JP2023139347A - air conditioner - Google Patents

Abstract

To provide an air conditioner reducing input in a cross flow fan by expanding an area where air flow passing through a heat exchanger flows into the cross flow fan, and thereby suppressing noise.SOLUTION: An air conditioner in the present disclosure includes a cross flow fan, a rear guider, a heat exchanger and an auxiliary heat exchanger. The rear guider is provided with an upper end projection part, and the relation of a distance RX between an intersection point X and an upper end point R and a distance QX between the intersection point X and a lower end point QX satisfies QX/(RX+QX)≥0.5 when a straight line is perpendicular to the front surface of a back surface heat exchanger and circumscribed on the upper end projection part is made to be a straight line A; an intersection point between the straight line A and the back surface of the back surface heat exchanger is made to be the intersection point X; the upper end of the surface facing the back surface heat exchanger in the auxiliary heat exchanger is made to be the upper end point R; and the lower end of the surface facing the back surface heat exchanger in the auxiliary heat exchanger is made to be the lower end point Q on a cross section orthogonal to the rotary shaft of the cross flow fan.SELECTED DRAWING: Figure 2

Description

The present disclosure mainly relates to a home air conditioner.

Generally, an air conditioner has a cross-flow fan with multiple blades, a stabilizer, a rear guider, a front heat exchanger on the front side of the cross-flow fan, and a rear heat exchanger on the back side of the cross-flow fan. A heat exchanger configured with Then, air is sucked in from the top side of the casing, heat is exchanged between the sucked air and the refrigerant flowing inside the heat exchanger, and air is blown out from the bottom side of the casing to perform indoor air conditioning. The rear guider has a proximal portion facing and proximate to the cross-flow fan and separated from the cross-flow fan by a predetermined distance, and an upper end protrusion extending upward from the proximal portion.

Patent Document 1 discloses an air conditioner that aims to prevent a decrease in heat exchange performance and an increase in noise. In this air conditioner, the air passage of the housing is formed continuously with the rear side wall section located behind the rear heat exchanger and the air outlet, and is arranged between the cross flow fan and the heat exchanger. It has a front nose part and a back nose part. The heat exchanger is configured in a substantially inverted V shape with a front heat exchanger and a back heat exchanger, and is disposed so as to cover the cross flow fan including the front nose portion and the back nose portion. The back heat exchanger includes a back main heat exchanger and a back auxiliary heat exchanger, each of which has a constant number of heat transfer tubes arranged in the air flow direction. The auxiliary heat exchanger is located on the windward side of the rear main heat exchanger and is spaced apart from the rear side wall surface, and extends from the lower edge of the rear side auxiliary heat exchanger in a direction perpendicular to the arrangement direction of the heat exchanger tubes. Along the line, the distance to the back side wall part was set as L1, the shortest distance between the auxiliary heat exchanger and the back side wall part was set as L2, and the distance between the back main heat exchanger and the tip of the back nose part was set as L3. Sometimes, the relationships 0.4<(L2/L1)<0.6 and 0.55<(L3/L1) are satisfied.

Japanese Patent Application Publication No. 2014-20718

The air conditioner disclosed in Patent Document 1 makes uniform the wind speed distribution of air passing through the back heat exchanger and the auxiliary heat exchanger, and the wind speed distribution of air passing only through the back heat exchanger. However, the air conditioner disclosed in Patent Document 1 has a problem in that a large backflow vortex is generated between the upper end protrusion and the cross flow fan, resulting in a decrease in air blowing performance.

The present disclosure provides an air conditioner that can improve air blowing performance.

The air conditioner according to the present disclosure includes a cross flow fan, a front heat exchanger disposed on the front side of the cross flow fan, a back heat exchanger disposed on the back side of the cross flow fan, and the back heat exchanger disposed on the front side of the cross flow fan. an auxiliary heat exchanger disposed on the back side of the exchanger, and a rear guider disposed between the cross flow fan and the back heat exchanger,
The rear guider has a proximal portion proximate to the cross flow fan, and an upper end protrusion extending upward from the proximal portion,
In a cross section perpendicular to the rotation axis of the cross flow fan, a straight line perpendicular to the front surface of the back heat exchanger and circumscribing the upper end protrusion is defined as a straight line A, and the straight line A and the back surface of the back heat exchanger The intersection point of the auxiliary heat exchanger is defined as the intersection point X, the upper end of the surface of the auxiliary heat exchanger facing the back heat exchanger is defined as the upper end point R, and the lower end of the surface of the auxiliary heat exchanger facing the back surface heat exchanger is defined as the lower end. In the case of a point Q, the distance RX between the intersection point X and the upper end point R and the distance QX between the intersection point X and the lower end point Q satisfy the relationship QX/(RX+QX)≧0.5.

The air conditioner according to the present disclosure improves air blowing performance by suppressing an increase in heat exchanger ventilation resistance above the upper end of the upper end projection of the rear guider and improving airflow turbulence near the upper end of the upper end projection. is possible.

