JPH0338496B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a flow direction control device that is installed at an air outlet of an air conditioner or the like and deflects the flow from an air source in an arbitrary direction. be.

Conventional configuration and its problems In an air conditioner that performs cooling and heating, in order to equalize the temperature distribution in the room being air-conditioned, the blowing flow direction must be controlled to blow downward during heating and horizontally during cooling. is desirable.

Furthermore, if a large amount of hot air is blown downward during heating, the amount of hot air may be too large and may cause discomfort when it hits the human body. Experiments have confirmed that if the purpose is to maintain a constant temperature distribution, an almost constant temperature distribution can be obtained by blowing out a certain amount downward and the rest in the horizontal direction. Therefore, in order to improve the temperature distribution and eliminate the discomfort caused by the blown hot air, a function for blowing out a certain amount of hot air in a downward direction and the rest in a horizontal direction, that is, a function of dividing the flow, has been necessary.

A conventional example for achieving this purpose is shown in FIGS. 1 and 2. In the figure, 1 is a blowout passage, 2 is a first adhesion wall, 3 is a second adhesion wall, and 4 is a control blade that rotates around an axis 5. 6 is a means for directing the flow inward. 100 is an outlet of the blowing passage.

The flow that has reached the outlet 100 of the blow-off passage 1 blows out the adhering walls 2 and 3 while being controlled by the rotation of the control blades 4 and changing the blow-out direction as desired. Further, when the control vane 4 is in the position shown in the figure, the flow is divided into two directions and flows out as shown by the dashed line in the figure. In this way, by rotating one shaft, it is possible to blow out the flow in any direction and also perform a flow dividing operation.

However, if the width H in Fig. 1 is small, the above operation is performed, but the width H becomes large (approximately 10 times or more the nozzle width W shown in Fig. 1).
A problem arises in that the shunting operation becomes incomplete.
The reason for this is that each jet jet blown out at the time of separation flows out while drawing in the surrounding flow. When the width H is small (within about 10 times the nozzle width W), this entangled flow is compensated for from the front and sides, so no negative pressure is generated in the space sandwiched between the two jets. However, when the width H becomes large (approximately 10 times or more the nozzle width W), the amount of flow supplemented from the sides remains constant, and negative pressure is generated in the space between the jets. As a result, the two jets attract each other and eventually merge. (This is shown by the broken line in FIG. 2.) For this reason, even if an attempt is made to perform a split flow operation, the result will be a single jet flow.

Further, in the conventional example, there was a problem in that the flow path was pinched during the diversion operation, resulting in a significant decrease in air volume.

Purpose of the invention The present invention solves such conventional problems,
It is an object of the present invention to enable reliable flow diversion operation even when the width H becomes large, and to prevent the air volume from decreasing substantially even during the diversion operation.

Structure of the Invention In order to achieve this object, the present invention provides a curved guide wall or a curved guide wall including a partially straight line on one surface of the outlet of the blowing passage, and on the side opposite to the said surface. means for directing the flow inward, downstream thereof a substantially straight wall and flow control vanes rotatable about an axis, said flow control vanes having two biasing surfaces and a curved section; The angle formed by the tangential direction of the downstream end of the guide wall and the direction of the substantially straight wall causes the flows attached to the two walls to merge due to negative pressure caused by the entrainment of the respective jets. It is set so that the size exceeds the angle.

This configuration increases the amount of flow flowing in from the front and suppresses the generation of negative pressure between the two jets. Even when the outlet width H becomes large, it is possible to reliably divide the flow and reduce the air volume. This allows deflection and diversion operations to be performed with almost no change.

DESCRIPTION OF EMBODIMENTS An embodiment of the present invention will be described below with reference to FIGS. 3 to 5. In FIGS. 3 and 4, 1 is a blowout passage, 7 is an outlet, 8 is a curved guide wall (as shown in the figure, there may be a part of the straight line on the downstream side of the curve), and 9 is a guide wall 8. 10 is a straight wall provided downstream of the bias projection 9;
is a flow control vane rotatable about an axis 110, which is formed by surfaces 12 and 13 having a biasing action and a curved portion 14. (For simplicity, 12
The surface 13 is the bias action surface, and the surface 13 is the diversion action surface.) Further, the connecting portion 15 between the bias acting surface 12 and the curved portion 14 is formed in a substantially arc shape. In addition, the straight wall 10 faces slightly upward,
The tangential direction of the downstream end of the guide wall 8 faces almost directly below. In other words, the angle θ ₂ between these two walls is
It is enlarged to more than 90°.

