JP5506821B2 - Air conditioner - Google Patents

Description

  The present invention relates to an air conditioner including a cross flow fan used as a blowing means.

Some conventional air conditioners are provided with a flow rate control member such as a mesh member between the heat exchanger and the crossflow fan in order to appropriately adjust the airflow flowing into the heat exchanger. (For example, refer to Patent Document 1).
Here, the structure of a conventional air conditioner including the cross flow fan will be described.
An air inlet is formed in the front portion of the casing of the air conditioner, and an air outlet is formed in the lower portion of the front. In the casing, a filter, a heat exchanger, a semi-cylindrical mesh member, and a cross-flow fan are sequentially arranged from the upstream side to the downstream side of the air flow path from the air inlet port to the air outlet port. ing.
The heat exchanger is composed of a refrigerant pipe and a plurality of fins arranged in parallel across the refrigerant pipe, and is located behind the air suction port. The semi-cylindrical mesh member has an arc shape equidistant from the central axis of the cross flow fan over the entire air suction port formed by the casing side rear guide and the drain pan side tongue of the cross flow fan. Is provided. Further, the cross flow fan is disposed at a position downstream of the heat exchanger and the mesh member corresponding to the installation shape of the air flow passage.
When the cross-flow fan is driven during cooling and heating, indoor air is supplied from the air suction port to the heat exchanger and heat exchange (heating or cooling) is performed. Thereafter, the heat-exchanged air is blown out from the air outlet through the cross flow fan into the room at a predetermined angle as appropriate.

JP-A-6-317334 (page 2-3, FIG. 1)

  However, in the configuration of the conventional air conditioner, a pressure loss body (flow velocity control member) such as a mesh member is provided between the heat exchanger and the cross flow fan in order to slow down the wind speed in the vicinity of the tongue. However, there are problems such as an increase in cost and an increase in power consumption of the fan motor due to an increase in input of the fan motor.

  The present invention solves the above-mentioned conventional problems, and flows into the heat exchanger at the lower front side without providing a separate pressure loss body on the secondary side of the heat exchanger (between the heat exchanger and the cross flow fan). An object of the present invention is to provide an air conditioner that effectively reduces the wind speed and has sufficient heat exchange capability without impairing the cooling and heating capability.

In order to solve the above-described conventional problems, an air conditioner according to the present invention includes a main body, an air passage provided so that air passes through the main body, a heat exchanger and a cloth disposed in the air passage. In the air conditioner including a flow fan, a tongue provided around the cross flow fan, and a rear guide, the front panel of the main body is configured vertically, and the main body has an inlet for the air passage. And the heat exchanger has a three-part heat exchanger including a front lower heat exchanger installed in parallel with the front panel, and the cross It is arranged in an inverted V shape upstream of the flow fan, and the number of rows of refrigerant pipes of the lower front heat exchanger is smaller than that of the other two parts of the heat exchanger, The wind speed flowing into the front lower heat exchanger will decrease The, the tongue, the tip of the drain pan located below the lower front heat exchanger, said has a configuration which is extended along the rotational direction of the cross flow fan and the center of the cross flow fan The tongue center angle, which is the angle formed between the line connecting the tip of the tongue and the line connecting the center of the cross flow fan and the tip of the drain pan, is θ, and the front lower heat exchange from the center of the cross flow fan When the angle formed by the line extending horizontally toward the vessel and the line connecting the center of the cross flow fan and the tip of the drain pan is α, the θ is 0.7α ≦ θ ≦ 0.98α. It is a range .

  According to the present invention, the tongue portion is configured to extend along the rotation direction of the cross flow fan, so that a pressure loss member is not separately provided between the heat exchanger and the cross flow fan as in the prior art. The wind speed flowing into the heat exchanger can be effectively reduced, and sufficient heat exchange capability can be ensured.

It is a section side view showing the composition of the air harmony machine concerning Embodiment 1 of the present invention. It is a schematic diagram for demonstrating the positional relationship of the crossflow fan, tongue part, and front lower part heat exchange in the air conditioner which concerns on Embodiment 1 of this invention. It is a figure which shows the flow of air when the tongue part center angle | corner (theta) is 30 degree | times. It is a figure when tongue part center angle (theta) is 95 degree | times. It is a figure which shows the flow of air when tongue part center angle | corner (theta) is 60 degree | times. It is a graph which shows the change of the heat exchange capability ratio by the change of tongue part center angle (theta). It is a cross-sectional side view which shows the structure of the air conditioner which concerns on Embodiment 2 of this invention. It is a cross-sectional side view which shows the structure of the air conditioner which concerns on Embodiment 3 of this invention.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the illustrated embodiment.

