WO2015098657A1 - Indoor air conditioner - Google Patents

Abstract

In order to combine surge bearing capacity and energy conservation, a stabilizer (17), a rear guider (18), and a cross-flow fan (30) are disposed in this wall-mounted indoor air conditioner so as to satisfy 3 formulas: (θa-θ0) > 16°; 17° < (θb-θ0) < 26°; and θb ≥ θa. Therein, a reference angle (θ0) is formed between a fan horizontal reference line (L1) and a scroll reference line (L2), a first angle (θa) is formed between a first straight line (SL1), which links a front-side closest point (P7) of the stabilizer (17) with a fan center point (O), and the fan horizontal reference line (L1), and a second angle (θb) is formed between a second straight line (SL2), which links a rear-side closest point (P8) of the rear guider (18) with the fan center point (O), and the fan horizontal reference line (L1).

Description

Air conditioning indoor unit

The present invention relates to an air conditioning indoor unit, and more particularly to a wall-mounted air conditioning indoor unit.

Conventionally, an indoor unit of an air conditioner (hereinafter referred to as an air conditioning indoor unit) that is installed on a side wall of a room instead of a ceiling, sucks air from the front or upper surface, and blows out air after air conditioning from a lower outlet. It is popular. Inside the indoor unit, a heat exchanger responsible for heat exchange between the refrigerant and air and a cross flow fan are accommodated.

For example, as shown in Patent Document 1 (Japanese Patent Laid-Open No. 2008-8500), an air conditioning indoor unit has a stabilizer and a rear guider as members constituting the air passage.

Recent air conditioner indoor units have a tendency of low rotation and high air flow with the increase in diameter of the cross flow fan. And while it is required to improve the surging proof strength, which has been reduced by the low rotation, even when the static pressure is increased, there is also a demand for low power from the viewpoint of energy saving.

An object of the present invention is to provide an air conditioning indoor unit having both surging resistance and energy saving performance.

An air conditioning indoor unit according to a first aspect of the present invention is a wall-hanging air conditioning indoor unit, and includes a crossflow fan, a casing, and a heat exchanger. In the cross flow fan, a plurality of blades are arranged along a circumference to generate an air flow. The casing includes a front-side stabilizer and a rear-side rear guider. By these stabilizers and the rear guider, the casing forms an air flow passage for scroll-like air flowing from the cross flow fan to the air outlet. The stabilizer is divided into an upper part and a lower part across the tongue. The heat exchanger includes a front-side heat exchange unit and a back-side heat exchange unit, and is disposed on the upstream side of the air flow of the cross flow fan. In the longitudinal sectional view of the air conditioning indoor unit, a horizontal line passing through the fan center point that is the rotation center of the cross flow fan is defined as a fan reference horizontal line. Also, in the vertical cross-sectional view, the straight line with the smallest angle formed with the fan reference horizontal line is the tangent line of the circle connecting the outer ends of the blades of the cross flow fan and the lower part of the stabilizer. A line. In addition, an angle formed by the fan reference horizontal line and the scroll reference line in the longitudinal sectional view is defined as a reference angle θ0. In addition, in the longitudinal sectional view, a first straight line that is a straight line connecting the front closest point that is the point closest to the cross flow fan in the upper part of the stabilizer and the fan center point, and the fan reference horizontal line are formed. The angle is a first angle θa. In addition, in the longitudinal sectional view, the angle formed by the second straight line that connects the rear side closest approach point that is the closest point to the cross flow fan in the rear guider and the fan center point and the fan reference horizontal line is The second angle θb. The air conditioning indoor unit is set so that the reference angle θ0, the first angle θa, and the second angle θb defined as described above satisfy the following first angle relational expression, second angle relational expression, and third angle relational expression. Then, a stabilizer, a rear guider, and a cross flow fan are arranged.
First angle relation: (θa−θ0)> 16 °
Second angle relational expression: 17 ° <(θb−θ0) <26 °
Third angle relational expression: θb ≧ θa
The air conditioning indoor unit according to the present invention does not satisfy any of the first angle relational expression, the second angle relational expression, and the third angle relational expression, but the first angle relational expression, the second angle relational expression, and the third angle relational expression. Stabilizer, rear guider and cross flow fan are arranged to satisfy all the angle relational expressions. As a result, the height position of the closest point on the front side of the stabilizer is kept low, so that the flow of air flowing from the lower part of the front side heat exchange section to the cross flow fan is reduced, and so-called fans The suction angle can also be increased within a range of 180 ° or less. For this reason, the flow of air with low loss is born, and the flow of air from the cross flow fan toward the outlet is prevented from flowing back to the suction port. The suppression of the reverse flow improves the surging strength.

