JPS5824099Y2 - indoor unit - Google Patents

Description

[Detailed Description of the Invention] The present invention relates to a low-noise indoor unit equipped with a heat exchanger and a cross-flow fan.

Conventionally, this type of indoor unit has only been made thinner in depth, but the height has been larger, which has caused problems such as the indoor unit protruding under the roof when installed on a wall, or the height of the indoor unit being too large. Because of the large size, there was a problem in that the space below the indoor unit became narrow, resulting in a decrease in space utilization efficiency.

Therefore, in order to eliminate this installation problem, in order to reduce the height dimension of the indoor unit without increasing the width dimension,
The only option is to reduce the height of the heat exchanger, but in this case, if the air volume is kept approximately the same, the air flow velocity within the heat exchanger increases in proportion to the decrease in the front surface area of the heat exchanger. By increasing the heat transfer coefficient on the air side of the heat exchanger, the heat exchange capacity of the heat exchanger is approximately the same as before.

However, as mentioned above, due to the increase in air flow velocity within the heat exchanger, the ventilation resistance of the heat exchanger increases extremely, and the required static pressure of the crossflow fan increases dramatically. There was a problem in that this caused the air volume to decrease and the noise to increase.

Furthermore, to explain the conventional problem with the embodiment shown in FIG. 2, in this embodiment, the conventional heat exchanger has a width dimension of 630 mm, a vertical heat exchange tube 4a having 10 stages,
A cross-in coil type heat exchanger having two rows of heat exchange tubes 4a in the front-rear direction and having an outer diameter of 90 mm and a length of 620 mm was used as the rotor 5 of the cross flow fan. The internal resistance of the indoor unit using
It is a constant curve ■ shown in the figure.

Further, as an example in which the height of the heat exchanger is lower than that of the conventional one, the number of stages of the conventional one is increased to six.

The internal resistance at this time is curve II in FIG.

In the conventional model, the static pressure per air volume is curve I in Figure 3.
II becomes the intersection point P with the in-flight resistance curve I, which means the air volume is 6.
．． It will be operated at a rate of 9 m3/min and a static pressure of 1.5 mmH2O.

However, if the number of stages of the heat exchanger is simply lowered to 6 as described above, the wind speed will increase, the ventilation resistance will increase, and the required static pressure will increase, so in the end, the air volume as shown by the dotted line in curve III in Figure 6 will increase. is operating in a small surging region,
Surging causes problems such as unstable operation, reduced efficiency, and increased noise.

Furthermore, the conventional problems that arise as described above will be explained with reference to the air flow diagram shown in FIG.

The air flow diagram in FIG. 9 is based on the conventional cross flow fan 20.
A heat exchanger 4 with a rotor 5 attached and a lowered height.
is installed and the in-flight resistance is greatly increased as shown by curve II in Figure 2.The center A of the vortex generated in the air streamline moves from a fixed position near the front plate 21 to the vortex part 2 on the rear plate 22.
2a is deviated to a position closer to the upper end B direction.

Incidentally, the above-mentioned fixed position means that the number of stages is 10, although not shown in the figure.
This refers to the center position of the vortex when a conventional multi-stage heat exchanger is used and the in-machine resistance is kept at a constant value as shown in curve II in Figure 2. Although not detailed, stable performance without surging can be obtained. .

That is, in the conventional sloch flow fan 20 with the heat exchanger 4 attached with a reduced height, the center A of the vortex is too close to the upper end B of the vortex part 22a, as shown in FIG. A backflow tends to occur from the gap with the upper end B to the upstream side of the rotor 5, which reduces efficiency and makes it susceptible to surging, increasing noise. Also, since the center A of the vortex is too far away from the front plate 21, the air flow is It is unstable, and moreover, there is a large amount of backflow from the gap between the rotor 5 and the front plate 21, resulting in a decrease in efficiency.

As a result of various studies to solve the above-mentioned problems, the present invention has been developed to reduce the heat exchange area by lowering the height of the heat exchanger compared to conventional products, while increasing the flow velocity of circulating air. In order to increase the flow velocity while maintaining a sufficiently large heat exchange capacity despite the reduction in the heat exchange area, internal resistance increases, surging is likely to occur, and noise becomes louder, making operation unstable and reducing efficiency. It has been discovered that the various problems associated with deterioration can be reliably resolved by specifying the length and angle values of each part of the ventilation passage within the main body casing.