Vertical cross-sectional view of the air conditioner in Embodiment 1 Vertical cross-sectional view near the back heat exchanger of the air conditioner in Embodiment 1 A diagram showing the air flow near the back heat exchanger of the air conditioner in Embodiment 1. A diagram showing airflow distribution near the back heat exchanger of the air conditioner in Embodiment 1 A diagram showing a change in the blowout air volume with respect to QX/(RX+QX) of the air conditioner in Embodiment 1 A diagram showing the input change of the crossflow fan with respect to QX/(RX+QX) of the air conditioner in Embodiment 1 Vertical cross-sectional view of the air conditioner according to Patent Document 1 Vertical cross-sectional view of the vicinity of the back heat exchanger of the air conditioner according to Patent Document 1

(Findings, etc. that formed the basis of this disclosure)
At the time the inventors came up with the present disclosure, a backflow occurred in the gap between the crossflow fan and the rear guider in a direction opposite to the rotational direction of the crossflow fan, and this backflow caused the adjacent portion of the crossflow fan and rear guider to By passing through the blade, a backflow vortex is formed upstream of the vicinity of the crossflow fan and the rear guider by drawing in the surrounding airflow, and when the blade passes through the backflow vortex, there is a problem in that interference noise is generated. To solve this problem, an upper end protrusion is provided toward the top of the cross flow fan from the adjacent part that partitions the upstream and downstream areas at the rear of the cross flow fan, so that the reverse flow vortex is attached to the surface of the upper end protrusion facing the cross flow fan. There is a technology that allows the center of the vortex to be located upstream of the adjacent part, thereby alleviating interference with the blade and suppressing noise. In an air conditioner using this technology, the rear heat exchanger is located behind the crossflow fan and behind the rear guider, and the lower end of the rear heat exchanger is inserted below the upper end of the upper end protrusion. An air passage is formed between the downstream side surface of the exchanger and the surface of the upper end projection facing the back heat exchanger. With this configuration, the suction airflow passing through the back heat exchanger located below the upper end of the upper end protrusion flows upward along the surface of the upper end projection that faces the back heat exchanger, and Nearby, it turns toward the cross-flow fan and flows into the cross-flow fan.

Here, Patent Document 1 will be described as an example of a conventional air conditioner using FIGS. 7 to 8.

The structure of the air conditioner 1 disclosed in Patent Document 1 will be explained using FIG. 7. The air conditioner 1 includes a housing 4 having an air inlet 2 and an air outlet 3. The housing 4 includes a cross-flow fan 5, a heat exchanger 6 between the air suction port 2 and the cross-flow fan 5, a front casing 7, and a back casing 8. The cross-flow fan 5 has a plurality of fan blades 5A. The heat exchanger 6 includes a front heat exchanger 6A, a back heat exchanger 6B, and an auxiliary heat exchanger 6C. The heat exchanger 6 includes fins 6D and heat exchanger tubes 6E passing through the fins 6D. The front heat exchanger 6A and the back heat exchanger 6B are arranged in a substantially inverted V shape so as to cover the cross-flow fan 5 from above. The auxiliary heat exchanger 6C of the heat exchanger 6 functions as a so-called subcooler, and is arranged on the windward side (upstream side of the air flow) of the back heat exchanger 6B.

The front casing 7 is located in front of the cross-flow fan 5, and a stabilizer 7A bent into a substantially rectangular shape is integrally formed at the tip of the front casing 7.

The back casing 8 is located on the back side of the cross-flow fan 5, and has an upper end protrusion 8C that protrudes between the cross-flow fan 5 and the heat exchanger 6 from the upper end (tip) 8B of the curved surface 8A. Behind the upper end protrusion 8C, there is a channel wall surface 8D extending vertically upward. A recess 8E into which a part of the back heat exchanger 6B is inserted is formed between the upper end 8B of the curved surface 8A of the back casing 8 and the lower end of the flow path wall surface 8D.

The back heat exchanger 6B has a substantially rectangular shape in longitudinal section, and its longitudinal direction is inclined from above the cross-flow fan 5 toward the flow path wall surface 8D, and its lower end is in contact with the flow path wall surface 8D. There is. The lower end of the back heat exchanger 6B is inserted into the recess 8E.

The auxiliary heat exchanger 6C is formed shorter than the longitudinal direction of the back heat exchanger 6B, and is overlapped with a part of the upstream surface of the back heat exchanger 6B. Further, the auxiliary heat exchanger 6C is spaced apart from the channel wall surface 8D. Note that the corner of the auxiliary heat exchanger 6C at the end closer to the channel wall surface 8D is cut out so as to be parallel to the channel wall surface 8D. Since the auxiliary heat exchanger 6C and the flow path wall surface 8D are not in contact with each other, the air path passing through the back heat exchanger 6B and the auxiliary heat exchanger 6C passes through both the back heat exchanger 6B and the auxiliary heat exchanger 6C. There are those that pass through, and those that pass only through the back heat exchanger 6B.

