FORM 2
THE PATENTS ACT, 1970
(39 of 1970)
&
THE PATENTS RULES, 2003
COMPLETE SPECIFICATION
[See section 10, Rule 13]
INDOOR UNIT AND AIR CONDITIONER
MITSUBISHI ELECTRIC CORPORATION A CORPORATION ORGANISED AND
EXISTING UNDER THE LAWS OF JAPAN, WHOSE ADDRESS IS 7-3,
MARUNOUCHI 2-CHOME, CHIYODA-KU, TOKYO 1008310, JAPAN
THE FOLLOWING SPECIFICATION PARTICULARLY DESCRIBES THE
INVENTION AND THE MANNER IN WHICH IT IS TO BE PERFORMED.
2
[DESCRIPTION]
[Technical Field]
[0001]
The present disclosure relates to an indoor unit and an air conditioner.
5 [Background Art]
[0002]
In the related art, an indoor unit of an air conditioner equipped with a cross-flow
fan has been known. Inside such an indoor unit, a stabilizer that separates a suction flow
path and a blowout flow path of the cross-flow fan from each other is provided. The
10 stabilizer forms a circulating vortex at a boundary portion between the suction flow path
and the blowout flow path. The circulating vortex may become larger in a case where a
ventilation resistance of a suction port increases as an operation time of the indoor unit
increases, and may cause condensation by drawing humid indoor air into a blowout port.
Patent Document 1 discloses an indoor unit in which a protrusion is provided in a stabilizer
15 in order to move a circulating vortex closer to a suction flow path and suppress the
occurrence of a backflow.
[Citation List]
[Patent Document]
[0003]
20 [Patent Document 1]
Japanese Unexamined Patent Application, First Publication No. 2004-150789
[Summary of Invention]
[PROBLEM TO BE SOLVED BY THE INVENTION]
[0004]
25 In the indoor unit described in Patent Document 1, since the circulating vortex is
3
moved closer to the suction flow path by providing the protrusion, there is a problem in
that the circulating vortex collides with the stabilizer in a case where the ventilation
resistance is low, conversely. In a case where the stabilizer and the circulating vortex
collide with each other, there is a problem in that a pressure fluctuation at a collision zone
5 increases, and a rotation sound of the cross-flow fan becomes louder.
[0005]
In view of the above-described circumstances, an object of the present disclosure
is to provide an indoor unit capable of suppressing the occurrence of internal condensation
and the occurrence of noise, and an air conditioner including the indoor unit.
10 [MEANS TO SOLVE THE PROBLEM]
[0006]
An aspect of an indoor unit according to the present disclosure is an indoor unit
of an air conditioner, the indoor unit including: a heat exchanger; a cross-flow fan; a
housing that includes a suction port and a blowout port and that accommodates the heat
15 exchanger and the cross-flow fan therein; and a stabilizer that separates a suction flow path
and a blowout flow path of the cross-flow fan from each other, in which the stabilizer
includes a tongue portion that extends along an outer circumference of the cross-flow fan
and that has a facing surface facing the cross-flow fan, a first protrusion portion that
protrudes from the facing surface toward the cross-flow fan, and a second protrusion
20 portion that protrudes from the facing surface toward the cross-flow fan and that is located
closer to the blowout flow path than the first protrusion portion.
[0007]
An aspect of an air conditioner according to the present disclosure includes: the
indoor unit; and an outdoor unit.
25
4
[EFFECTS OF THE INVENTION]
[0008]
According to the present disclosure, it is possible to provide an indoor unit capable
of suppressing the occurrence of internal condensation and the occurrence of noise, and an
5 air conditioner including the indoor unit.
[Brief Description of Drawings]
[0009]
FIG. 1 is a schematic diagram showing a schematic configuration of an air
conditioner according to an embodiment.
10 FIG. 2 is a perspective view of an indoor unit in the embodiment.
FIG. 3 is a cross-sectional view of the indoor unit in the embodiment.
FIG. 4 is a perspective view of a stabilizer in the embodiment.
FIG. 5 is a partially enlarged view showing a part of FIG. 3.
FIG. 6 is a cross-sectional view of the indoor unit in the embodiment, and is a
15 diagram schematically showing a first circulating vortex.
FIG. 7 is a cross-sectional view of the indoor unit in the embodiment, and is a
diagram schematically showing a second circulating vortex.
[Description of Embodiments]
[0010]
20 Hereinafter, an embodiment of the present disclosure will be described with
reference to the drawings. The scope of the present disclosure is not limited to the
following embodiment, and can be changed in any way within the scope of technical ideas
of the present disclosure. In addition, in the following drawings, a scale and the number
in each structure may be different from a scale and the number in an actual structure to
25 facilitate understanding of each configuration.
5
[0011]
In addition, in the drawings, an X-axis, a Y-axis, and a Z-axis are shown as
appropriate. The X-axis indicates one direction in a horizontal direction. The Y-axis
indicates another direction in the horizontal direction. The Z-axis indicates a vertical
5 direction. In the following description, a horizontal direction along the X-axis is referred
to as a “front-rear direction X”, a horizontal direction along the Y-axis is referred to as a
“left-right direction Y”, and a vertical direction is referred to as a “vertical direction Z”.