Furthermore, by keeping the height position of the rear closest approach point of the rear guider within an appropriate range, an increase in fan power caused by making the rear guideer too low is suppressed, and energy saving is improved. That is, if the height position of the rear closest approach point of the rear guider is made too low, the scroll-like air blowing air flow path becomes shorter, and the holding force of the circulating vortex generated on the cross flow fan side of the rear closest approach point However, the turbulent flow on the surface of the scroll-like blown air flow path increases and the fan power increases, but according to the present invention, such an increase in fan power is suppressed.

The air conditioning indoor unit according to the second aspect of the present invention is the air conditioning indoor unit according to the first aspect, and in the longitudinal sectional view, the lower part of the front side heat exchange part is located below the fan reference horizontal line, The lower part of the back side heat exchange part is located above the fan reference horizontal line. And in the longitudinal sectional view of the air conditioning indoor unit, the straight line having the largest angle with the fan reference horizontal line among the straight lines passing through the lower part of the front side heat exchange section and the fan center point is defined as the third straight line. The angle formed by the fan reference horizontal line is defined as the third angle θc, and the straight line having the smallest angle formed by the fan reference horizontal line among the straight lines passing through the lower portion of the rear heat exchange section and the fan center point is defined as the fourth straight line. When the angle formed by the straight line and the fan reference horizontal line is the fourth angle θd, the stabilizer, the rear guider, the heat exchanger, and the cross flow fan are arranged so as to satisfy the following fourth angle relational expression and fifth angle relational expression Has been.
Fourth angle relational expression: θc> θa
Fifth angle relational expression: θd <θb
In the air conditioning indoor unit according to the second aspect, the lower part of the front side heat exchange unit is arranged at a low position so that the fourth angle relational expression is satisfied, and the rear side heat exchange part is satisfied so that the fifth angle relational expression is satisfied. The lower part is arranged at a low position, and the capacity of the heat exchanger can be increased. And since the 1st angle relational expression, the 2nd angle relational expression, and the 3rd angle relational expression are satisfied simultaneously, even if the lower part of the front side heat exchange part and the back side heat exchange part is arranged in a low position, there The flow of air flowing from the fan to the cross flow fan is hardly obstructed, and a large amount of air also flows under the heat exchange parts, improving energy saving performance.

In the air conditioning indoor unit according to the first aspect of the present invention, both the surging proof strength and the energy saving performance are improved.

In the air-conditioning indoor unit according to the second aspect of the present invention, the capacity of the heat exchanger increases, but a large amount of air flows through the lower part of each heat exchanging portion, further improving energy saving.

The block diagram of the air conditioning apparatus which consists of an air-conditioning outdoor unit and an air-conditioning indoor unit. The longitudinal cross-sectional view of the air-conditioning indoor unit for demonstrating arrangement | positioning of a front panel, a filter, and a heat exchanger (cross-sectional view of the II-II arrow of FIG. 1). The longitudinal cross-sectional view of the air-conditioning indoor unit for demonstrating arrangement | positioning of a stabilizer and a rear guider. The graph which shows the relationship between arrangement | positioning of a stabilizer and the efficiency improvement of fan motive power. The graph which shows the relationship between arrangement | positioning of a rear guider and the fan power efficiency improvement.