The structure near the back heat exchanger 6B of the air conditioner 1 disclosed in Patent Document 1 will be described using FIG. 8. The lower end of the back heat exchanger 6B is inserted into the recess 8E, and a narrow portion S1 is formed between the downstream surface of the back heat exchanger 6B and the surface of the upper end protrusion 8C facing the back heat exchanger 6B. A narrow portion S2 is formed between the channel wall surface 8D and the auxiliary heat exchanger 6C on the upstream side of the back surface heat exchanger 6B where the auxiliary heat exchanger 6C is not present in the back surface heat exchanger 6B.

The distance from the lower edge of the auxiliary heat exchanger 6C to the flow path wall surface 8D along the direction perpendicular to the arrangement direction of the heat exchanger tubes 6E (directions of arrows A and B) is defined as L1, and The dimension of the narrow part S2, that is, the shortest distance between the auxiliary heat exchanger 6C and the flow path wall surface 8D is L2, and the dimension of the narrow part S1 on the downstream side of the back heat exchanger 6B, that is, the shortest distance between the back heat exchanger 6B and the upper end. When the distance between the tip of the projection 8C is L3, it was set to satisfy the following relationships: 0.4<(L2/L1)<0.6 and 0.55<(L3/L1) It is something.

In this way, by setting the relationship between the distances L1, L2, and L3, the sum of the ventilation resistances of these two narrow parts S1 and S2 and the ventilation resistance of the auxiliary heat exchanger 6C can be made to match. This reduces the imbalance between the wind speed distribution of the air passing through the heat exchanger 6B and the auxiliary heat exchanger 6C (arrow A) and the wind speed distribution of the air passing only through the rear heat exchanger 6B (arrow B), resulting in a decrease in heat exchange performance. The present invention is intended to provide an air conditioner 1 that can prevent an increase in air and noise levels and that has small variations in performance.

However, since the air passing only through the back heat exchanger 6B flows from the bottom to the top through the narrow part S1 between the surface of the upper end protrusion 8C facing the back heat exchanger 6B and the back heat exchanger 6B, Even if the wind speed distribution of the air passing through the back heat exchanger 6B and the auxiliary heat exchanger 6C (arrow A) and the wind speed distribution of the air passing only through the back heat exchanger 6B (arrow B) are made uniform, the back heat exchange will not be possible. The velocity of the airflow that has passed through the heat exchanger 6B and the auxiliary heat exchanger 6C, and the airflow that is deflected toward the once-through fan 5 at the tip of the upper end protrusion 8C after passing only through the back heat exchanger 6B and flowing through the narrow part S1 from below. There is a difference between the speed of Depending on the speed at which the flow is deflected to the once-through fan 5 at the tip of the upper end protrusion 8C after passing only through the back heat exchanger 6B and flowing through the narrow part S1 from below, the turning radius near the tip of the upper end protrusion 8C may vary. becomes larger, and the position where the suction airflow that has passed through the heat exchanger 6 flows into the cross-flow fan 5 becomes a position that is forwardly away from the tip of the upper end protrusion 8C, and faces the cross-flow fan 5 and the cross-flow fan 5 of the upper end protrusion 8C. The backflow vortex generated between the heat exchanger 6 and the cross-flow fan 5 may expand, and the area where the airflow that has passed through the heat exchanger 6 flows into the cross-flow fan 5 may be narrowed. In this case, the inventors discovered the problems that the airflow volume of the fan decreases, the fan input increases, and the noise cannot be suppressed, and in order to solve the problems, they constituted the subject matter of the present disclosure. Ta.

Therefore, the present disclosure reduces the turning radius of the airflow near the tip of the upper end protrusion, moves the position where the suction airflow that has passed through the heat exchanger into the crossflow fan (cross-flow fan) closer to the tip of the upper end protrusion, The area where the airflow that has passed through the heat exchanger flows into the cross-flow fan (once-through fan) is reduced by reducing the backflow vortex that occurs between the cross-flow fan (once-through fan) and the surface of the upper end protrusion that faces the once-through fan. To provide an air conditioner that can improve air blowing performance by expanding the size.

Hereinafter, embodiments will be described in detail with reference to the drawings. However, more detailed explanation than necessary may be omitted. For example, detailed explanations of well-known matters or redundant explanations of substantially the same configurations may be omitted. This is to avoid making the following description unnecessarily redundant and to facilitate understanding by those skilled in the art.

The accompanying drawings and the following description are provided to enable those skilled in the art to fully understand the present disclosure, and are not intended to limit the subject matter recited in the claims.

(Embodiment 1)
Embodiment 1 will be described below using FIGS. 1 to 6.

[1-1. composition]
In FIG. 1, an air conditioner 100 includes a main body casing 103 having an inlet 101 and an outlet 102, a stabilizer 104, a rear guider 105, a cross flow fan 106, and a heat exchanger 107.