The front-rear direction X, the left-right direction Y, and the vertical direction Z are
directions orthogonal to each other. In the following description, a side (+Z side) in the
10 vertical direction Z to which an arrow on the Z-axis points is defined as an upper side, and
a side (-Z side) in the vertical direction Z opposite to the side to which the arrow on the Zaxis points is defined as a lower side. In addition, a side (+X side) of the front-rear
direction X to which an arrow on the X-axis points is defined as a front side, and a side (-
X side) in the front-rear direction X opposite to the side to which the arrow on the X-axis
15 points is defined as a rear side. In addition, the left-right direction Y is a left-right
direction in a case in which the indoor unit of the embodiment described below is viewed
from the front (+X side). That is, a side (+Y side) in the left-right direction Y to which
an arrow on the Y-axis points is defined as a right side, and a side (-Y side) in the left-right
direction Y opposite to the side to which the arrow on the Y-axis points is defined as a left
20 side.
[0012]
FIG. 1 is a schematic diagram showing a schematic configuration of an air
conditioner 100 according to the present embodiment. As shown in FIG. 1, the air
conditioner 100 includes an outdoor unit 10, an indoor unit 20, and a circulation path
25 portion 18. The outdoor unit 10 is disposed outdoors. The indoor unit 20 is disposed
6
indoors. The outdoor unit 10 and the indoor unit 20 are connected to each other by the
circulation path portion 18 through which a refrigerant 19 circulates.
[0013]
The air conditioner 100 enables heat exchange between the refrigerant 19 flowing
5 inside the circulation path portion 18 and the air in a room in which the indoor unit 20 is
disposed, thereby regulating a temperature of the air in the room. Examples of the
refrigerant 19 include a fluorine-based refrigerant having a low global warming potential
(GWP) and a hydrocarbon-based refrigerant.
[0014]
10 The outdoor unit 10 includes a housing 11, a compressor 12, a heat exchanger 13,
a flow regulating valve 14, a blower 15, a four-way valve 16, and a control unit 17. The
compressor 12, the heat exchanger 13, the flow regulating valve 14, the blower 15, the
four-way valve 16, and the control unit 17 are accommodated inside the housing 11.
[0015]
15 The compressor 12, the heat exchanger 13, the flow regulating valve 14, and the
four-way valve 16 are provided parts of the circulation path portion 18 located inside the
housing 11. The compressor 12, the heat exchanger 13, the flow regulating valve 14, and
the four-way valve 16 are connected by the parts of the circulation path portion 18 located
inside the housing 11.
20 [0016]
The four-way valve 16 is provided in a part of the circulation path portion 18
connected to a discharge side of the compressor 12. The four-way valve 16 can reverse
a direction of the refrigerant 19 flowing inside the circulation path portion 18 by switching
between paths of parts of the circulation path portion 18. In a case where the paths
25 connected by the four-way valve 16 are the paths indicated by solid lines in the four-way
7
valve 16 in FIG. 1, the refrigerant 19 flows inside the circulation path portion 18 in a
direction indicated by a solid line arrow in FIG. 1. On the other hand, in a case where the
paths connected by the four-way valve 16 are the paths indicated by dashed lines in the
four-way valve 16 in FIG. 1, the refrigerant 19 flows inside the circulation path portion 18
5 in a direction indicated by a dashed line arrow in FIG. 1.
[0017]
The indoor unit 20 includes a housing 21, a heat exchanger 22, a cross-flow fan
23 as a blower, and a control unit 24. The housing 21 accommodates the heat exchanger
22, the cross-flow fan 23, and the control unit 24 therein. The indoor unit 20 can perform
10 a cooling operation for cooling the air in the room in which the indoor unit 20 is disposed
and a heating operation for warming the air in the room in which the indoor unit 20 is
disposed. In FIG. 1, the cross-flow fan 23 is schematically shown.
[0018]
In a case where the indoor unit 20 performs the cooling operation, the refrigerant
15 19 flowing inside the circulation path portion 18 flows in the direction indicated by the
solid line arrow in FIG. 1. That is, in the case where the indoor unit 20 performs the
cooling operation, the refrigerant 19 flowing inside the circulation path portion 18
circulates to return to the compressor 12 after circulating through the compressor 12, the
heat exchanger 13 of the outdoor unit 10, the flow regulating valve 14, and the heat
20 exchanger 22 of the indoor unit 20 in this order. In the cooling operation, the heat
exchanger 13 in the outdoor unit 10 functions as a condenser, and the heat exchanger 22 in
the indoor unit 20 functions as an evaporator.
[0019]
On the other hand, in a case where the indoor unit 20 performs the heating
25 operation, the refrigerant 19 flowing inside the circulation path portion 18 flows in the
8
direction indicated by the dashed line in FIG. 1. That is, in the case where the indoor unit
20 performs the heating operation, the refrigerant 19 flowing inside the circulation path
portion 18 circulates to return to the compressor 12 after circulating through the
compressor 12, the heat exchanger 22 of the indoor unit 20, the flow regulating valve 14,
5 and the heat exchanger 13 of the outdoor unit 10 in this order. In the heating operation,
the heat exchanger 13 in the outdoor unit 10 functions as an evaporator, and the heat
exchanger 22 in the indoor unit 20 functions as a condenser.
[0020]
Next, the indoor unit 20 will be described in more detail. FIG. 2 is a perspective
10 view schematically showing the indoor unit 20. FIG. 3 is a cross-sectional view showing
the indoor unit 20.