Embodiment 1 FIG.
1 is a cross-sectional side view showing an air conditioner according to Embodiment 1 of the present invention.
An air conditioner 10 according to Embodiment 1 includes a main body 1 made of a box-shaped casing, a heat exchanger 2 and a cross flow fan 3 disposed in an air passage 4 formed in the main body 1. ing.
The heat exchanger 2 indicated by 2 as a whole is constituted by a three-part cross-fin tube heat exchanger in this example. In other words, the heat exchanger 2 is vertically sectioned as shown in the drawing and viewed from the side, the front lower heat exchanger 2c located on the drain pan 14 and located on the front side of the cross flow fan 3 is shown. And a front heat exchanger 2b which is disposed on the upper side of the lower front heat exchanger 2c and whose upper end is inclined rearward, and a rear heat which is connected on the upper side of the front heat exchanger 2b and is inclined lower rearward. The heat exchangers 2a to 2c of these three parts are configured to be connected in an inverted V shape so that the refrigerant flows continuously. Furthermore, the heat exchangers 2a to 2c of each portion are configured by repeatedly reciprocating the refrigerant pipe 5 through a large number of fins arranged in parallel in the lateral direction (direction perpendicular to the drawing sheet).

  A top air inlet 6 and a front air inlet 7 are formed on the upper surface and lower front of the main body 1 (below the front panel 11 on the front), respectively, and an air blower opening toward the front is formed on the lower portion of the main body 1. An outlet 8 is formed. The upper surface air inlet 6, the front air inlet 7 and the air outlet 8 form an air passage 4 through which air passes through the main body 1. An air cleaning filter 9, the heat exchanger 2, and the cross flow fan 3 are disposed in the air path 4 in order from the upstream side. A tongue 12 and a rear guide 13 are provided around the cross flow fan 3 in order to form an air suction port of the cross flow fan 3. Further, the tongue 12 is extended along the rotation direction of the cross flow fan 3 (arrow direction shown in the drawing) so that the wind speed flowing into the front lower heat exchanger 2c decreases. Moreover, the tongue part 12 is arrange | positioned under the front lower heat exchanger 2c, and is integrally formed with the drain pan 14 for receiving the drain water dripped from the heat exchangers 2b and 2c.

  In the air conditioner 10, when the cross flow fan 3 is rotationally driven, air is sucked from the upper surface air inlet 6 and the front air inlet 7, and the sucked air is heat-exchanged with the refrigerant in the heat exchanger 2. The air that has become cold air or warm air is blown into the room from the air outlet 8. The air outlet 8 is equipped with a louver (not shown) for changing the direction of the blown air.

FIG. 2 is a cross-sectional side view showing the main part of the present invention, for explaining the positional relationship among the crossflow fan 3, the tongue 12 and the front lower heat exchanger 2c of the air conditioner according to Embodiment 1. It is a schematic diagram.
In FIG. 2, the center of the crossflow fan 3 is O, a line extending horizontally from the center O toward the lower front heat exchanger 2c is 30, and the center O of the crossflow fan 3 and the tip 12a of the tongue 12 are connected. 31 is a line, 32 is a line connecting the center O of the crossflow fan 3 and the tip 14a of the drain pan 14, the angle between the line 30 and the line 32 is α, and the angle between the line 31 and the line 32 (hereinafter referred to as the tongue) Where the tongue central angle θ is 0.5α ≦ θ <1.05α, preferably 0.7α ≦ θ ≦ 0.98α. The height position of 12a is set. In addition, the position of the center O of the crossflow fan 3 is disposed at a substantially intermediate position of the height dimension L (the height below the bent portion) of the front lower heat exchanger 2c. Α is set in a range of 60 degrees to 70 degrees.