Hereinafter, an air conditioning indoor unit 92 according to an embodiment of the present invention will be described with reference to the drawings. The following embodiments are specific examples of the present invention and do not limit the technical scope of the present invention.

(1) Configuration of Air Conditioning Indoor Unit FIG. 1 is a configuration diagram of an air conditioner 90 including an air conditioning indoor unit 92 according to an embodiment of the present invention. The air conditioning indoor unit 92 is a wall-mounted indoor unit that is attached to a wall surface in the room. The air conditioner indoor unit 92 is connected to the air conditioner outdoor unit 91 arranged outside the room via a refrigerant pipe 93 to constitute an air conditioner 90. The air conditioning indoor unit 92 performs indoor cooling operation and heating operation in accordance with an operation by a remote controller or the like.

As shown in FIG. 2, the air conditioning indoor unit 92 mainly includes a casing 10, a filter 40, a heat exchanger 20, and a cross flow fan 30.

(1-1) Casing The casing 10 is an assembly of members that form an outer frame and a frame of the air conditioning indoor unit 92, and supports and accommodates the filter 40, the heat exchanger 20, the cross flow fan 30, and the like.

In the upper part of the casing 10, a suction port 10a for taking in indoor air is formed. At the lower part of the casing 10, an air outlet 10b for sending air after air conditioning into the room is formed. The suction port 10 a is at a position higher than the fan center point 0 that is the rotation center of the cross flow fan 30. More specifically, the suction port 10 a is formed on the top surface (upper surface) of the casing 10 and sucks room air from the space above the air conditioning indoor unit 92. The blower outlet 10b is at a position lower than the fan center point O. In more detail, the blower outlet 10b is formed in the front side part of the bottom face of the casing 10, and blows off air to the front and the lower side of the air conditioning indoor unit 92.

Casing 10 includes a front panel 15, a stabilizer 17, a rear guider 18, and the like shown in FIGS. By means of the stabilizer 17 and the rear guider 18, a scroll-like air blowing air passage 10 c that flows from the cross flow fan 30 to the air outlet 10 b is formed in the casing 10. The stabilizer 17 disposed on the front side of the rear guider 18 is divided into an upper portion 72 and a lower portion 73 with a tongue portion 71 formed of a curved surface interposed therebetween. As shown in FIG. 3, which is a longitudinal sectional view, the stabilizer 17 is closest to the cross flow fan 30 at the front side closest approach point P <b> 7 of the upper portion 72. The upper part of the rear guider 18 is located at a position higher than the fan center point O, and is closest to the cross flow fan 30 at the rear side closest approach point P8. The front panel 15 is disposed on the front side of the filter 40.

(1-2) Heat Exchanger and Filter The heat exchanger 20 is a fin-and-tube heat exchanger having an inverted V shape in a longitudinal sectional view, and flows from the suction port 10a side to the cross flow fan 30 side. Heat exchange is performed between the air and the refrigerant flowing through the tube. The heat exchanger 20 includes a large number of aluminum heat transfer fins and a large number of tubes penetrating a large number of holes formed in the heat transfer fins. The tube which is a copper heat transfer tube has an outer diameter of 5 mm or 4 mm.

Moreover, the heat exchanger 20 includes a front-side heat exchange unit 21 located on the front side of the top part 20a and a back-side heat exchange unit 22 located on the back side of the top part 20a. A lower portion 21a of the front-side heat exchange unit 21 is located below a fan reference horizontal line L1, which will be described later, and a lower part 22a of the back-side heat exchange unit 22 is located above the fan reference horizontal line L1.

The heat exchanger 20 located on the upstream side of the airflow of the crossflow fan 30, specifically, above and in front of the crossflow fan 30 is covered with a filter 40. The filter 40 disposed on the upstream side of the air flow of the heat exchanger 20 is located above and in front of the heat exchanger 20 and collects dust contained in the air flowing from the suction port 10a to the heat exchanger 20.