[0021]
As shown in FIG. 2, the indoor unit 20 is a wall-mounted type indoor unit that is
fixed to a wall surface WS of the room. The indoor unit 20 has a substantially rectangular
15 shape that is long in the left-right direction Y.
[0022]
As shown in FIG. 3, the cross-flow fan 23 is accommodated in the housing 21 of
the indoor unit 20. The cross-flow fan 23 extends in the left-right direction Y. The
cross-flow fan 23 rotates around a rotation axis R extending in the left-right direction Y.
20 The cross-flow fan 23 includes a plurality of blades 23a arranged in a circumferential
direction.
[0023]
In the following description, unless otherwise specified, a direction (Y-axis
direction) parallel to the rotation axis R of the cross-flow fan 23 is simply referred to as an
25 “axial direction”. The axial direction is the left-right direction Y of the indoor unit 20.
9
In addition, a radial direction around the rotation axis R is simply referred to as a “radial
direction”. In addition, a circumferential direction around the rotation axis R, that is, a
direction around the rotation axis R is simply referred to as a “circumferential direction”,
and a direction in which the cross-flow fan 23 rotates in the circumferential direction is
5 referred to as a rotation direction RD.
[0024]
The heat exchanger 22 has a first heat exchanger 22a, a second heat exchanger
22b, and a third heat exchanger 22c. The first heat exchanger 22a is located in front of
the cross-flow fan 23. The first heat exchanger 22a extends in the vertical direction Z as
10 viewed in the left-right direction Y. The second heat exchanger 22b and the third heat
exchanger 22c are located above the cross-flow fan 23. The second heat exchanger 22b
extends upward and obliquely rearward from an upper end portion of the first heat
exchanger 22a as viewed in the left-right direction Y. The third heat exchanger 22c is
located rearward of the second heat exchanger 22b. The third heat exchanger 22c extends
15 downward and obliquely rearward from an upper end portion of the second heat exchanger
22b as viewed in the left-right direction Y.
[0025]
The housing 21 has an outer shell member 21b and a wind path member 21a.
The outer shell member 21b is a member that constitutes a part of an outer shell of the
20 housing 21. The outer shell member 21b improves designability of an external
appearance of the indoor unit 20. The outer shell member 21b has a substantially
rectangular box shape that is open to the rear. An opening of the outer shell member 21b
on the rear side is blocked by the wind path member 21a.
[0026]
25 The wind path member 21a is a member that constitutes a part of a wind path
10
through which the air suctioned into the housing 21 by the cross-flow fan 23 passes. The
wind path member 21a is hooked on an installation plate (not shown) that is fixed to the
wall surface WS. Accordingly, the indoor unit 20 is fixed to the wall surface WS.
[0027]
5 The wind path member 21a includes a casing portion 29. The casing portion 29
extends along an outer circumference of the cross-flow fan 23 on a rear side of the crossflow fan 23. The casing portion 29 is gradually spaced apart from the outer circumference
of the cross-flow fan 23 toward a lower side of the casing portion 29. A blowout flow
path F2 of the cross-flow fan 23 is formed in a gap between the cross-flow fan 23 and the
10 casing portion 29 on a lower side of the cross-flow fan 23. In the present specification,
the “outer circumference of the cross-flow fan” means a cylindrical plane of a rotation
trajectory of radially outer end portions of the blades 23a provided in the cross-flow fan
23.
[0028]
15 The housing 21 has a suction port 20a and a blowout port 20b. In the present
embodiment, the suction port 20a and the blowout port 20b are formed in the outer shell
member 21b. The suction port 20a opens upward and extends in the axial direction. A
filter 40 is disposed in the suction port 20a. On the other hand, the blowout port 20b
opens forward and downward and extends in the axial direction. A wind direction
20 adjusting portion 25 is disposed in the blowout port 20b. The wind direction adjusting
portion 25 has a left-right wind direction vane 25a that adjusts a wind direction in the leftright direction Y and an up-down wind direction vane 25b that adjusts a wind direction in
the vertical direction Z.
[0029]
25 The air in the room is suctioned into an inside of the housing 21 from the suction
11
port 20a by drive of the cross-flow fan 23. The air suctioned into the housing 21 from
the suction port 20a passes through the filter 40 and then flows to the heat exchanger 22.
The filter 40 captures at least some of dust contained in the air passing through the filter
40. Furthermore, the air suctioned into the housing 21 by the cross-flow fan 23 is blown
5 into the room from the blowout port 20b. The air passing through the blowout port 20b
is blown into the room in the vertical direction Z and in the left-right direction Y separately
by the wind direction adjusting portion 25.
[0030]
The indoor unit 20 has a stabilizer 30. The stabilizer 30 is disposed inside the
10 housing 21. The stabilizer 30 is disposed on a lower side of the suction flow path F1 and
on an upper side of the blowout flow path F2. The stabilizer 30 separates the suction flow
path F1 and the blowout flow path F2 of the cross-flow fan 23 from each other. The
stabilizer 30 extends from a panel on a front surface side of the housing 21 toward the
lower side of the cross-flow fan 23. The stabilizer 30 is located on a lower side of the
15 first heat exchanger 22a.