  In the cross flow fan 3, the flow that flows into the impeller crosses the impeller in the diametrical direction, that is, the flow first flows inward in the radial direction of the impeller and then flows outward. It has the feature of passing through twice. In particular, when the crossflow fan 3 is installed in the main body 1, the air that flows in from the front side of the crossflow fan 3 is sucked in most. Therefore, the wind speed passing through the front lower heat exchanger 2c tends to be faster than the wind speed passing through the other heat exchangers 2b and 2a. For this reason, there exists a problem that heat exchange performance falls easily.

This problem will be described with reference to the drawings. FIG. 3 is a diagram showing the air flow when θ is 25 degrees. FIG. 4 is a view when θ is 95 degrees, and FIG. 5 is a view showing an air flow when θ is 60 degrees.
When the tongue center angle θ is set to less than 0.5α, the pressure loss on the front side of the crossflow fan 3 is reduced, and the amount of air flowing from the front lower heat exchanger 2c is increased as shown in FIG. As the wind speed increases, sufficient heat exchange capacity cannot be secured. Further, since the vortex 40 is generated so as to extend from the vicinity of the tongue portion 12 toward the discharge air passage 4a, the flow width of the air flowing through the cross flow fan 3 is reduced, and the blowing air speed is increased, so that noise is generated. It can also be a cause.
On the other hand, when the tongue center angle θ is set to 1.5α or more, the substantial suction area region 35 (the region indicated by the thick solid line in FIG. 4) of the cross flow fan 3 is reduced and the air blowing performance is lowered. Experimental results have shown that ability is also reduced.

  Therefore, by setting the tongue center angle θ in the above range, that is, 0.5α ≦ θ <1.05α, preferably 0.7α ≦ θ ≦ 0.98α, the front surface as shown in FIG. Since the amount of air flowing into the cross flow fan 3 from the lower heat exchanger 2c is reduced and the wind speed is effectively reduced, a sufficient heat exchange capability can be ensured. Further, since the vortex 40 is generated at a position closer to the tongue portion 12 so as to widen the through-flow width, the blowing wind speed is reduced and the noise is also reduced.

FIG. 6 (a) shows a ratio of heat exchange capacity to a conventional air conditioner (conventional machine) when the tongue center angle θ is changed. The solid line in the figure indicates the heat exchange capacity of the conventional machine as “1”, the vertical axis in the figure represents the ratio of the heat exchange capacity to the conventional machine, and the horizontal axis in the figure represents the central angle of the tongue. It shows the change of θ. Further, the tongue center angle θ in the conventional machine is 20 degrees to 25 degrees. The table of FIG. 6B shows the coordinate positions of the points A to J in FIG. 6A, and the points A, C to E, G, and J are actual experimental values, and the points B, F, H, and I are the coordinate positions of each point on the approximate curve 50 that passes through these experimental values.
From the graph of FIG. 6, the heat exchange capacity is higher than that of the conventional machine within the range of 0.45α <θ <1.07α, and in particular, the heat exchange capacity ratio is within the range of 0.5α ≦ θ <1.05α. It can be seen that the heat exchange capacity is 1.02 or more, and more preferably in the range of 0.7α ≦ θ ≦ 0.98α, the heat exchange capacity is improved by 1.1 times or more than the conventional machine.

  As described above, in the present embodiment, the tongue 12 has a tongue center angle θ satisfying the range of 0.45α <θ <1.07α, particularly 0.5α ≦ θ <1.05α. Is configured to extend along the rotation direction of the cross flow fan 3, the wind speed flowing into the front lower heat exchanger 2c can be effectively reduced, and sufficient heat exchange capability can be ensured. . Also, noise can be reduced. In addition, since no pressure loss body as in the prior art is required, the cost can be reduced.

Embodiment 2. FIG.
FIG. 7 is a cross-sectional view showing an air conditioner according to Embodiment 2 of the present invention.
In the air conditioner 10A according to the second embodiment, the refrigerant pipe 5 of the lower front heat exchanger 2c is configured with a smaller number than the other heat exchangers 2a and 2b in the depth direction of the air conditioner. That is, for example, the point that the number of rows of the refrigerant pipes 5 of the front lower heat exchanger 2c is reduced as compared with the other heat exchangers 2a and 2b is different from the first embodiment in that the air conditioner main body is made thinner. Other configurations are the same as those of the first embodiment.
Thus, when the air conditioner main body is thinned by reducing the number of refrigerant pipes 5 of the front lower heat exchanger 2c, that is, the number of rows, the wind speed distribution of the heat exchanger 2 has a low air resistance due to its configuration. In the front lower heat exchanger 2c, the wind speed is extremely unbalanced.