(1-3) Cross Flow Fan The cross flow fan 30 includes a cylindrical fan rotor that extends long in the horizontal direction and a motor that rotates the fan rotor. The fan rotor has a large number of fan blades 31 arranged along the circumference, and generates an air flow that flows from the heat exchanger 20 side to the outlet 10b side by rotating.

When the crossflow fan 30 rotates, air flows from the room to the heat exchanger 20 through the suction port 10a and the filter 40, and the air that has passed through the heat exchanger 20 flows to the blown air flow path 10c to blow out the air outlet 10b. Is blown out into the room.

Note that the rotational speed of the motor of the cross flow fan 30 is changed by a control device (not shown). The control device built in the air conditioning indoor unit 92 changes the number of rotations of the motor based on a user operation input from a remote controller or the like.

(2) Details of Arrangement of Front Panel, Filter, and Heat Exchanger In the air conditioning indoor unit 92 according to the present invention, new arrangements of respective parts not used in the conventional air conditioning indoor unit are adopted. Hereinafter, the arrangement of the front panel, the filter, and the heat exchanger will be described in detail.

As shown in FIG. 2, the lower part 21 a of the front heat exchange unit 21 and the lower part 40 a of the filter 40 are located below the fan center point O in the longitudinal sectional view of the air conditioning indoor unit 92. In other words, the front-side heat exchanging part 21 includes a lower part 21a located below the fan center point O, and the filter 40 includes a lower part 40a located below the fan center point O.

Here, the lines L1, SL3, SL5, the angles θc, θe, and the gap distances D1, D2, D3 are defined as follows.

The fan reference horizontal line L1 is a horizontal line passing through the fan center point O.

The third straight line SL3 is a straight line having the largest angle with the fan reference horizontal line L1 among straight lines passing through the lower portion 21a of the front-side heat exchange unit 21 and the fan center point O.

The heat exchanger lower angle θc is an angle formed by the third straight line SL3 and the fan reference horizontal line L1.

The fifth straight line SL5 is a straight line having the largest angle with the fan reference horizontal line L1 among straight lines passing through the lower portion 40a of the filter 40 and the fan center point O.

The filter lower angle θe is an angle formed by the fifth straight line SL5 and the fan reference horizontal line L1.

The first distance D1 is a gap distance between the cross flow fan 30 and the front side heat exchange unit 21 at the height position of the fan center point O.

The second distance D2 is a gap distance between the front heat exchange section 21 and the filter 40 at the height position of the fan center point O.

The third distance D3 is a gap distance between the filter 40 and the front panel 15 at the height position of the fan center point O.

The air-conditioned room so that the lines L1, SL3, SL5, the angles θc, θe and the gap distances D1, D2, D3 defined as described above satisfy the following first, second, and third expressions: In the machine 92, the cross flow fan 30, the heat exchanger 20, the filter 40, and the front panel 15 are disposed.

First formula: θe> (θc × 0.4)
Second formula: D3>D2> D1
Third formula: D1> (0.3 × R)
Note that the fan radius R, which is the radius of the fan rotor of the cross flow fan 30, is a virtual circle (a circle indicated by a dotted line in FIG. 2) connecting the outer ends of a large number of fan blades 31 from the fan center point O in a longitudinal sectional view. 30a)).

Satisfying these equations allows sufficient air to pass through the lower portion 21a of the front-side heat exchange unit 21 while suppressing the depth dimension of the air-conditioning indoor unit 92. The numerical value is adopted.

Heat exchanger lower angle θc = 52 °
Filter lower angle θe = 23 °> (θc × 0.4)
Fan radius R = 52mm
First distance D1 = 16 mm> (0.3 × R)
Second distance D2 = 22 mm> D1
Third distance D3 = 27 mm> D2
Further, in the air conditioning indoor unit 92, the fourth distance D4 that is the distance between the fan center point O and the front panel 15 at the height position of the fan center point O in the longitudinal sectional view is less than three times the fan radius R. It is suppressed to. That is, the fourth distance D4 and the fan radius R satisfy the following fourth expression.