[0031]
The stabilizer 30 includes a top surface 35b located on the upper side of the
blowout flow path F2. The top surface 35b of the present embodiment faces the lower
side. The top surface 35b is provided with the left-right wind direction vane 25a and the
20 up-down wind direction vane 25b.
[0032]
FIG. 4 is a perspective view of the stabilizer 30.
The stabilizer 30 is a resin molded product. The stabilizer 30 has a tongue
portion 35, a first protrusion portion 31, a second protrusion portion 32, and a side plate
25 portion 39. The tongue portion 35, the second protrusion portion 32, and the second
12
protrusion portion 32 extend over an entire axial length of the cross-flow fan 23. That is,
right end portions of the tongue portion 35, the second protrusion portion 32, and the
second protrusion portion 32 are located on the right side (+Y side) with respect to a right
end portion of the cross-flow fan 23. Left end portions of the tongue portion 35, the
5 second protrusion portion 32, and the second protrusion portion 32 are located on the left
side (-Y side) with respect to a left end portion of the cross-flow fan 23.
[0033]
As shown in FIG. 3, the tongue portion 35 is disposed with a gap from an outer
circumferential surface of the cross-flow fan 23. The tongue portion 35 has a facing
10 surface 35a that is disposed to face the cross-flow fan 23. The tongue portion 35 extends
along the outer circumferential surface of the cross-flow fan 23.
[0034]
The tongue portion 35 is provided with the facing surface 35a that faces the crossflow fan 23. The facing surface 35a faces an inner side in the radial direction. The
15 facing surface 35a extends in the axial direction in a uniform shape.
[0035]
The tongue portion 35 has an end portion 35c located closer to a blowout flow
path F2. In the following description, the end portion of the tongue portion 35 closer to
the blowout flow path F2 is simply referred to as an end portion 35c. The end portion
20 35c forms a curved surface that smoothly curves between the facing surface 35a and the
top surface 35b of the blowout port 20b. As shown in FIG. 4, a plurality of slits 35s
arranged in the axial direction are provided in the end portion 35c of the tongue portion 35.
[0036]
FIG. 5 is a partially enlarged view of FIG. 3.
25 The first protrusion portion 31 protrudes from the facing surface 35a of the tongue
13
portion 35 toward the cross-flow fan 23. Similarly, the second protrusion portion 32
protrudes from the facing surface 35a of the tongue portion 35 toward the cross-flow fan
23. The second protrusion portion 32 is located closer to the blowout flow path F2 than
the first protrusion portion 31.
5 [0037]
The tongue portion 35 and the first protrusion portion 31 according to the present
embodiment are each plate-shaped. That is, the first protrusion portion 31 has a rib shape
that extends from the tongue portion 35. Therefore, it is possible to suppress a local
increase in thickness of the tongue portion 35 at a connection portion with the first
10 protrusion portion 31. Therefore, in a case where the tongue portion 35 is manufactured
by die molding, the generation of a sink mark in the tongue portion 35 during the molding
can be suppressed, and as a result, dimensional accuracy of each portion of the stabilizer
30 can be increased.
[0038]
15 In addition, in the present embodiment, a recess portion 36 is provided between
the first protrusion portion 31 and the tongue portion 35. The recess portion 36 is a space
surrounded by the first protrusion portion 31 and the tongue portion 35. By forming the
recess portion 36 between the first protrusion portion 31 and the tongue portion 35, rigidity
of the first protrusion portion 31 and the tongue portion 35 can be increased.
20 [0039]
In addition, the recess portion 36 according to the present embodiment opens
toward the upper side. Therefore, condensation water generated in the housing 21 can be
retained in the recess portion 36, and even in a case where the condensation water is
generated in the housing 21, dripping of the condensation water into the room from the
25 blowout port 20b can be suppressed. Furthermore, the recess portion 36 of the present
14
embodiment is disposed directly below a front end (end portion on the +X side) of the
cross-flow fan 23. Therefore, the recess portion 36 can efficiently receive the
condensation water dripped from the front end of the cross-flow fan 23.
[0040]
5 The second protrusion portion 32 of the present embodiment has a triangular
shape as viewed in the axial direction of the cross-flow fan 23. That is, the second
protrusion portion 32 is constituted by two surfaces, that is, a flat second rectifying surface
(rectifying surface) 32a facing the blowout flow path F2 and a flat opposite side surface
32b facing the suction flow path F1. As will be described below, the second protrusion
10 portion 32 has a lower protruding height than the first protrusion portion 31. Therefore,
by causing the second protrusion portion 32 to have a triangular shape, it is easier to make
the thickness of the tongue portion 35 uniform compared to a case where the second
protrusion portion 32 has a plate shape like the first protrusion portion 31. According to
the present embodiment, the generation of a sink mark in the second protrusion portion 32
15 after the molding can be suppressed, and the dimensional accuracy of each portion of the
stabilizer 30 can be increased.
[0041]
FIGS. 6 and 7 are schematic diagrams showing circulating vortices V1 and V2
formed inside the housing 21 by the cross-flow fan 23 and the stabilizer 30. FIG. 6 is a
20 diagram showing a first circulating vortex V1 formed in a case where a ventilation
resistance of the suction port 20a is high. On the other hand, FIG. 7 is a diagram showing
a second circulating vortex V2 formed during a steady state in which a sufficient air volume
is secured in the suction flow path F1.