  For this reason, as shown in FIG. 2, the position of the tip 12a of the tongue 12 is such that the line 32 connecting the center O of the crossflow fan 3 and the tip 14a of the drain pan 14, and the center O of the crossflow fan 3 and the tongue. 12 is a line in which the tongue center angle θ, which is an angle formed with the line 31 connecting the tip 12a of the twelve, extends horizontally from the center O of the crossflow fan 3 toward the front lower heat exchanger 2c, The angle is 0.7α ≦ θ ≦ 0.98α, which is 70% or more of the angle α formed by the line 32 connecting the center O of the fan 3 and the tip 14 a of the drain pan 14. In addition, the position of the center O of the cross flow fan 3 is arranged at a substantially middle position of the height dimension L of the front lower heat exchanger 2c. Α is set in a range of 60 degrees to 70 degrees.

  Here, when the tongue center angle θ is set to be less than 0.7α, the pressure loss on the front side of the cross flow fan 3 is reduced, and the amount of air flowing from the front lower heat exchanger 2c as shown in FIG. As the wind speed increases, sufficient heat exchange capacity cannot be secured, and when it is set to 1.05α or more, as shown by the thick solid line in FIG. Experimental results have been obtained that the heat exchange capacity is also reduced due to the decrease in air flow and the air blowing performance. Therefore, when the wind speed of the heat exchanger 2 has an unbalanced distribution, by setting the tongue central angle θ to the range 0.7α ≦ θ ≦ 0.98α, the front lower heat exchanger as shown in FIG. Since the amount of air flowing in from 2c is reduced and the wind speed is effectively reduced, sufficient heat exchange capability can be ensured. Also, noise can be reduced.

  As described above, in the present embodiment, when the air speed of the heat exchanger 2 has an unbalanced distribution as the air conditioner body becomes thinner, the tongue center angle θ is 0.7α ≦ θ ≦. By configuring the tongue 12 to extend along the rotational direction of the crossflow fan 3 so as to satisfy the range of 0.98α, the wind speed flowing into the front lower heat exchanger 2c can be effectively reduced. Sufficient heat exchange capacity can be ensured. Also, noise can be reduced. In addition, since no pressure loss body as in the prior art is required, the cost can be reduced.

Embodiment 3 FIG.
FIG. 8 is a cross-sectional view showing an air conditioner according to Embodiment 3 of the present invention.
The air conditioner 10 </ b> B according to the third embodiment is provided with a suction port 6 only on the upper surface of the main body 1 made of a box-shaped casing, and in an inverted V shape upstream of the cross flow fan 3. The point which made the air conditioner main body thin by making the acute angle of the heat exchanger 2 arrange | positioned smaller was different from Embodiment 1 and Embodiment 2. FIG. In this example, the lower end of the front panel 11 disposed on the front surface is connected to the drain pan 14 and the front air inlet 7 shown in FIG. 1 is closed. Other configurations are the same as those of the second embodiment.

  In the air conditioner 10B of the present embodiment, the air suction port 7 on the front surface side is eliminated and only the air suction port 6 on the upper surface side of the main body 1 is used, and the heat exchanger 2 is the same as that of the front heat exchanger 2b. The air conditioner main body is made thin by making the angle of the inverted V-shaped portion with the rear heat exchanger 2a that is connected to the upper side and inclined rearward and lower than the configuration of the first and second embodiments. It has become. Therefore, the wind speed distribution of the heat exchanger 2 becomes an unbalanced distribution in which the wind speed is extremely high in the front lower heat exchanger 2c with a small pressure loss due to the thinning of the air conditioner body.