Fourth formula: D4 <(3 × R)
Specifically, the front panel 15 is disposed relative to the cross flow fan 30 so that the fourth distance D4 is 143 mm. Although the fourth distance D4 is kept small so that the depth dimension of the air conditioning indoor unit 92 does not become too large, the cross flow fan 30, the heat exchanger 20, By disposing the filter 40 and the front panel 15, a sufficient amount of air sucked from the suction port 10 a formed on the top surface is sent to the lower portion 21 a of the front-side heat exchange unit 21. .

(3) Details of Arrangement of Stabilizer and Rear Guider Next, a new arrangement of the stabilizer 17 and the rear guider 18 that was not included in the conventional air conditioning indoor unit will be described in detail.

As shown in FIG. 3, in the longitudinal sectional view of the air conditioning indoor unit 92, the lines L2, SL1, SL2, and SL4 and the angles θ0, θa, θb, θc, and θd are defined as follows. The fan reference horizontal line L1 and the third straight line SL3 are as described above.

The scroll reference line L2 is the tangent of a circle 30a connecting the outer ends of the plurality of fan blades 31 of the crossflow fan 30 and the angle formed with the fan reference horizontal line L1 is the most straight line in contact with the lower portion 73 of the stabilizer 17. A small straight line. Here, since the lower part 73 of the stabilizer 17 which becomes the upper wall of the blowout air flow path 10c near the blower outlet 10b is a plane, and the straight line extended from the plane to the back side contacts the circle 30a in the longitudinal sectional view, The straight line is the scroll reference line L2.

The reference angle θ0 is an angle formed by the fan reference horizontal line L1 and the scroll reference line L2.

The first straight line SL1 is a straight line connecting the front closest point P7, which is the point closest to the cross flow fan 30 in the upper portion 72 of the stabilizer 17, and the fan center point O.

The first angle θa is an angle formed by the first straight line SL1 and the fan reference horizontal line L1.

The second straight line SL2 is a straight line connecting the rear side closest approach point P8, which is the point closest to the cross flow fan 30 in the rear guider 18, and the fan center point O.

The second angle θb is an angle formed by the second straight line SL2 and the fan reference horizontal line L1.

The third angle θc is the above-described heat exchanger lower angle θc, and is an angle formed by the third straight line SL3 and the fan reference horizontal line L1.

The fourth straight line SL4 is a straight line having the smallest angle with respect to the fan reference horizontal line L1 among straight lines passing through the lower portion 22a of the back side heat exchanger 22 and the fan center point O.

The fourth angle θd is an angle formed by the fourth straight line SL4 and the fan reference horizontal line L1.

The lines L2, SL1, SL2, SL4 and the angles θ0, θa, θb, θc, θd defined as described above satisfy all the following first to fifth angle relational expressions. In the machine 92, the stabilizer 17, the rear guider 18, the heat exchanger 20, and the crossflow fan 30 are arranged.

First angle relation: (θa−θ0)> 16 °
Second angle relational expression: 17 ° <(θb−θ0) <26 °
Third angle relational expression: θb ≧ θa
Fourth angle relational expression: θc> θa
Fifth angle relational expression: θd <θb
By satisfying these equations, the surging proof strength is improved as will be described later, and the increase in fan power is suppressed, but the air conditioning indoor unit 92 adopts the following numerical values that satisfy them.

Reference angle θ0 = 28 °
First angle θa = 48 °
Second angle θb = 51 °
Third angle θc = 52 °
Fourth angle θd = 31 °
(4) Features (4-1)
In the air conditioning indoor unit 92 according to the present embodiment, the first angle relational expression, the second angle relational expression is not satisfied, but the first angle relational expression, the second angle relational expression, and the third angle relational expression are not satisfied. The stabilizer 17, the rear guider 18, and the cross flow fan 30 are arranged so as to satisfy both the equation and the third angle relational equation.