[0042]
25 In the following description, a state in which the first circulating vortex V1 as
15
shown in FIG. 6 is formed is referred to as a first state, and a state in which the second
circulating vortex V2 as shown in FIG. 7 is formed is referred to as a second state.
[0043]
As shown in FIGS. 6 and 7, the circulating vortices V1 and V2 are vertex-like
5 winds that pass through the inside of the cross-flow fan 23 and between the cross-flow fan
23 and the tongue portion 35. The circulating vortices V1 and V2 rotate clockwise as
viewed from the right side (+Y side). In addition, inside the housing 21, the circulating
vortices V1 and V2 are formed, and a flow from the suction flow path F1 across the inside
of the cross-flow fan 23 to the blowout flow path F2 is formed.
10 [0044]
A blowout region A is provided between the circulating vortices V1 and V2 and
the casing portion 29. The blowout region A is a region extending in the front-rear
direction and the left-right direction Y of the blowout flow path F2. The air passing
through the blowout region A among the air discharged from the cross-flow fan 23 flows
15 into the room from the blowout port 20b. On the other hand, the air that passes through
a front side (+X side) of the blowout region A of the air discharged from the cross-flow fan
23 circulates inside and outside the cross-flow fan 23 as the circulating vortices V1 and
V2.
[0045]
20 In the indoor unit 20 shown in FIG. 3, dust is continuously deposited on the filter
40 as the operation time increases until the filter 40 is cleaned. In this case, the ventilation
resistance of the suction port 20a increases, and a pressure of the suction flow path F1
decreases. The first state shown in FIG. 6 appears in a case where the pressure of the
suction flow path F1 decreases. On the other hand, the second state appears in a case
25 where the ventilation resistance of the suction port 20a is sufficiently low and the pressure
16
of the suction flow path F1 can be sufficiently maintained.
[0046]
As shown in FIG. 6, the first circulating vortex V1 in the first state is larger than
the second circulating vortex V2, and the blowout region A is narrowed in the front-rear
5 direction. Furthermore, in the first state, since the pressure of the suction flow path F1
decreases, the air in the room flows back into the housing 21 via the blowout port 20b and
is easily drawn into the first circulating vortex V1. In a case where the back flow occurs,
a blowing efficiency deteriorates. Furthermore, in a case where a back flow occurs during
the cooling operation, humid indoor air comes into contact with the cross-flow fan 23
10 having a low temperature, and condensation occurs on the blades 23a of the cross-flow fan
23.
[0047]
According to the present embodiment, the first protrusion portion 31 is provided
on the facing surface 35a of the tongue portion 35. The first protrusion portion 31
15 functions as a starting point 8a on the suction flow path F1 side of the first circulating
vortex V1 that increases as the ventilation resistance increases. That is, the air of the first
circulating vortex V1 flows from the blowout flow path F2 side to the suction flow path
F1 side along the facing surface 35a of the tongue portion 35, hits the first protrusion
portion 31, is blown up to the upper side, and enters the inside of the cross-flow fan 23.
20 According to the present embodiment, a position of the starting point 8a of the first
circulating vortex V1 in the case where the ventilation resistance increases can be
stabilized. This can suppress the narrowing of the blowout region A of the first
circulating vortex V1 (-X side), thereby suppressing the back flow of the indoor air from
the blowout port 20b. As a result, not only can the blowing efficiency by the cross-flow
25 fan 23 be enhanced, but also the occurrence of condensation on the blades 23a of the cross-
17
flow fan 23 during the cooling operation can be suppressed.
[0048]
The first protrusion portion 31 of the present embodiment extends over the entire
axial length of the cross-flow fan 23. Therefore, the starting point 8a of the first
5 circulating vortex V1 can be set to the same position at any location in the axial direction.
That is, according to the present embodiment, the first circulating vortex V1 having the
same shape can be stably formed at any position in the axial direction.
[0049]
As shown in FIG. 7, in the second state in which the pressure of the suction flow
10 path F1 is sufficiently high, the suction flow path F1 is widely formed in the vertical
direction Z. Therefore, the second circulating vortex V2 is smaller than the first
circulating vortex V1, and the blowout region A is widened in the front-rear direction. In
this case, in a case where only the first protrusion portion 31 is provided on the facing
surface 35a of the tongue portion 35, a circulating vortex collides head-on with the end
15 portion 35c of the tongue portion 35 and causes a large pressure fluctuation. Such a
pressure fluctuation causes a rotation sound of the cross-flow fan 23.
[0050]
According to the present embodiment, the second protrusion portion 32 is
provided on the facing surface 35a of the tongue portion 35 in addition to the first
20 protrusion portion 31. The second protrusion portion 32 is located closer to the blowout
flow path F2 than the first protrusion portion 31. The second protrusion portion 32
functions as a starting point 8b on the suction flow path F1 side of the second circulating
vortex V2. That is, the air of the second circulating vortex V2 flows from the blowout
flow path F2 side to the suction flow path F1 side along the facing surface 35a of the tongue
25 portion 35, hits the second protrusion portion 32, is blown up to the upper side, and enters
18
the inside of the cross-flow fan 23. According to the present embodiment, the starting
point 8b of the second circulating vortex V2 can be stabilized on the blowout flow path F2
side with respect to the first circulating vortex V1. Accordingly, the air of the second
circulating vortex V2 is likely to flow along the facing surface 35a of the tongue portion
5 35 without colliding with the end portion 35c of the tongue portion 35, and the pressure
fluctuation in the vicinity of the end portion 35c of the tongue portion is reduced, so that
the rotation sound of the cross-flow fan 23 can be reduced.