The rear guider 105 has a proximal portion 105A that faces and approaches the cross-flow fan 106 and is separated from the cross-flow fan 106 by a predetermined dimension, and an upper end protrusion 105B that extends upward from the proximal portion 105A. The rear guider 105 is arranged between the crossflow fan 106 and a backside heat exchanger 107B, which will be described later.

The crossflow fan 106 has a plurality of blades 106A arranged in a cylindrical shape.

The heat exchanger 107 includes a front heat exchanger 107A, a back heat exchanger 107B, and an auxiliary heat exchanger 108. The front heat exchanger 107A is arranged on the front side of the cross flow fan 106. The back heat exchanger 107B is arranged on the back side of the cross flow fan 106. The auxiliary heat exchanger 108 is disposed on the back side of the back heat exchanger 107B, that is, on the opposite side of the surface where the cross flow fan 106 and the back heat exchanger 107B face each other. is arranged on the surface of the back heat exchanger 107B on the upstream side of the air flowing in from the suction port 101 when the crossflow fan rotates. Hereinafter, for convenience, the surface on the windward side of the heat exchanger will be referred to as the upstream surface, and the surface on the leeward side of the heat exchanger will be referred to as the downstream surface, with respect to the air flowing in from the suction port 101.

The front heat exchanger 107A and the back heat exchanger 107B include fins 107C and heat transfer tubes 107D passing through the fins 107C, and the outer diameter D1 of the heat transfer tubes 107D is D1=5MM.

The auxiliary heat exchanger 108 includes fins 108A and heat exchanger tubes 108B passing through the fins 108A, and the outer diameter D2 of the heat exchanger tubes 108B is D2=6MM.

Next, referring to FIG. 2, the detailed shape of the vicinity of the back heat exchanger 107B will be described. The rear guider 105 has a proximal portion 105A that faces and approaches the cross-flow fan 106 and is separated from the cross-flow fan 106 by a predetermined dimension, and has an upper end protrusion 105B that extends upward from the proximal portion 105A.

The straight line that is perpendicular to the substantially planar front surface (downstream surface) of the rear heat exchanger 107B and circumscribes the upper end protrusion 105B is defined as a straight line A, and the intersection of the straight line A and the rear surface (upstream surface) of the rear heat exchanger 107B is the intersection point. X, the upper end of the surface of the auxiliary heat exchanger facing the back heat exchanger (downstream surface) is the upper end point R, and the lower end of the surface of the auxiliary heat exchanger facing the back heat exchanger (downstream surface) is the lower end point When Q, the lengths of the distance RX between the intersection point X and the upper end point R and the distance QX between the intersection point X and the lower end point Q are QX/(RX+QX)≧0.5.

The intersection of the straight line A and the back surface (upstream surface) of the back heat exchanger 107B is the intersection point X, the lower end point of the back surface (upstream surface) of the back heat exchanger 107B is the lower end point Y, and the distance between the intersection point X and the lower end point Y is Let the distance be XY, and let the length of the auxiliary heat exchanger 108 in the step direction be the length H. The distance XY and the length H satisfy XY/H≧1.0. Here, the stage direction length H of the auxiliary heat exchanger 108 is defined as the surface of the auxiliary heat exchanger 108 closest to the back heat exchanger 107B, that is, the surface of the auxiliary heat exchanger facing the back heat exchanger (downstream surface). ) Specified by the distance between the top and bottom edges of

[1-2. motion]
The operation of the air conditioner 100 configured as described above will be described below with reference to FIG. In the air conditioner 100, when the cross flow fan 106 rotates, indoor air is sucked into the main body casing 103 from the suction port 101. The indoor air sucked into the main body casing 103 passes through the front heat exchanger 107A, the back heat exchanger 107B, and the auxiliary heat exchanger 108, flows into the crossflow fan 106, and is blown out from the air outlet 102 into the indoor space. Ru.

At this time, there are four suction airflows: suction airflow 200A and suction airflow 200B that pass only through the back heat exchanger 107B, and suction airflow 200C and suction airflow 200D that pass through both the back heat exchanger 107B and the auxiliary heat exchanger 108. do.

The suction airflow 200A passes through a portion of the back heat exchanger 107B located below the upper end of the upper end protrusion 105B.

The suction airflow 200B passes through a portion of the back heat exchanger 107B located above the upper end of the upper end protrusion 105B.

The suction airflow 200C passes through both the auxiliary heat exchanger 108 and the portion of the back heat exchanger 107B located below the upper end of the upper end protrusion 105B.

The suction airflow 200D passes through both the auxiliary heat exchanger 108 and the portion of the back heat exchanger 107B located above the upper end of the upper end protrusion 105B.