FIG. 6 shows a case where the above-described embodiment is applied to a ceiling-mounted heat pump air conditioner. 16
is the air conditioner main body casing, 17 is a sirotskov fan, 18 is a heat exchanger, 19 is a heater, 20 is an inclined top plate for restricting the outlet, and 21 is a lower aperture. Reference numeral 22 denotes left and right deflection vanes that deflect the flow in the left and right directions.

In the above configuration, the blowing direction of the blowing flow is controlled according to the rotation of the flow control blade 11 as shown in FIGS. 3 to 5. Fig. 3 shows the state of horizontal blowing, Fig. 4 shows the state of downward blowing, and Fig. 5 shows the state during diversion operation. First, the horizontal blowing state shown in FIG. 3 will be explained. In this case, the flow control vanes 11 are set in a horizontal position. (The position of the flow control vane 11 in FIG. 3 is assumed to be a horizontal position.) The flow F from upstream is divided into an upper flow Fa and a lower flow Fb at the flow control vane 1 in the figure. At this time, since the connecting portion 15 has a substantially arcuate shape, the flow separates smoothly without being disturbed.
Fa flows along the curved portion 14 due to the flow Fc due to the action of the bias protrusion 9, and Fb flows along the bias action surface 12. Flow along curved portion 14
Fa flows along the straight wall 10 because it interferes with the straight wall because it is nearby. On the other hand, the lower flow Fb flows along the bias action surface 12, but merges with the upper flow Fa, so that the entire flow flows in a substantially horizontal direction. Next, the state of downward blowing as shown in FIG. 4 will be explained. In this case, the flow control vanes have been rotated approximately 60 degrees counterclockwise in the figure from the horizontal blow state. In this case, the flow F is divided into a flow Fa above the flow control blade 11 and a flow Fb below, as in the case of horizontal blowing. and the upper flow Fa
is directed downward by the flow Fc caused by the bias protrusion 9 and attaches to the curved portion 14 of the flow control vane 11. On the other hand, the flow Fb on the lower side is the bias action surface 12
It is directed downward by the Coanda effect and adheres to the guide wall 8 due to the Coanda effect. Since the upper flow Fa flows along the curved surface part 14 of the flow control vane 11, it easily merges with the lower flow Fb, and the entire flow flows downward by adhering to the guide wall 8. It will be deflected and it will blow out. As a result, the adhesion effect of the flow to the wall is effectively utilized, so
A downward blow deflection of approximately 85° is possible when the rate of decrease in air volume is within 10% compared to the case of horizontal blow.
Next, the state of the flow dividing operation as shown in FIG. 5 will be explained. In this case, the flow control vanes 11 have been rotated approximately 120 degrees counterclockwise from the horizontal blow setting state. In this case, the flow F is the flow control vane 1 as before.
1 is divided into an upper flow Fa and a lower flow Fb.
The upper flow Fa is directed in the direction of adhering to the straight wall 10 by the action of the bias action surface 12, efficiently adheres to the straight wall 10, and is blown out horizontally as it is. The lower flow Fb is directed in the direction of adhering to the guide wall 8 by the action of the flow dividing surface 13, efficiently adheres to the guide wall 8, and blows out in the downward direction. As a result, the flow is split horizontally and downwardly. As a result of the above, as in the case of downward blowing, the diversion operation becomes possible when the rate of decrease in air volume is within 10% compared to the case of horizontal blowing. In addition, since the straight wall 10 faces slightly upward and the guide wall 8 faces almost directly below, the flow path widens when the flow is split, reducing the decrease in air volume and widening the deflection angle width. It turns out. Moreover, as a result of increasing θ ₂ in the figure, the angle formed by the jets adhering to the two walls increases. This produces the following effects.

In the splitting operation, the two jets flow out by drawing in the surrounding fluid as in the conventional case, but because the opening angle θ between the jets is large, the flow between the two jets is compensated for by the flow from the front. No pressure is created. In other words, when θ is approximately 75° as in the conventional case, the two jets are close to each other, so the two jets do not merge until the width H is approximately 10 times the nozzle width W, but beyond that, the two jets The negative pressure between them increases and the two jets merge. On the other hand, when θ is widened to about 90° or more, flow is supplemented from the front between the two jets, the negative pressure does not increase, and no merging occurs regardless of the width H. As a result, even if the width H becomes large, supplementary flow from the sides is not required, so that the diversion operation is always guaranteed.