[0051]
The second protrusion portion 32 according to the present embodiment extends
10 over the entire axial length of the cross-flow fan 23. Therefore, the starting point 8b of
the second circulating vortex V2 can also be the same position at any location in the axial
direction. That is, according to the present embodiment, the second circulating vortex V2
having the same shape can be stably formed at any position in the axial direction.
[0052]
15 As shown in FIG. 5, a first gap C1 between the first protrusion portion 31 and the
cross-flow fan 23 is smaller than a second gap C2 between the second protrusion portion
32 and the cross-flow fan 23 (C1 < C2). That is, a tip of the first protrusion portion 31 is
disposed closer to the cross-flow fan 23 than a tip of the second protrusion portion 32. A
“distance between the protrusion portion and the cross-flow fan” means a “distance
20 between the protrusion portion and the outer circumference of the cross-flow fan (that is,
the rotation trajectory of radially outer end portions of the blades)”.
[0053]
The first circulating vortex V1 in the first state flows along the facing surface 35a
of the tongue portion 35, hits the second protrusion portion 32 after crossing the first
25 protrusion portion 31, and is blown up to the upper side. By causing the second gap C2
19
to be larger than the first gap C1, the first circulating vortex V1 can easily pass through
between the first protrusion portion 31 and the cross-flow fan 23. In addition, by causing
the first gap C1 to be smaller than the second gap C2, the first circulating vortex V1 can
easily hit the first protrusion portion 31, and the first protrusion portion 31 can function as
5 the starting point 8a of the first circulating vortex V1. On the other hand, since the second
circulating vortex V2 in the second state is a relatively small vortex, it is difficult for the
second circulating vortex V2 to cross the second protrusion portion 32 even in a case where
the second gap C2 is relatively wide, and the second circulating vortex V2 hits the second
protrusion portion 32 and is blown up to the upper side.
10 [0054]
As shown in FIG. 5, in the present embodiment, a difference (C2 - C1) between
the first gap C1 and the second gap C2 is preferably 0.5% or more of a diameter of the
cross-flow fan 23. As an example, in a case where an outer diameter of the cross-flow
fan 23 is 106 mm, the difference between the first gap C1 and the second gap C2 is
15 preferably 0.6 mm or more. By setting the first gap C1 and the second gap C2 in such a
relationship, the first circulating vortex V1 can be stably formed in the first state, and the
second circulating vortex V2 can be stably formed in the second state.
[0055]
In the present embodiment, the first gap C1 is the narrowest gap between the
20 stabilizer 30 and the cross-flow fan 23. In addition, the second gap C2 is the second
narrowest gap between the stabilizer 30 and the cross-flow fan 23. That is, portions of
the tongue portion 35 except the first protrusion portion 31 and the second protrusion
portion 32 are not closer to the cross-flow fan 23 than the first protrusion portion 31 and
the second protrusion portion 32. According to the present embodiment, functioning of
25 the portions of the tongue portion 35 other than the first protrusion portion 31 and the
20
second protrusion portion 32 as the starting point can be suppressed, and the starting point
of the circulating vortex can be easily controlled by the first protrusion portion 31 and the
second protrusion portion 32.
[0056]
5 As shown in FIG. 5, an imaginary line connecting the rotation axis R of the crossflow fan 23 and the tip of the first protrusion portion 31 is defined as a first imaginary line
L1 as viewed in the axial direction of the cross-flow fan 23. In addition, an imaginary
line connecting the rotation axis R and the tip of the second protrusion portion 32 is defined
as a second imaginary line L2. Furthermore, an imaginary line connecting the rotation
10 axis R and the end portion 35c of the tongue portion 35 is defined as a third imaginary line
L3.
[0057]
According to the present embodiment, a ratio of an angle α between the first
imaginary line L1 and the second imaginary line L2 to an angle γ between the first
15 imaginary line L1 and the third imaginary line L3 is larger than 50%. That is, the second
protrusion portion 32 is disposed between the end portion 35c of the tongue portion 35 and
the first protrusion portion 31 to be biased toward an end portion 35c side of the tongue
portion 35.
[0058]
20 In a case where the second protrusion portion 32 is disposed to be biased toward
a first protrusion portion 31, the second circulating vortex V2 is likely to collide with the
end portion 35c of the tongue portion 35 in the second state, and an effect of reducing the
pressure fluctuation in the vicinity of the end portion 35c of the tongue portion 35 cannot
be sufficiently obtained. According to the present embodiment, by disposing the second
25 protrusion portion 32 to be biased toward the end portion 35c side of the tongue portion
21
35, the starting point 8b of the second circulating vortex V2 can be disposed sufficiently
to the rear side (-X side). Accordingly, the air of the second circulating vortex V2 can
easily flow along the facing surface 35a of the tongue portion 35.