Since this arrangement is adopted, the height position of the front-side closest point P7 of the stabilizer 17 is kept low, and the flow of air flowing from the lower portion 21a of the front-side heat exchange unit 21 to the cross flow fan 30 is hindered. Things are getting smaller. That is, a low-loss air flow is generated from the lower portion 21 a of the front heat exchange unit 21 to the cross flow fan 30. FIG. 4 shows data on which the first angle relational expression is based. In the graph of FIG. 4, the horizontal axis is the angle difference (θa−θ0), and the vertical axis is the efficiency improvement that is the ratio of the fan power that is the load on the motor of the crossflow fan 30 to a certain reference value. Amount. As a result of the test, when the angle difference (θa−θ0) is less than 16 °, the efficiency improvement amount is small, and when it exceeds 16 °, the efficiency improvement amount is large. When the angle difference (θa−θ0) is 17 °, 20 °, 24 °, or 28 °, the efficiency improvement amount is large and the increase in fan power is suppressed.

Further, the arrangement adopted by the air conditioning indoor unit 92 can increase the so-called fan suction angle (the angle on the suction port 10a side formed by the first straight line SL1 and the second straight line SL2) within a range of 180 ° or less. ing. Here, the fan suction angle is
180 ° -θb + θa = 177 °
Thus, the flow of air from the cross flow fan 30 toward the air outlet 10b is prevented from flowing backward to the inlet 10a. That is, the surging strength is improved in the air conditioning indoor unit 92. Many conventional air-conditioning indoor units have a fan suction angle of about 170 °.

Furthermore, in the air conditioning indoor unit 92, by keeping the height position of the rear closest approach point P8 of the rear guider 18 within an appropriate range, an increase in fan power caused by making the rear guider 18 too low is suppressed, and energy saving is achieved. Has improved. That is, if the height position of the rear side closest approach point P8 of the rear guider 18 is set too low, the scroll-like air blowing air flow path 10c is shortened, and is generated on the cross flow fan 30 side of the rear side closest approach point P8. Although the holding power of the circulating vortex is weakened, the turbulent flow on the surface of the scroll-like blown air flow path 10c is increased and the fan power is increased, but according to the arrangement of the rear guider 18 and the cross flow fan 30 described above, Such an increase in fan power is suppressed. FIG. 5 shows data on which the second angle relational expression is based. In the graph of FIG. 5, the horizontal axis is the angle difference (θb−θ0), and the vertical axis is the same efficiency improvement amount as in FIG. As a result of the test, when the angle difference (θb−θ0) is less than 17 ° or exceeds 26 °, the efficiency improvement amount is small, and when the angle difference is in the range of 17 ° to 26 °, the efficiency improvement amount is large. When the angle difference (θb−θ0) is 18 °, 22 °, or 25 °, the efficiency improvement amount is large, and the increase in fan power is suppressed.

As described above, in the air conditioning indoor unit 92 according to the present embodiment, the stabilizer 17, the rear guider 18, and the cross flow fan 30 are set so as to satisfy all of the first angle relational expression, the second angle relational expression, and the third angle relational expression. By arranging, the surging proof stress is improved and the increase in fan power is suppressed.

(4-2)
In the air conditioning indoor unit 92, the lower portion 21a of the front-side heat exchange unit 21 is disposed at a low position so that the fourth angle relational expression is satisfied, and the lower part of the rear-side heat exchange unit 22 is satisfied so that the fifth angle relational expression is satisfied. Since 22a is arrange | positioned in the low position, the capacity | capacitance of the heat exchanger 20 is large. In particular, since the third angle θc is set to 45 ° or more and the air conditioning indoor unit 92 adopts a structure in which the lower portion 21a of the front side heat exchanging portion 21 is extended downward, the capacity of the heat exchanger 20 larger than the conventional one is increased. It is secured. When such a large heat exchanger 20 is mounted, a partial bias occurs in the distribution of air flow through the heat exchanger, and the air flow is obstructed and the fan power tends to increase. Since the air conditioner indoor unit 92 adopts a component arrangement that satisfies all of the first angle relational expression, the second angle relational expression, and the third angle relational expression as described above, the air conditioner indoor unit 92 is crossed from the lower portions 21a and 22a of the heat exchanger 20. The flow of air flowing to the flow fan 30 is not easily obstructed, and a large amount of air also flows through the lower portions 21a and 22a of the heat exchange units 21 and 22. That is, the energy saving performance of the air conditioning indoor unit 92 is improved.