In other words, even if the height of the heat exchanger is reduced, the present invention maintains sufficient thermal efficiency, does not cause surging, and can operate stably with low noise, high efficiency, and improved overall efficiency. This product provides an indoor linnit that can reduce the height dimension of the fan, does not take up much space, and can be easily installed.A cross-flow fan is installed inside the main body casing, which is connected to the rotor, front plate, and rear plate. Indoor air is sucked in from the suction port provided at the upper front of the main body casing,
In an indoor unit in which the indoor air is blown out from an air outlet provided at the lower front of the main body casing, heat is generated on the suction side of the cross flow fan between the suction port of the main body casing and the rotor of the cross flow fan. In addition to providing an exchanger, the front plate of the cross-flow fan is constituted by a flat plate part and a rising part provided at the tip of the flat plate part on the rotor side, while the rear plate of the cross-flow fan is formed of a rear plate of the rotor. a spiral portion formed in a spiral shape, a portion of the spiral portion from the tip of the air outlet side toward the air outlet as a flat plate portion formed in a flat plate shape, and a flat plate portion of the front plate and a portion of the rear plate. The flat plate portions are arranged so that the blowout passage between these flat plate portions widens toward the blowing direction, and the outer diameter of the rotor of the cross flow fan is D, and the center of the vortex rotor and the vortex of the rear plate are The angle of the line connecting both ends of the section is 01, the distance of the perpendicular line drawn from the center of the rotor to the upper surface of the flat plate section of the rear plate is Hl, the height of the rising part of the front plate is L, the rising part and the rotor, ε is the minimum gap between the rising portion and the flat plate portion of the rear plate, H2, and the angle between the lower surface of the flat plate of the front plate and the upper surface of the flat plate portion of the rear plate. When 02, each of these DI, θ1°Hl, L, ε, H2, θ
2, 120°〈θ1〈160°, 0.7<''<1.
0,0.2< , <0.3,0.08<H<0.1
1,0.34<O.

4.20°<θ2<50°.

Embodiments of the indoor unit of the present invention will be described below based on the drawings.

In FIG. 1, 1 is a main body casing, which is provided with an inlet 2 at the upper part and an outlet 3 at the lower front, and inside the main casing 1 is a cross-fin coil type heat exchanger 4 and a rotor 5. , a cross-flow fan 8 consisting of a front plate 6 and a rear plate 7 is disposed, and the heat exchanger 4 is connected to a refrigerant pipe that communicates with an outdoor unit (not shown), and functions as an evaporator during cooling. It also acts as a condenser during heating.

Therefore, the heat exchanger 4 is provided on the suction side of the crossflow fan 8 between the suction port 2 of the main body casing 1 and the rotor 5 of the crossflow fan 8.

In FIG. 1, the heat exchanger 4 is a conventional heat exchanger with a reduced number of stages, a detailed width dimension of 630 mm, and vertical heat exchange tubes 4a.
The number of stages of heat exchange tubes 4a is six, and the number of rows of heat exchange tubes 4a in the longitudinal direction is two.

Further, the cross flow fan 8 has a front plate 6 as a flat plate part 6.
a, and a rising portion 6b provided at the tip of the flat plate portion 6a on the rotor 5 side, and a spiral portion 7a formed in a spiral shape on the back side of the rotor 5 of the rear plate 7, The spiral part 7
A portion from the tip of the air outlet 3 side toward the air outlet 3 of a is formed into a flat plate shape to form a flat plate portion 7b, and the flat plate portion 6 of the front plate 6
a and the flat plate part 7b of the rear plate 7, these flat plate parts 6a,
The blowing passage between the holes 7b is arranged so as to widen toward the blowing direction.

As shown in FIG. 1, the rotor 5 of the cross flow fan 8 has an outer diameter of 9Q mm and a length of 620 m, similar to the conventional one.
This is because I used the one from m.

Then, the outer diameter of the rotor 5 of the cross flow fan 8 is D
(90 mm in FIG. 1), the angle formed by the line connecting the center of the rotor 5 and both ends of the spiral portion 7a of the rear plate 7 is θ1°, and the upper surface of the flat plate portion 7b of the rear plate 7 from the center of the rotor 5. Hl is the distance of the suise drawn down to the front plate 6, L is the height of the rising part 6b of the front plate 6, ε is the minimum gap between the rising part 6b and the rotor 5, and is the height of the rising part 6b of the front plate 6 and the rear plate 7. flat plate part 7b of
When the minimum gap between the two is represented by H2, and the angle between the lower surface of the flat plate portion 6b of the front plate 6 and the upper surface of the flat plate portion 7b of the rear plate 7 is represented by θ2, these θ1. He forced H1, L, H2, ε, and θ2 to be set as follows.

First, the setting range of the value of H0 is determined.

