JPS6135871Y2 - - Google Patents

Description

[Detailed description of the invention] The present invention relates to the improvement of a fluid blowing element, and in particular aims to improve the deflection angle of the fluid blowing element attached to the blowing part of an air conditioner and the noise during deflection. This is one of the

Conventionally, this type of fluid blowing element installed in an air conditioner has a small wind direction deflection angle and the entrainment phenomenon of the air flow within the control port at the upstream end of the guide wall is not stable, so a uniform deflection flow cannot be obtained. the result,
There are disadvantages in that the distance the wind reaches is shortened, and the unstable entrainment phenomenon increases the noise level at the time of maximum wind deflection.

The present invention eliminates the drawbacks of the conventional fluid ejection elements mentioned above.

Hereinafter, the present invention will be described with reference to the accompanying drawings showing one embodiment thereof.

First, the structure of the fluid blowing element will be explained with reference to FIG.

In the figure, reference numeral 1 denotes an element side wall made of synthetic resin, on which a nozzle forming portion 2, a guide wall 3, and a control port 4 are integrated by extrusion molding. This element side wall 1 is formed symmetrically with respect to the axis XX of the air outlet. Further, an arcuate portion r is formed at the upstream end of the guide wall 3, and is curved toward the inside of the control port 4. Reference numeral 5 denotes a lower cover made of synthetic resin or the like, and a groove 5a that fits into the lower end of the element side wall 1 is formed in the same planar shape as the element side wall 1.
The formation of this groove 5a improves the sealing performance with the element side wall 1. Reference numeral 6 denotes an upper lid that closes the upper end of the element side wall 1, and has a groove (not shown) formed therein similarly to the lower lid 5, and provides good sealing with the element side wall 1. This is a closing port provided in the upper lid 6, and is formed at a laterally symmetrical position corresponding to the control port 4. Reference numeral 8 denotes a closing plate driven and rotated by a motor 9, which rotates at a constant cycle to sequentially open and close the closing port 7 provided in the upper lid 6 at a constant cycle.

Next, the operation of the fluid blowing element in the above structure will be briefly explained. Blower from upstream side (not shown)
The air sent by the nozzle forming portion 2 causes a contracted flow and flows into the fluid element as a jet flow.
The jetted wind entrains the air in the control ports 4 provided on the left and right side walls 1 of the element, and flows out from the fluid element while making the pressure in the control ports 4 negative with respect to the atmosphere. Here, assuming that the closing plate 8 driven and rotated by the motor 9 is in a state in which neither of the closing ports 7 provided in the upper lid 6 is closed, the insides of the left and right control ports 4 are equally filled with air from the closing ports 7. The jet is blown out from the center to the front.

Next, when the motor 9 rotates and the closing plate 8 closes the left closing port 7 in FIG. 1, the left control port 4 cannot receive air supply, resulting in a pressure drop. The jet is pulled to the left by this negative pressure and adheres to the surface of the guide wall 3 having an arcuate portion r at the upstream end.
Due to the Coanda effect, the wind flows along the guide wall 3,
It is deflected to the left and blown out. The deflection operation to the right side is similar to the deflection operation to the left side.
This is done by occluding the

Next, the effect of the arcuate portion r provided on the guide wall 3 in the deflection operation of the fluid blowing element having the above structure will be explained with reference to FIGS. 2 to 9.

Here, Fig. 2 shows the structure of the fluid blowing element used for experiments of the present invention, Fig. 3 shows the structure of a conventionally known fluid blowing element, and Fig. 4 shows the measurement state of the wind speed distribution. It shows. Furthermore, Figures 6 to 9
The figure shows data of experimental results described below.

That is, FIG. 6 shows the differential pressure 4P between the setback value Se and the pressures P _L and P _R at each control port 4 using the arcuate portion r at the upstream end of the guide wall 3 in FIG _{. 2} as a parameter. ) is a graph showing the relationship between As a result, the larger the diameter of the arcuate portion r is, the larger the differential pressure 4P between the left and right control ports 4 is, and the larger the setback Se is, the larger the pressure difference 4P between the left and right control ports 4 is.
It can be seen that a large differential pressure 4P can be obtained. (In this experiment, the radius of the arcuate portion r was confirmed up to 7.5 mm.) This is because the flow coming out of the nozzle is entrained at the control port 4, and the larger the radius of the arcuate portion r, the more the radius of the arcuate portion r is 7.5 mm. Conventional entrainment flow b shown in Figure 3
This is because the entrainment flow a is generated with less loss compared to the above, and as a result, the negative pressure inside the control port 4 becomes larger.