(4-3)
The air conditioning indoor unit 92 employs a structure for sucking indoor air from a suction port 10a formed on the top surface of the casing 10 located higher than the fan center point O, and a lower portion 21a of the front side heat exchange unit 21 is also used. The lower part 40a of the filter 40 also has a structure located below the fan center point O. For this reason, when the conventional design method is followed, the amount of air passing through the lower portion 21a of the front-side heat exchange unit 21 is reduced, and the entire heat exchanger 20 cannot be effectively used.

Therefore, in the air conditioning indoor unit 92, first, the lower portion 40a of the filter 40 is extended downward to a position lower than the conventional one so as to satisfy the above-described first formula, and the air passes through the lower portion 40a of the filter 40 and the front side heat exchange unit. The flow path toward the lower part 21a of 21 is secured.

Further, in the air conditioning indoor unit 92, the cross flow fan 30, the heat exchanger 20, the filter 40, and the front panel 15 are arranged so that the three gap distances D1, D2, and D3 satisfy the above-mentioned second formula, While suppressing the depth dimension of the machine 92, it passes from the suction port 10a to the lower part 40a of the filter 40 and the lower part 21a of the front side heat exchange part 21 through the gap (gap distance is the third distance D3) between the filter 40 and the front panel 15. The pressure loss of the flowing air flow path is reduced. Thereby, the quantity of the air which passes the lower part 21a of the front side heat exchange part 21 is fully ensured, and the structure where the whole heat exchanger 20 is utilized effectively is implement | achieved.

By adopting the arrangement as described above, in the air conditioning indoor unit 92, the gap distance (first distance D1) between the heat exchanger 20 and the cross flow fan 30 is not reduced too much, and the lower portion 21a of the front side heat exchange unit 21 is set. The width of the air flow path to can be expanded, and the frictional resistance (pressure loss) can be suppressed. In addition, since the second distance D2 is made larger than the first distance D1, the third distance D3 is made larger than the second distance D2, and a wider width is ensured in the flow path away from the cross flow fan 30, As shown in FIG. 2, there is no space in which the width becomes narrow in the middle from the suction port 10a to the lower portion 21a of the front side heat exchange section 21, and the fluid friction resistance is greatly reduced as compared with the conventional structure.

(4-4)
In the air conditioning indoor unit 92, the arrangement of each component that satisfies the second formula is adopted in order to suppress the depth dimension (the dimension in the left-right direction in FIG. 2). When the distance between the heat exchange unit 21 and the cross flow fan 30 becomes too close, noise may occur when the air passes through the front heat exchange unit 21. In particular, the air-conditioning indoor unit 92 that employs the fin-and-tube heat exchanger 20 and has a small outer diameter of the tube (5 mm or 4 mm) is more susceptible to the periodic speed fluctuations represented by Karman vortices. There is a high possibility that high-frequency turbulent fluctuations occur, and discrete frequency noise at high frequencies is caused by interaction with periodic pressure fluctuations of the fan blades 31.

In order to suppress this noise, the air conditioner indoor unit 92 employs an arrangement of components that satisfies the above-described third formula. That is, by setting the first distance D1, which is the gap distance between the cross flow fan 30 and the front heat exchange portion 21 at the height position of the fan center point O, to a size exceeding 30% of the fan radius R, Noise is within an acceptable range. If the size of the first distance D1 of the air conditioning indoor unit 92 is secured, the air flow after passing through the heat exchanger 20 is changed to a broadband turbulent structure having no periodicity and then collided with the fan blade 31. The periodic noise due to the interaction with the fan blade 31 can be reduced.