[0059]
5 In addition, the ratio of the angle α between the first imaginary line L1 and the
second imaginary line L2 to the angle γ between the first imaginary line L1 and the third
imaginary line L3 is preferably less than 62%. In a case where the ratio of the angle α to
the angle γ is too large, the second circulating vortex V2 formed in the second state is
biased to the rear side (-X side) too much, the blowout region A is narrowed in the front10 rear direction, and the air volume passing through the blowout flow path F2 is reduced,
which may deteriorate aerodynamic performance. According to the present embodiment,
by setting the ratio of the angle α to the angle γ to be less than 62%, a width of the blowout
region A can be sufficiently secured, and the air volume of the blowout flow path F2 can
be sufficiently secured.
15 [0060]
The first protrusion portion 31 has a first rectifying surface 31a that faces the
blowout flow path F2. The first rectifying surface 31a is inclined toward the suction flow
path F1 toward a tip side of the first protrusion portion 31. Furthermore, the first
rectifying surface 31a of the present embodiment has a first inclined portion 31e and a
20 second inclined portion 31f, which have different inclination angles from each other. The
first inclined portion 31e is disposed on a root side of the first protrusion portion 31, and
the second inclined portion 31f is disposed on a tip side of the first protrusion portion 31.
That is, the second inclined portion 31f is located closer to the tip side of the first protrusion
portion 31 than the first inclined portion 31e.
25
22
[0061]
The inclination angle of the first inclined portion 31e with respect to the first
imaginary line (imaginary line) L1 extending from the rotation axis R of the cross-flow fan
23 toward the first inclined portion 31e in the radial direction is referred to as a first
5 inclination angle θ1. In addition, the inclination angle of the second inclined portion 31f
with respect to the first imaginary line L1 extending from the rotation axis R toward the
second inclined portion 31f in the radial direction is referred to as a second inclination
angle θ2. The first inclination angle θ1 and the second inclination angle θ2 are the
inclination angles of the first inclined portion 31e and the second inclined portion 31f with
10 respect to the radial direction of the rotation axis R.
[0062]
In the present embodiment, the first inclination angle θ1 and the second
inclination angle θ2 are each an acute angle. Therefore, the first rectifying surface 31a of
the first protrusion portion 31 is inclined at an acute angle with respect to the radial
15 direction toward the suction flow path F1 over an entire region from the root side to the tip
side.
[0063]
In a case where the first rectifying surface 31a is parallel to the radial direction of
the rotation axis R or is inclined toward the blowout flow path F2, there is a concern that
20 the first circulating vortex V1 collides with the first rectifying surface 31a, causing a large
pressure fluctuation, and increasing the rotation sound of the cross-flow fan 23.
According to the present embodiment, since the first rectifying surface 31a is inclined at
an acute angle with respect to the radial direction of the rotation axis R toward the suction
flow path F1, the first circulating vortex V1 can be smoothly guided to the inside of the
25 cross-flow fan 23 at the first protrusion portion 31.
23
[0064]
In the present embodiment, the second inclination angle θ2 is larger than the first
inclination angle θ1. That is, the second inclined portion 31f has a larger inclination angle
with respect to the radial direction of the cross-flow fan 23 than the first inclined portion
5 31e. Therefore, the first protrusion portion 31 steeply rises from the facing surface 35a
in the first inclined portion 31e, and gently inclines toward the rotation direction of the
cross-flow fan 23 in the second inclined portion 31f on the tip side.
[0065]
As described above, the air of the first circulating vortex V1 passes through
10 between the facing surface 35a of the tongue portion 35 and the outer circumference of the
cross-flow fan 23. In addition, the air of the first circulating vortex V1 hits the first
protrusion portion 31 after crossing the second protrusion portion 32. The air of the first
circulating vortex V1 passes through a region that is biased toward the cross-flow fan 23
than the tip of the second protrusion portion 32 by crossing the second protrusion portion
15 32. Therefore, the air of the first circulating vortex V1 is more likely to hit a region of
the first rectifying surface 31a of the first protrusion portion 31, which is close to the crossflow fan 23 (that is, the second inclined portion 31f), and is less likely to hit the first
inclined portion 31e located on the root side of the first protrusion portion 31.
[0066]
20 According to the present embodiment, by forming the first inclined portion 31e
into the steep shape, the first protrusion portion 31 can be reduced in the front-rear direction.
In addition, according to the present embodiment, since the first rectifying surface 31a has
a bent shape on the tip side, the rigidity of the first protrusion portion 31 can be increased
compared to a case where the entire first rectifying surface 31a is inclined at a uniform
25 inclination angle.
24
[0067]
The second protrusion portion 32 has the second rectifying surface 32a that faces
the blowout flow path F2. The second rectifying surface 32a is inclined toward the
suction flow path F1 toward a tip side of the second protrusion portion 32. An inclination
5 angle of the second rectifying surface 32a with respect to the second imaginary line
(imaginary line) L2 extending in the radial direction from the rotation axis R of the crossflow fan 23 toward the second rectifying surface 32a is referred to as a third inclination
angle θ3. The first inclination angle θ1 and the second inclination angle θ2 are the
inclination angles of the second rectifying surface 32a with respect to the radial direction
10 of the rotation axis R. In the present embodiment, the second rectifying surface 32a of
the second protrusion portion 32 is inclined at an acute angle with respect to the radial
direction of the rotation axis R over an entire region from a root side to the tip side.