The suction airflow 200A and the suction airflow 200C passing through the portion of the back heat exchanger 107B located below the upper end of the upper end protrusion 105B flow upward along the surface of the upper end protrusion 105B facing the back heat exchanger 107B. Then, near the upper end of the upper end protrusion 105B, it turns toward the cross flow fan 106 and flows into the cross flow fan 106.

In addition, the suction airflow 200B and the suction airflow 200D passing through the portion of the back heat exchanger 107B located above the upper end of the upper end protrusion 105B are connected to the upper end protrusion of the back heat exchanger 107B near the upper end of the upper end protrusion 105B. It merges with the suction airflow 200A and the suction airflow 200C passing through the portion located below the upper end of the portion 105B, and flows into the crossflow fan 106.

The suction airflow 200A and the suction airflow 200C passing through the portion of the back heat exchanger 107B located below the upper end of the upper end protrusion 105B flow upward along the surface of the upper end protrusion 105B that faces the back heat exchanger 107B. However, near the upper end of the upper end protrusion 105B, when joining with the suction airflow 200B and the suction airflow 200D passing through the portion of the back heat exchanger 107B located above the upper end of the upper end protrusion 105B, it is suppressed from above to below. It turns toward the cross-flow fan 106 and flows into the cross-flow fan 106.

The ventilation resistance of the back heat exchanger 107B and the auxiliary heat exchanger 108 is higher than that of only the back heat exchanger 107B. The wind speeds of the airflow 200C and the suction airflow 200D are lower than the wind speeds of the suction airflows 200A and 200B that pass only through the back heat exchanger 107B.

The auxiliary heat exchanger 108 is located at a position where QX/(RX+QX)≧0.5, that is, the auxiliary heat exchanger 108 is located at a position where QX/(RX+QX)≧0.5. More than half of the container 108 in the tier direction is located below. With this arrangement, near the tip of the upper end protrusion 105B, the combined wind speed of the suction airflow 200A and the suction airflow 200C flowing from below the upper end protrusion 105B toward the tip of the upper end protrusion 105B is The velocity is relatively lower than the combined wind speed of the suction airflow 200B and the suction airflow 200D flowing from above the upper end protrusion 105B toward the vicinity of the tip. Due to the difference in wind speed, the suction airflow 200A and the suction airflow 200C passing through the back heat exchanger 107B located below the upper end of the upper end protrusion 105B are located near the upper end of the upper end protrusion 105B and above the upper end of the upper end protrusion 105B. The airflow is strongly suppressed by the suction airflow 200C and the suction airflow 200D passing through the back heat exchanger 107B located at .

A countercurrent vortex 201 is generated in the space between the crossflow fan 106 and the surface of the upper end protrusion 105B facing the crossflow fan 106 in a direction opposite to the rotational direction of the crossflow fan 106. The backflow vortex 201 adheres to the surface of the upper end protrusion 105B facing the crossflow fan 106, and the vortex center is located upstream of the proximal portion 105A.

Using FIGS. 4, 5, and 6, when the straight line A intersects with the auxiliary heat exchanger 108, that is, the intersection point X contacts the auxiliary heat exchanger 108, improvement of air blowing performance depending on the placement position of the auxiliary heat exchanger will be explained in detail.

The airflow distribution in the vicinity of the back heat exchanger 107B of the air conditioner 100 in this embodiment, particularly in the vicinity of the upper end of the upper end protrusion 105B, will be described in detail below with reference to FIG.

In FIG. 4, QX/(RX+QX)=0.34 as a comparison of the intake airflow near the tip of the upper end protrusion 105B and the inflow airflow to the crossflow fan 106 depending on the position of the auxiliary heat exchanger 108. Wind speed distribution of the intake airflow near the tip of the upper end protrusion 105B based on numerical analysis in the case of the position of the auxiliary heat exchanger 108 and the case of the position of the auxiliary heat exchanger 108 where QX/(RX+QX) = 0.67 A comparison of the flow line distribution of the inflow air to the cross flow fan 106 is shown.

The position of the auxiliary heat exchanger is shown in the upper part of Figure 4. In the figure, regarding the area surrounded by a square, the middle part of FIG. 4 shows the wind speed distribution in the vicinity of the upper end protrusion 105B, and the lower part shows the streamline distribution of the airflow flowing into the cross-flow fan 106.

The wind speed distribution in the vicinity of the upper end protrusion 105B will be explained using the middle part of FIG. 4. In the middle part of FIG. 4, the broken line indicates the boundary line of the wind speed of 3 M/S, and the area inside the broken line indicates the wind speed of 3 M/S or more.

In addition, the left side of the middle row of FIG. 4 shows the wind speed distribution in the case of the position of the auxiliary heat exchanger 108 where QX/(RX+QX)=0.34, and the right side of the middle row shows the wind speed distribution where QX/(RX+QX)=0.67. A wind speed distribution diagram in the case of the position of the auxiliary heat exchanger 108 is shown. On the middle right side of FIG. 4, a dotted line indicates the wind speed of 3 M/S at the position of the auxiliary heat exchanger 108 where QX/(RX+QX)=0.34.