As a result of measuring the driving noise (hons) by changing the value of H, as shown in Figure 3, when the bone value was set to a value within the range of 0.7 to 1.0, the driving noise was below 42 phons. It was possible to suppress it.

That is, the value of H1 is set within the range of 0.7 to 1.0D.

That is, when the value of Hl is set within the above range, the center A of the vortex generated at the back of the lower part of the heat exchanger 4 is located at an appropriate position within a certain distance from the rising portion 6b as shown in FIG. This allows the air blown out from the rotor 5 to not flow back to the lower and upper inflow sides of the rotor 5, and the entire amount to the air outlet 3.
It can flow smoothly in all directions, is highly efficient, does not generate surging, and can reduce operating noise.

Incidentally, if the value of the preceding symbol is made larger than the above range, the center O of the vortex departs inward from the proper position, causing the backflow, resulting in a decrease in efficiency, frequent occurrence of surging, and increase in noise. If the value of the preceding symbol is made smaller than the above range, the ventilation resistance between the main body casing and the main body casing will increase and the noise will become louder.

Next, the setting range of the value of θ1 is determined.

As a result of measuring the operating noise by varying the angle θ1 with reference to the line connecting the center of the rotor 5 to the lower end of the spiral portion 7a, the value of θl ranged from 120° to 16° as shown in FIG.
When the value was within the range of 0°, the operating noise could be suppressed to 42 phons or less.

That is, the value of θ1 is set within the range of 120° to 160°.

That is, when θ1 is set to a value within the above range, the center A of the vortex as shown in FIG.
can be located at an appropriate position a certain distance inward from the rising portion 6b, and the air blown from the rotor 5 can smoothly flow in the direction of the three air outlet ports without causing a backflow effect.
It is highly efficient, does not generate surging, and can reduce operating noise.

Moreover, at the same time, it is possible to form an appropriate space on the upper rear side of the heat exchanger 4 that exhibits a good wind speed distribution without surging, and therefore it is possible to prevent noise from being generated in the space.

Incidentally, if the value of θ1 is made larger than the above range, the depth dimension of the space formed on the upper rear side of the heat exchanger 4 becomes too small, and the wind speed and therefore the ventilation resistance become excessive, resulting in an increase in noise. If the value of θ1 is made smaller than the above range, the upper end B of the spiral portion 7a will be too close to the center A of the vortex, and a backflow will occur from the gap between the upper end B of the spiral portion 7a and the rotor 5, resulting in a decrease in efficiency. This makes surging more likely to occur.

Also, find the setting range of the value of H2.

Using the flat plate part 7b as a reference, the front plate 6 was moved so that the rising part 6b moved away from or came close to each other without changing the angle θ2, thereby changing the value of H2 and, in turn, measuring the driving sound. As a result, the operating noise could be suppressed to 42 phon or less when the value of silicon was set within the range of 0.3 to 0.4 as shown in FIG.

That is, the value of H2 is set within the range of 0.3D to 0.4D.

That is, if the value of H2 is set to a value within the above range, the center A of the vortex as shown in FIG.
can be located at an appropriate position inside the rising portion 6b, and the air blown from the rotor 5 can flow smoothly in the direction of the air outlet 3 without causing a backflow effect, thereby reducing operating noise.

However, if the value of H1 is too large, the distance between the rising portion 6b and the rotor 5 will become large, causing backflow and surging. If it is too small, ventilation resistance will increase and noise will increase. be.

Furthermore, the setting ranges of the values of ε and L are determined.

As a result of measuring the driving noise by changing the value of 5 using the above as a parameter, we found that the value of 0.2 to 0.3 for JB in Figure 6 and 0.08 to 0.11 for the paternal side. When the value was within the range of , the operating noise could be suppressed to 42 phon or less.

That is, the above values are set within the range of 0.2D to 0.3D, and the value of ε is set within the range of 0.08D to 0.11D.

That is, by setting the values of ε and soil within the respective ranges, it is possible to reduce the interference sound between the blade 5a of the rotor 5 and the rising portion 6b, that is, the so-called hini sound.

Incidentally, if the value of ε is made too small, the noise due to the whistling sound will increase significantly, and if the value of ε is made too large, a backflow from the interval ε will occur.

Also, find the setting range of the value of θ2.

As a result of measuring the operating noise by changing the value of θ2 by changing the inclination angle of the flat plate portion 6a around the lower end of the rising portion 6b, the value of θ2 was changed to 20 as shown in FIG.
When the value was within the range of 50° to 50°, the operating noise could be suppressed to 42 phon or less.

That is, the value of θ2 is set within the range of 20° to 50°.

