FIG. 19 is a sectional view showing the operation of the twelfth embodiment.

FIG. 20 is a sectional view showing the operation of the twelfth embodiment.

FIG. 21 is a sectional view showing a thirteenth embodiment.

FIG. 22 is a sectional view showing a fourteenth embodiment.

FIG. 23A is a sectional view showing a fifteenth embodiment,
(B) is a bottom view of the same.

FIG. 24A is a sectional view showing a sixteenth embodiment,
(B) is a bottom view of the same.

FIG. 25 is a sectional view showing a seventeenth embodiment.

FIG. 26 is a diagram schematically showing a result of an experiment on how the state of formation of the guide annular flow changes depending on the deflector position δ and the blowing air velocity V.

FIG. 27 is a graph showing an experimental result for considering a relationship between a deflector position δ and a range of an occupant portion (airflow corresponding thereto).

FIG. 28 is a sectional view showing an eighteenth embodiment.

[Explanation of symbols]

DL: detection line, L: guide plate length,
P ... Occupant, d ... Deflector length, α ... First guide angle, β ... Second guide angle, γ ... Deflector angle,
δ ... Deflector position, 1 ... Exit part, 10 ... Deflector plate, 13 ... Deflector support, 20, 22
0,300 ... Guide member, 21, 221, 301 ... Ceiling wall part, 23, 223, 303 ... Cylindrical wall part, 30, 305
… Outlet

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Masahiko Osuka 1-1, Showa-cho, Kariya city, Aichi Prefecture Nihon Denso Co., Ltd. (72) Inventor Shinji Aoki 1-1-1, Showa-cho, Kariya city, Aichi prefecture Nidec Corporation Within the corporation

Claims (2)

[Claims] 1. A device provided in the vicinity of an outlet through which a fluid flows,
A fluid flow blowout control device for controlling a fluid blown out from the outlet part, the device being formed so as to be larger than the outlet part, separated from the outlet part, and arranged so as to interrupt the flow downstream of the outlet part. A deflector plate, a ceiling wall portion that is continuously provided outward in the circumferential direction from the vicinity of the outlet portion, and a cylindrical shape that is provided continuously to the ceiling wall portion and extends toward the downstream side, and has a larger inner diameter than the deflector plate. And a tubular wall portion having a guide member, and the flow blown out from the outlet portion is guided to the deflector plate and the guide member and blown out in an annular shape. Blowing control device. 2. Provided in the vicinity of the outlet portion through which the fluid flows,
A fluid flow blowout control device for controlling a fluid blown out from the outlet part, the device being formed so as to be larger than the outlet part, separated from the outlet part, and arranged so as to interrupt the flow downstream of the outlet part. And a guide member having a ceiling wall portion and a tubular wall portion that is connected to the ceiling wall portion and is formed in a tubular shape toward the outlet portion side and has an inner diameter larger than that of the outlet portion. A fluid flow blowout control device characterized in that the flow blown out from the section is guided to the guide member and blown out in an annular shape.