[0068]
In a case where the second rectifying surface 32a is parallel to the radial direction
15 of the rotation axis R or is inclined toward the blowout flow path F2, there is a concern
that the second circulating vortex V2 collides with the second rectifying surface 32a,
causing a large pressure fluctuation, and increasing the rotation sound of the cross-flow
fan 23. According to the present embodiment, since the second rectifying surface 32a is
inclined at an acute angle with respect to the radial direction of the rotation axis R toward
20 the suction flow path F1, the first circulating vortex V1 can be smoothly guided to the
inside of the cross-flow fan 23 at the second protrusion portion 32.
[0069]
As described above, each configuration and each method described in the present
specification can be combined as appropriate within the scope in which all of these do not
25 contradict each other.
25
[0070]
For example, in the embodiment described above, a case where the suction port
20a is disposed on the upper side and the blowout port 20b is disposed on the lower side
with respect to the cross-flow fan 23 has been described. However, the disposition of the
5 suction port 20a and the blowout port 20b with respect to the cross-flow fan 23 is not
limited to the embodiment.
[Reference Signs List]
[0071]
10: Outdoor unit
10 21: Housing
22: Heat exchanger
20: Indoor unit
20a: Suction port
20b: Blowout port
15 23: Cross-flow fan
30: Stabilizer
31: First protrusion portion
31a: First rectifying surface
31e: First inclined portion
20 31f: Second inclined portion
32: Second protrusion portion
32a: Second rectifying surface (rectifying surface)
32b: Opposite side surface
35: Tongue portion
25 35a: Facing surface
26
35c: End portion
36: Recess portion
100: Air conditioner
C1: First gap
5 C2: Second gap
F1: Suction flow path
F2: Blowout flow path
L1: First imaginary line (imaginary line)
L2: Second imaginary line (imaginary line)
10 L3: Third imaginary line (imaginary line)
L4: Imaginary line
R: Rotation axis
α, γ: Angle

WE CLAIM:
[Claim 1]
An indoor unit of an air conditioner, comprising:
a heat exchanger;
5 a cross-flow fan that rotates around a rotation axis;
a housing that includes a suction port and a blowout port and that accommodates
the heat exchanger and the cross-flow fan therein; and
a stabilizer that separates a suction flow path and a blowout flow path of the crossflow fan from each other,
10 wherein the stabilizer includes
a tongue portion that extends along an outer circumferential surface of the crossflow fan and that has a facing surface facing the cross-flow fan,
a first protrusion portion that protrudes from the facing surface toward the crossflow fan, and
15 a second protrusion portion that protrudes from the facing surface toward the
cross-flow fan and that is located closer to the blowout flow path than the first protrusion
portion.
[Claim 2]
The indoor unit according to Claim 1,
20 wherein a first gap between the first protrusion portion and the cross-flow fan is
smaller than a second gap between the second protrusion portion and the cross-flow fan.
[Claim 3]
The indoor unit according to Claim 2,
wherein a difference between the first gap and the second gap is 0.5% or more of
25 a diameter of the cross-flow fan.
28
[Claim 4]
The indoor unit according to any one of Claims 1 to 3,
wherein, as viewed in an axial direction of the cross-flow fan, when an imaginary
line connecting the rotation axis and a tip of the first protrusion portion is referred to as a
5 first imaginary line, an imaginary line connecting the rotation axis and a tip of the second
protrusion portion is referred to as a second imaginary line, and an imaginary line
connecting the rotation axis and an end portion of the tongue portion closer to the blowout
flow path is referred to as a third imaginary line, a ratio of an angle between the first
imaginary line and the second imaginary line to an angle between the first imaginary line
10 and the third imaginary line is larger than 50%.
[Claim 5]
The indoor unit according to any one of Claims 1 to 4,
wherein the first protrusion portion has a first rectifying surface that faces the
blowout flow path and is inclined toward the suction flow path toward a tip side of the first
15 protrusion portion,
the second protrusion portion has a second rectifying surface that faces the
blowout flow path and that is inclined toward the suction flow path toward a tip side of the
second protrusion portion, and
the first rectifying surface and the second rectifying surface are each inclined
20 toward the suction flow path at an acute inclination angle with respect to a radial direction
of the rotation axis.
[Claim 6]
The indoor unit according to Claim 5,
wherein the first rectifying surface has a first inclined portion and a second
25 inclined portion located closer to the tip side of the first protrusion portion than the first
29
inclined portion, and
an inclination angle of the second inclined portion with respect to the radial
direction is larger than an inclination angle of the first inclined portion with respect to the
radial direction.
5 [Claim 7]
The indoor unit according to any one of Claims 1 to 6,
wherein the tongue portion and the first protrusion portion are plate-shaped, and
the stabilizer has a recess portion that is surrounded by the tongue portion and the
first protrusion portion 31 and opens upward.
10 [Claim 8]
The indoor unit according to any one of Claims 1 to 7,
wherein the second protrusion portion is constituted by a flat rectifying surface
facing the blowout flow path F2 and a flat opposite side surface facing the suction flow
path.
15 [Claim 9]
The indoor unit according to any one of Claims 1 to 8,
wherein the first protrusion portion and the second protrusion portion extend over
an entire axial length of the cross-flow fan.
30
[Claim 10]
An air conditioner comprising:
the indoor unit according to any one of Claims 1 to 9; and
an outdoor unit.