FIG. 7 also shows the relationship between the setback value Se and the deflection angle θ when the radius of the arcuate portion r of the guide wall 3 is changed from 0 mm to 7.5 mm in steps of 2.5 mm. The deflection angle θ is the arcuate portion r
It is largest when the radius of is set to 5 mm. Furthermore, the larger the setback value Se is within the range of 7 mm, the larger the deflection angle θ can be obtained. Based on these experimental results, the setback value Se is 7.
At mm or less, the differential pressure 4P at the control port and the deflection angle θ
It can be seen that there is a positive correlation between

Next, the experimental results shown in FIGS. 8 and 9 will be explained. This means that the radius of the arcuate portion r is 0 in Fig. 8.
That is, the conventional structure is shown, and FIG. 9 shows the arcuate part r.
The results are shown when the radius of is 5 mm. Then, as shown in Fig. 4, the wind speed distribution and deflection angle at each point in the X direction 50 mm downstream from the end face of the air outlet of the fluidic element were measured using a two-dimensional hot wire anemometer A (one X-shaped pull). Measurements were made at intervals, and data processing and plotting using a computer were performed for each setback value Se. The wind speed distribution V indicated by each dotted vertical axis indicates relative comparison, and its direction indicates the deflection angle θ. In addition, since the two-dimensional hot wire anemometer measures at an angle of 20° from the blowout direction, the actual deflection angle θ
is the value obtained by adding 20° to the dotted line indicating the wind speed V.

Based on the data shown in Figures 8 and 9, when comparing the cases where the radius of the circular arc part r is 0 mm and 5 mm, the case of Figure 9 (radius of the circular part r = 5 mm) has the fastest wind speed. The central portion is moved to the left (this data indicates left deflection motion).

This effect increases the distance that the wind travels, and as a result, the human body feels that the wind is bending more easily.

As described above, the arcuate portion r formed at the upstream end of the guide wall 3
Having explained the relationship between the size of .theta. and the deflection angle .theta., next, another effect of the arcuate portion r of the guide wall 3, which is noise reduction, will be explained. In a window integrated air conditioner (not shown) incorporating a conventional fluid blowing element, the noise value in the front blowing state is 56 dB (A) when the air volume is 11 m ³ /min, but the noise level is 56 dB (A) when the air is blowing from the left or right. The maximum deflection was 58 dB (A), causing extreme discomfort. However, in a window integrated air conditioner that incorporates a fluid blowing element with an arcuate portion with a radius of 5 mm at the upstream end of the guide wall 3, the air flow rate is 56 dB (A) even when blowing from the front and when deflecting to the left and right. A quiet and pleasant driving noise result was obtained.

In this embodiment, a structure was explained in which the arcuate portion r on the upstream side of the guide wall 3 was bent into an arcuate shape, but it was formed into a curved shape as shown in a to c of FIG. Similar results can be obtained even if the curved surface is extended inward from the tangent y.

As is clear from the above embodiments, the fluid blowing element of the present invention includes an arcuate portion provided at the upstream end of the guide wall,
With a simple structure in which the end extends inside this arc-shaped connection, a large wind deflection angle can be obtained, and the distance the wind can reach is also extended, resulting in a good wind deflection. In addition to increasing the perceptible deflection effect, there is no abnormal noise generated during the maximum deflection to the left or right, and a quiet operation effect can be obtained.

[Brief explanation of the drawing]

Fig. 1 is an exploded perspective view of a fluid blowing element according to an embodiment of the present invention, Fig. 2 a and b are explanatory diagrams and enlarged views of essential parts of the wind direction deflection operation of the fluid blowing element, and Fig. 3 is an exploded perspective view of a fluid blowing element according to an embodiment of the present invention. An explanatory diagram of the wind direction deflection operation of the fluid blowing element, FIG. 4 is an explanatory diagram showing the actual noise measurement state of the fluid blowing element, and FIGS. 5 a to 5 c are circles of the fluid blowing element showing other embodiments of the present invention. 6 is a cross-sectional view of the arcuate portion, FIG. 6 is an experimental result diagram showing the relationship between the setback value Se and the control port differential pressure 4P in the fluid blowing element of the present invention, and FIG. 7 is a graph showing the relationship between the setback value and the deflection angle θ in the fluid blowing element. Experimental results diagrams showing the relationship, FIGS. 8 and 9, are wind speed distribution diagrams in different cases in the same fluid blowing element, respectively. 1... Element side wall, 2... Nozzle forming part, 3...
Guide wall, 4... Control port, 7... Obstruction port, r... Arc-shaped portion, y... Tangent line.

Claims (1)

[Scope of utility model registration request] A nozzle part that throttles the air from the blower and allows it to flow in, a control port part that applies pressure to the flow of air that has passed through the nozzle part from a direction perpendicular to the flow direction, and a control port part that generates pressure at the control port part. In the fluid blowing element, the upstream end of the guide wall is located at a position inside the tangent line of the fluid blowing element, which has a closing plate that causes the wind to blow out, and a guide wall that is formed in a substantially arc shape that causes a Coanda effect in the blown wind. Fluid blowout element set to .