  For this reason, as shown in FIG. 2, the position of the tip 12a of the tongue 12 is such that the line 32 connecting the center O of the crossflow fan 3 and the tip 14a of the drain pan 14, and the center O of the crossflow fan 3 and the tongue. 12 is a line in which the tongue center angle θ, which is an angle formed with the line 31 connecting the tip 12a of the twelve, extends horizontally from the center O of the crossflow fan 3 toward the front lower heat exchanger 2c, The angle is 0.7α ≦ θ ≦ 0.98α, which is 70% or more of the angle α formed by the line 32 connecting the center O of the fan 3 and the tip 14 a of the drain pan 14. In addition, the position of the center O of the cross flow fan 3 is arranged at a substantially middle position of the height dimension L of the front lower heat exchanger 2c. Α is set in a range of 60 degrees to 70 degrees.

  Here, when the tongue center angle θ is set to be less than 0.7α, the pressure loss on the front side of the cross flow fan 3 is reduced, and the amount of air flowing from the front lower heat exchanger 2c as shown in FIG. As the wind speed increases, sufficient heat exchange capacity cannot be ensured, and when it is set to 1.05α or more, as shown by the thick solid line in FIG. Experimental results have been obtained that the heat exchange capacity is also reduced due to the decrease in air flow and the air blowing performance. Therefore, when the wind speed of the heat exchanger 2 has an unbalanced distribution, by setting the tongue central angle θ to the range 0.7α ≦ θ ≦ 0.98α, the front lower heat exchanger as shown in FIG. Since the amount of air flowing in from 2c is reduced and the wind speed is effectively reduced, sufficient heat exchange capability can be ensured.

  As described above, in the present embodiment, when the air speed of the heat exchanger 2 has an unbalanced distribution as the air conditioner body becomes thinner, the tongue center angle θ is set to 0.7α ≦ θ. By setting the tongue 12 to extend along the rotation direction of the cross flow fan 3 so as to satisfy the range of ≦ 0.98α, the wind speed flowing into the front lower heat exchanger 2c can be effectively reduced. And sufficient heat exchange capability can be secured. Also, noise can be reduced. In addition, since no pressure loss body as in the prior art is required, the cost can be reduced.

  In addition, although the reverse V-shaped heat exchanger 2 was demonstrated in the above Embodiments 1-3, the heat exchanger in this invention is not limited to this, For example, the heat exchanger 2a of the back side The heat exchangers 2b and 2c on the front side may be used.

  DESCRIPTION OF SYMBOLS 1 Main body, 2 Heat exchanger, 2a Rear heat exchanger, 2b Front heat exchanger, 2c Front lower heat exchanger, 3 Cross flow fan, 4 Air path, 4a Outlet air path, 5 Refrigerant piping, 6 Top air inlet , 7 Front air inlet, 8 Air outlet, 9 Filter, 10, 10A, 10B Air conditioner, 11 Front panel, 12 Tongue, 13 Rear guide, 14 Drain pan, 30 Cross flow fan 3 from center O to lower front A line extending horizontally toward the heat exchanger 2c, 31 a line connecting the center O of the cross flow fan 3 and the tip 12a of the tongue 12, and 32 connecting the center O of the cross flow fan 3 and the tip 14a of the drain pan 14 Line, 35 suction area, 40 vortex.

Claims (2)

A main body, an air passage provided to allow air to pass through the main body, a heat exchanger and a cross flow fan disposed in the air passage, a tongue and a rear guide provided around the cross flow fan, In an air conditioner equipped with
The front panel of the main body is configured vertically,
The main body is provided with an air suction port constituting the inlet of the air passage only on the upper surface,
The heat exchanger has a three- part heat exchanger including a front lower heat exchanger installed in parallel with the front panel, and is arranged in an inverted V shape upstream of the cross flow fan. And the number of rows of refrigerant piping of the front lower heat exchanger is less than the heat exchanger of the other two parts,
The tongue is extended along the rotational direction of the cross flow fan from the tip of a drain pan located below the front lower heat exchanger so that the wind speed flowing into the front lower heat exchanger is reduced. It is composed ,
The tongue central angle, which is an angle formed by a line connecting the center of the cross flow fan and the tip of the tongue, and a line connecting the center of the cross flow fan and the tip of the drain pan, is θ, and the cross flow fan When the angle formed by a line extending horizontally from the center of the front to the front lower heat exchanger and a line connecting the center of the cross flow fan and the tip of the drain pan is α, the θ is 0. An air conditioner having a range of 7α ≦ θ ≦ 0.98α . Wherein α is an air conditioner according to claim 1, wherein the 90 degrees or less than 60 degrees.

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