Comparing the positions of the auxiliary heat exchanger 108 where QX/(RX+QX)=0.34 and QX/(RX+QX)=0.67, the area near the upper end protrusion 105B has a wind speed of 3 M/S or more. That agrees. However, in the case of the position of the auxiliary heat exchanger 108 where QX/(RX+QX)=0.67, the broken line is narrower on the upper end side of the upper end protrusion 105B. In other words, in the case of the position of the auxiliary heat exchanger 108 where QX/(RX+QX)=0.67, the wind speed of the intake airflow passing through the back heat exchanger 107B located below the upper end of the upper end protrusion 105B is It can be seen that it is decreasing.

The streamline distribution of the incoming airflow to the crossflow fan 106 will be explained using the lower part of FIG. 4. A solid line in the streamline diagram indicates an incoming airflow that swirls toward the crossflow fan 106 near the upper end of the upper end protrusion 105B. Among the streamlines flowing into the cross-flow fan 106, a solid line with an arrow indicates the streamline most rearward from the tip of the upper end protrusion 105B. That is, the solid line with an arrow indicates the boundary between the suction airflow that actually flows into the crossflow fan 106 and the backflow vortex.

The lower left side of FIG. 4 shows the streamline distribution in the case of the position of the auxiliary heat exchanger 108 where QX/(RX+QX)=0.34, and the lower right side shows the streamline distribution where QX/(RX+QX)=0.67. A streamline distribution diagram for the position of the heat exchanger 108 is shown. On the lower right side of FIG. 4, the rearmost streamline in the case of the position of the auxiliary heat exchanger 108 where QX/(RX+QX)=0.34 is shown as a dotted line.

In the case of the position of the auxiliary heat exchanger 108 where QX/(RX+QX) = 0.67, the cross flow fan 106 actually The boundary between the incoming airflow and the backflow vortex has moved to the right in the figure, and the area of the backflow vortex has shrunk. This indicates that the area where the airflow that has passed through the heat exchanger 107 flows into the crossflow fan 106 is expanded.

In FIG. 5, a change in air volume with respect to QX/(RX+QX) will be described. FIG. 5 is a diagram illustrating changes in the amount of air blown from the air conditioner 100 when QX/(RX+QX) is used as a parameter based on numerical analysis. The horizontal axis is QX/(RX+QX), and the vertical axis is the air volume ratio when the rotation speed of the cross flow fan 106 of the air conditioner 100 is the same (air volume ratio 100 when QX/(RX+QX) = 0.5) %). The coordinates of the five points plotted on the XY coordinates are (0,97.8), (0.34,99.4), (0.5,100), (0.67,100.3), (1.0,99.8). As shown in FIG. 5, when QX/(RX+QX) is less than 0.5, the air volume ratio decreases rapidly, whereas when QX/(RX+QX) is 0.5 or more, the air volume ratio remains almost constant. In other words, when the value of QX/(RX+QX) is increased from 0 to 1, the air volume ratio increases rapidly between 0 and 0.5, and when it reaches 0.5, the air volume ratio reaches its upper limit. reach In other words, it can be said that when QX/(RX+QX) is 0.5 or more, the air volume ratio increases and the air blowing performance improves.

In FIG. 6, input changes to QX/(RX+QX) will be explained. FIG. 6 is a diagram showing input changes to the air conditioner 100 when QX/(RX+QX) is a parameter based on numerical analysis. The horizontal axis shows QX/(RX+QX), and the vertical axis shows the input ratio of the crossflow fan when the air volume of the air conditioner 100 is the same (100% input ratio when QX/(RX+QX) is 0.0) ). The coordinates of the five points plotted on the XY coordinates are (0,100), (0.34,100.1), (0.5,99.9), (0.67,99.9), (1.0,99.8). As shown in Figure 6, the input ratio increases when QX/(RX+QX) is between 0.0 and 0.34, but when it is between 0.34 and 0.5, the input ratio decreases rapidly. Thereafter, the input ratio remains low until it reaches 1.0. In other words, there is a point where QX/(RX+QX) rapidly improves between 0.34 and 0.5, and it can be said that the input ratio is reduced if QX/(RX+QX) is at least 0.5 or more. Moreover, when QX/(RX+QX) is 0.5 or more, the input ratio can be reduced by 0.1%, and a sufficient improvement in air blowing performance can be expected.

Above, improvement in air blowing performance has been explained in the case where the straight line A intersects with the auxiliary heat exchanger 108, that is, the intersection point X comes into contact with the auxiliary heat exchanger 108. However, when the intersection point X does not come into contact with the auxiliary heat exchanger 108, In other words, even when all of the auxiliary heat exchangers 108 are located below the straight line A, the relationship QX/(RX+QX)≧0.5 is satisfied, and the same effect is produced, so that the air blowing performance of the air conditioner is improved.