That is, the flat plate portion 6a is positioned at the center A of the vortex as shown in FIG.
The blown air is tilted along the streamline of the blown air, which corresponds to the position of the blown air.
This allows for smooth flow between a and 7b, making it possible to sufficiently reduce noise.

As described above, each θ of the ventilation passage in the main body casing 1
1. By specifying the values of H1, L, H2, ε, and θ2, the center A of the vortex is located at a certain position near the rising portion 6b, as shown in FIG. Since there is no backflow from the gap between the vortex and the vortex, the air flow is stable and the efficiency can be increased, and the center A of the vortex is located at a sufficient distance from the upper end B of the vortex part 7a. There is no backflow in the gap between the rotor 5 and the upper end B, which makes it possible to further increase the efficiency.
mH20), it is resistant to surging and can sufficiently reduce overall noise.

In the above description, the diameter of the rotor 5 was set to 9Qmm, but it is not limited to this value and can be applied to any diameter.

Furthermore, in the above explanation, the heat exchanger 4 is constructed by disposing heat exchange tubes 4a in six stages and in two rows on a large number of plate fins. , it goes without saying that it can be applied to anything.

Further, it is preferable that the front plate 6 is formed to have a flat plate part 6a and a rising part 6b to serve as a drain pan provided below the heat exchanger 4, as shown in FIG. 1, so that the structure can be simplified.

As described above, according to the present invention, even if the heat exchange area is reduced by lowering only the height of the heat exchanger, sufficient heat exchange capacity can be achieved by increasing the flow velocity of air flowing through the heat exchanger. However, by specifying the length and angle of each part of the air passage in the main body casing, in response to the increased internal resistance due to increasing the flow velocity, the vortex can be reduced as shown in Figure 8. The center A of the front plate can be located at an appropriate position near the rising part of the front plate, so there is no backflow, the air flow is stable and highly efficient, and it is resistant to surging and reduces overall noise.

Therefore, the external dimensions of the entire unit can be reduced while maintaining its thinness, and when installed on a wall, it does not protrude under the roof, making it possible to increase the space utilization rate below the unit.

[Brief explanation of the drawing]

FIG. 1 is a cross-sectional explanatory diagram showing an embodiment of the present invention, FIG. 2 is an explanatory diagram showing the relationship between air volume and static pressure, and FIGS. 3 to 7 are each dimension H1, θ1. FIG. 8 is an air flow diagram, and FIG. 9 is an explanatory diagram showing the relationship between H2, ε+L +θ2 and operating noise. 1...Body casing, 2...Suction port, 3...Blowout port, 4...Heat exchanger, 5
...Rotor, 6...Front plate, 6a...
...Flat plate part, 6b... Rising part, 7...
... Rear plate, 7a ... Spiral section, 7b ...
Flat plate part, 8...Cross flow fan.

Claims (1)

[Claims for Utility Model Registration] A crossflow fan consisting of a rotor, a front plate, and a rear plate is disposed inside the main casing, and indoor air is sucked in from the suction port provided at the upper front of the main casing. In an indoor unit in which the indoor air is blown out from an outlet provided at a lower front surface, a heat exchanger is provided on the suction side of the cross-flow fan between the suction port of the main body casing and the rotor of the cross-flow fan. In addition, the front plate of the cross flow fan is a flat plate part,
On the other hand, the back plate of the cross flow fan has a spiral portion formed in a spiral shape on the back side of the rotor, and a spiral portion on the blower outlet side of the spiral portion. The part from the tip toward the air outlet is formed into a flat plate part, and the flat plate part of the front plate and the flat plate part of the rear plate are formed so that the air outlet passage between these flat plate parts widens toward the blowing direction. The outer diameter of the rotor of the cross-flow fan is D, the angle of the line connecting the center of the rotor and both ends of the spiral portion of the rear plate is 01, and the angle from the center of the rotor to the The distance of the perpendicular line drawn to the top surface of the flat plate part of the rear plate is Hl,
The height of the rising part of the front plate is L, the minimum gap between the rising part and the rotor is ε, the minimum gap between the rising part and the flat plate part of the rear plate is H2, and the minimum gap between the rising part and the rotor is H2. When the angle between the lower surface of the flat plate and the upper surface of the flat plate portion of the rear plate is θ2, each of these D1. θ1. H1, L, ε, H2, θ2, 120
° θ1<160', O. Rei 7 < D < 1.0, 0.2 < j < 0.3, 0.08
<10,000<0.11,0゜3〈All<0.4,20°〈θ2〈
An indoor unit characterized by having a value within a range that satisfies each equation of 50°.