(4-5)
In the air conditioning indoor unit 92, the front panel 15 is disposed so as to satisfy the above-described fourth formula, and the distance from the fan center point O to the front panel 15 (fourth distance D4) is relatively small. As a result, a thin air-conditioning indoor unit 92 with a reduced depth dimension is realized. However, since the structure satisfies the first to third formulas at the same time, the entire heat exchanger 20 can be used even if it is thin. It can be used effectively.

DESCRIPTION OF SYMBOLS 10 Casing 10b Outlet 10c Outlet air flow path 17 Stabilizer 18 Rear guider 20 Heat exchanger 21 Front side heat exchange part 21a Lower part of front side heat exchange part 22 Rear side heat exchange part 22a Lower part of rear side heat exchange part 30 Crossflow fan 30a Circle connecting the outer ends of the wings 31 Fan wings (wings)
71 Stabilizer tongue 72 Stabilizer upper part 73 Stabilizer lower part 92 Air conditioning indoor unit L1 Fan reference horizontal line L2 Scroll reference line O Fan center point P7 Stabilizer front side closest point P8 Rear guider rear side closest point θ0 Reference angle θa No. 1 angle θb 2nd angle θc 3rd angle θd 4th angle SL1 1st straight line SL2 2nd straight line SL3 3rd straight line SL4 4th straight line

JP 2008-8500 A

Claims (2)

A wall-mounted air conditioning indoor unit (92),
A plurality of blades (31) are arranged along the circumference, and a cross flow fan (30) that generates an air flow;
A front-side stabilizer (17) and a rear-side rear guider (18), and the stabilizer is divided into an upper part (72) and a lower part (73) with a tongue part (71) in between, and the stabilizer and the rear guider A casing (10) that forms an air flow passage (10c) for scroll-like air flowing from the cross flow fan to the air outlet (10b);
A heat exchanger (20) including a front side heat exchange part (21) and a back side heat exchange part (22), disposed on the upstream side of the air flow of the cross flow fan;
With
In longitudinal section view,
A horizontal line passing through the fan center point (O) that is the rotation center of the cross flow fan is defined as a fan reference horizontal line (L1),
Among the straight lines that are tangent to a circle (30a) connecting the outer ends of the blades of the crossflow fan and are in contact with the lower portion of the stabilizer, the straight line having the smallest angle with the fan reference horizontal line is scrolled. The reference line (L2)
An angle formed by the fan reference horizontal line and the scroll reference line is a reference angle θ0,
A first straight line (SL1) that is a straight line connecting the front closest point (P7) that is the point closest to the cross flow fan among the upper part of the stabilizer and the fan center point, and the fan reference The angle formed by the horizontal line (L1) is the first angle θa,
A second straight line (SL2) that is a straight line connecting the rear side closest approach point (P8) that is the point closest to the cross flow fan in the rear guider and the fan center point, and the fan reference horizontal line (L1). ) Is the second angle θb,
First angle relation: (θa−θ0)> 16 °
Second angle relational expression: 17 ° <(θb−θ0) <26 °
And the third angle relational expression: θb ≧ θa
To meet
The stabilizer, the rear guider and the cross flow fan are arranged,
Air conditioning indoor unit. In longitudinal section view,
The lower part (21a) of the front side heat exchange part is located below the fan reference horizontal line (L1),
The lower part (22a) of the back side heat exchange part is located above the fan reference horizontal line (L1),
Of the straight lines passing through the lower part of the front side heat exchange section and the fan center point, the straight line having the largest angle with the fan reference horizontal line (L1) is defined as a third straight line (SL3),
An angle formed by the third straight line and the fan reference horizontal line is a third angle θc,
Of the straight lines passing through the lower part of the back side heat exchange part and the fan center point, a straight line having the smallest angle with the fan reference horizontal line is defined as a fourth straight line (SL4),
When the angle formed by the fourth straight line and the fan reference horizontal line is a fourth angle θd,
Fourth angle relational expression: θc> θa
And the fifth angle relational expression: θd <θb
To meet
The stabilizer, the rear guider, the heat exchanger and the cross flow fan are arranged,
The air conditioning indoor unit according to claim 1.

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