[1-3. Effects, etc.]
As described above, in this embodiment, the air conditioner 100 includes a main body casing 103 having an inlet 101 and an outlet 102, a stabilizer 104, a rear guider 105, a cross flow fan 106, and a front heat exchanger. 107A, a back heat exchanger 107B, and an auxiliary heat exchanger 108. The rear guider 105 has a proximal portion 105A that faces and approaches the cross-flow fan 106 and is separated from the cross-flow fan 106 by a predetermined dimension, and has an upper end protrusion 105B that extends upward from the proximal portion 105A. , has an upper end protrusion 105B extending upward from the proximal portion 105A. The intersection point X of the straight line A that is perpendicular to the front surface (downstream surface) of the back surface heat exchanger 107B and circumscribes the upper end protrusion 105B and the back surface (upstream surface) of the back surface heat exchanger 107B, and the back surface heat exchanger in the auxiliary heat exchanger. The upper end point R of the opposing surface (downstream surface), the lower end point Q of the surface (downstream surface) of the auxiliary heat exchanger that faces the rear heat exchanger, the distance RX between the intersection X and the lower end point R, and the distance RX between the intersection X and the lower end The length of the distance QX of the point Q is QX/(RX+QX)≧0.5. The auxiliary heat exchanger 108 is located at a position where QX/(RX+QX)≧0.5, and the auxiliary heat exchanger 108 is located at a position where QX/(RX+QX)≧0.5. 108 is located below, the wind speed of the suction airflow flowing from below the upper end protrusion 105B toward the tip of the upper end protrusion 105B near the tip of the upper end protrusion 105B is The wind speed is relatively lower than the wind speed of the suction airflow flowing from above the upper end projection 105B toward the vicinity of the tip of the projection 105B. Due to the difference in wind speed, the suction airflow that passes through the portion of the back heat exchanger 107B located below the upper end of the upper end protrusion 105B is near the upper end of the upper end protrusion 105B. It is strongly suppressed by the suction airflow that passes through the portion located above the upper end. Thereby, the air conditioner 100 can reduce the turning radius of the airflow swirling toward the crossflow fan 106 near the upper end of the upper end protrusion 105B. Therefore, the region where the airflow that has passed through the heat exchanger 107 flows into the cross-flow fan 106 is reduced by reducing the backflow vortex that occurs between the cross-flow fan 106 and the surface of the upper end protrusion 105B that faces the cross-flow fan 106. By enlarging, the amount of air blown from the cross-flow fan 106 can be increased, the input to the cross-flow fan 106 can be reduced, noise can be suppressed, and the air blowing performance of the air conditioner can be improved.

As in this embodiment, the distance XY between the intersection X of the straight line A and the upstream surface of the back heat exchanger 107B and the lower end point Y of the upstream surface of the back heat exchanger 107B, and the distance The length H may be XY/H≧1.0.

Since the length H of the auxiliary heat exchanger 108 satisfies XY/H≧1.0, the auxiliary heat exchanger 108 has an auxiliary All heat exchangers 108 can be located below straight line A. Since all the auxiliary heat exchangers 108 are located below the straight line A, the back heat exchanger 107B and the auxiliary heat The wind speed of the suction airflow passing through the exchanger 108 and the suction airflow flowing from above the upper end protrusion 105B toward the vicinity of the tip of the upper end protrusion 105B, passing only through the back heat exchanger 107B. The relative wind speed difference between the two wind speeds can be further expanded. Due to the difference in wind speed, the suction airflow that passes through the portion of the back heat exchanger 107B located below the upper end of the upper end protrusion 105B is near the upper end of the upper end protrusion 105B. It is strongly suppressed by the suction airflow that passes through the portion located above the upper end. Thereby, the air conditioner 100 can further reduce the turning radius of the airflow swirling toward the crossflow fan 106 near the upper end of the upper end protrusion 105B. Therefore, the backflow vortex generated between the cross-flow fan 106 and the surface of the upper end protrusion 105B facing the cross-flow fan 106 is more effectively reduced, and the airflow that has passed through the heat exchanger 107 is directed to the cross-flow fan 106. By enlarging the inflow area depending on various conditions, it is possible to increase the amount of air blown from the cross flow fan 106, reduce input, and suppress noise.