Hereinafter, the content of the present invention will be specifically explained using FIG. 3. That is, specific dimensional relationships are shown below. In the figure, based on the nozzle height W, the heightwise position of the vane 11 L/W = 0.5, the distance from the means 9 for directing the flow inward, K/
W = 0.2 Major axis J/W of flow deflection member 11 = 0.35 Minor axis I/W of flow deflection member 11 = 0.2 Angle θ between surfaces 12 and 13 having bias action = 120° Formed with the flow direction of the straight wall Due to the angle α=10° or more, deflection and diversion operations are possible with an air volume reduction rate of 10% or less, as described above.

FIG. 7 shows the relationship between θ and branching/merging. Width H
is 5 times the nozzle width W or less, θ
A split flow occurs at 75°. However, if the width H is 10 times or more the nozzle width W, they will merge when θ is 75°. On the other hand, when θ becomes 90° or more, the width H becomes
Even if the current is 10W or more, shunt operation will be performed. Therefore, by setting θ to 90° or more, the shunting operation is always possible regardless of the value of the width H.

When the flow direction control device that performs the above action is applied to a ceiling-mounted heat pump air conditioner as shown in FIG. It is heated or cooled and enters the blowout passage 1 of the flow control device. This flow is blown out by being vertically deflected or divided over a wide angle by the above-mentioned action. As a result, the most comfortable blowout control can be achieved by changing the blowout pattern: horizontally when the flow is cold, warm air and downward when the flow is small, and branching when the flow is warm and large. becomes.
In addition, when trying to increase the air conditioning effect by making the air conditioning flow reach farther during cooling, by tilting the control vane 11 to the position shown in Fig. 6, the flow is blown upward and the ceiling of the flow is increased. It promotes the adhesion effect to the air, reduces the fall of cold air, and allows the flow to be sent over long distances.

Effects of the Invention As described above, the flow direction control device of the present invention provides the following effects.

(1) Since the structure is such that the opening angle of the flow that is blown out along the two opposing adhesion walls is expanded, even when the width of the outlet is increased, it is possible to reliably divide the flow.

(2) Since the opening angle of the air outlet is expanded, it is possible to increase the deflection angle width of the air outlet, and there is almost no decrease in the air volume when dividing the flow.

(3) Since the attached wall surface faces upward, when applied to a ceiling-mounted air conditioner, etc., it is possible to attach the air flow to the ceiling and increase the distance the flow reaches.

(4) By rotating a single shaft, wide-angle deflection and shunting operations can be performed with almost no change in air volume.

[Brief explanation of the drawing]

FIG. 1 is a perspective view of a conventional flow direction control device, FIG. 2 is a sectional view taken along line A-A in FIG. 1, and FIGS. 3 to 5 are cross sections showing an embodiment of the flow direction control device of the present invention. 6 is a sectional view of an embodiment in which the flow direction control device of the present invention is applied to a ceiling-mounted air conditioner, and FIG. 7 is a characteristic diagram of the same flow direction control device. DESCRIPTION OF SYMBOLS 1... Blowout passage, 7... Outlet part, 8... Guide wall, 9... Means for directing the flow inward (bias protrusion), 10... Straight wall, 11... Flow control vane,
12, 13... Two surfaces with bias action,
14...Curved surface portion, 110...Axis.

Claims (1)

[Scope of Claims] 1. A curved guide wall or a curved guide wall including a partially straight line is provided on one surface of the outlet of the blowing passage, and means for directing the flow inward is provided on the side opposite to said surface. , a substantially straight wall is provided downstream thereof, and a flow control vane is provided which is rotatable about an axis, the flow control vane being comprised of two surfaces having a biasing action and a curved portion, and the flow control vane is comprised of two surfaces having a biasing action and a curved portion, is formed so that it acts to direct the flow in two directions when setting a branch flow, and in other cases acts to direct the flow in a single direction in cooperation with the curved surface part, and in the tangential direction of the downstream end of the guide wall. and the direction of the substantially straight wall is set to be 90° or more. 2. Claim 1, wherein the substantially straight wall is oriented outward with respect to the upstream flow direction, and the tangential direction of the downstream end of the guide wall is oriented substantially perpendicular to the upstream flow direction. Flow direction control device as described in .