As in this embodiment, the heat exchanger 107 includes fins 107C and heat transfer tubes 107D passing through the fins 107C, and the auxiliary heat exchanger 108 includes fins 108A and heat transfer tubes 108B passing through the fins 108A. The outer diameter D1 of the heat exchanger tube 107D and the outer diameter D2 of the heat exchanger tube 108B may satisfy D1<D2. However, the outer diameter D1 of heat exchanger tube 107D = 5 MM and the outer diameter D2 = 6 MM of heat exchanger tube 108B shown in this embodiment are only examples. The heat exchanger 107 may be any heat exchanger tube 107D that satisfies D1≦5MM. As a result, in the air conditioner 100, the outer diameter D1 of the heat exchanger tube 107D and the outer diameter D2 of the heat exchanger tube 108B become D1<D2, and the ventilation resistance of the auxiliary heat exchanger 108 becomes larger than that of the back heat exchanger 107B. Then, the wind speed of the suction airflow flowing from below the upper end projection 105B through the back heat exchanger 107B and the auxiliary heat exchanger 108 toward the tip of the upper end projection 105B, and the vicinity of the tip of the upper end projection 105B. It is possible to further increase the relative wind speed difference with the wind speed of the suction airflow flowing from above the upper end protrusion 105B through only the back side heat exchanger 107B.

In addition, the heat exchanger tube 107D is provided with a back heat exchanger 107B whose outer diameter D1 is 5 MM to reduce pressure loss. It is possible to actively increase the wind speed of the suction airflow flowing from above the upper end protrusion 105B, passing only through the back heat exchanger 107B, toward the vicinity of the tip of the upper end protrusion 105B. Therefore, the backflow vortex generated between the cross-flow fan 106 and the surface of the upper end protrusion 105B facing the cross-flow fan 106 is more effectively reduced, and the airflow that has passed through the heat exchanger 107 is directed to the cross-flow fan 106. By enlarging the inflow area, the amount of air blown from the cross flow fan 106 can be increased, the input power can be reduced, and noise can be suppressed.

In the above embodiment, when the upper end point of the upstream surface of the back heat exchanger 107B is the upper end point Z, the distance XZ between the intersection X of the straight line A and the upstream surface of the back heat exchanger 107B and the upper end point Z is , the upper end protrusion of the rear heat exchanger 107B such that the distance XY between the intersection X of the straight line A and the upstream surface of the rear heat exchanger 107B and the lower end point Y of the upstream surface of the rear heat exchanger 107B satisfies XZ<XY. It is preferable that there are more regions located below the upper end of 105B.

Note that the above-described embodiments are for illustrating the technology of the present disclosure, and therefore various changes, substitutions, additions, omissions, etc. can be made within the scope of the claims or equivalents thereof.

The present disclosure reduces the turning radius of the airflow swirling toward the crossflow fan near the upper end of the upper end protrusion, and reduces the backflow vortex formed upstream of the vicinity of the rear guider, so that the airflow passing through the heat exchanger can be reduced. Since the air blowing performance can be improved by expanding the area where air flows into the cross-flow fan, it is suitable for use in home air conditioning and commercial air conditioning.

100 Air conditioner 101 Suction port 102 Air outlet 103 Main body casing 104 Stabilizer 105 Rear guider 105A Proximal part 105B Upper end protrusion 106 Cross flow fan 107 Heat exchanger 107A Front heat exchanger 107B Back heat exchanger 107C Fin 107D Heat transfer tube 108 auxiliary heat Exchanger 108A Fin 108B Heat exchanger tube

Claims (4)

a cross flow fan; a front heat exchanger disposed on the front side of the cross flow fan; a rear heat exchanger disposed on the rear side of the cross flow fan; and a rear heat exchanger disposed on the rear side of the cross flow fan; an auxiliary heat exchanger disposed in the auxiliary heat exchanger, and a rear guider disposed between the cross flow fan and the rear heat exchanger,
The rear guider has a proximal portion proximate to the cross flow fan, and an upper end protrusion extending upward from the proximal portion,
In a cross section perpendicular to the rotation axis of the cross flow fan, a straight line perpendicular to the front surface of the back heat exchanger and circumscribing the upper end protrusion is defined as a straight line A, and the straight line A and the back face of the back heat exchanger are defined as , the upper end of the surface of the auxiliary heat exchanger facing the back heat exchanger is the upper end point R, and the lower end of the surface of the auxiliary heat exchanger facing the back heat exchanger is the lower end point Q, the distance RX between the intersection point X and the upper end point R, and the distance QX between the intersection point X and the lower end point Q are QX/(RX+QX)≧0.5. . When the intersection X, the lower end point Y of the back surface of the back heat exchanger, the distance XY between the intersection X and the lower end point Y, and the length H of the auxiliary heat exchanger in the step direction, XY/H The air conditioner according to claim 1, wherein ≧1.0. The back heat exchanger includes back heat exchanger fins and back heat exchanger heat transfer tubes passing through the back heat exchanger fins, and the auxiliary heat exchanger includes auxiliary heat exchanger fins and the auxiliary heat exchanger fins. auxiliary heat exchanger heat exchanger tubes penetrating through exchanger fins, and an outer diameter D1 of the back heat exchanger heat exchanger tubes and an outer diameter D2 of the auxiliary heat exchanger heat exchanger tubes satisfy D1<D2. The air conditioner according to 1 or 2. The air conditioner according to any one of claims 1 to 3, wherein the outer diameter D1 of the back heat exchanger heat transfer tube satisfies D1≦5MM.