U.S. patent application number 13/196998 was filed with the patent office on 2012-02-09 for indoor unit of air-conditioning apparatus and air-conditioning apparatus.
This patent application is currently assigned to Mitsubishi Electric Corporation. Invention is credited to Tomoya FUKUI, Kunihiko KAGA, Takashi MATSUMOTO, Satoshi MICHIHATA, Takeshi MORI, Kenichi SAKODA, Mitsuhiro SHIROTA, Shinichi SUZUKI, Akira TAKAMORI, Yoshinori TANIKAWA, Shoji YAMADA.
Application Number | 20120031139 13/196998 |
Document ID | / |
Family ID | 44735810 |
Filed Date | 2012-02-09 |
United States Patent
Application |
20120031139 |
Kind Code |
A1 |
SHIROTA; Mitsuhiro ; et
al. |
February 9, 2012 |
INDOOR UNIT OF AIR-CONDITIONING APPARATUS AND AIR-CONDITIONING
APPARATUS
Abstract
An indoor unit includes a casing having a suction port formed on
an upper portion and a blow-out port on a lower side of a front
surface portion, an axial-flow or mixed-flow fan provided on the
downstream side of the suction port in the casing, and a heat
exchanger provided in the casing at a position on the downstream
side of the fan and on the upstream side of the blow-out port. The
heat exchanger includes a plurality of fins arranged side by side
with predetermined gaps therebetween and a plurality of
heat-transfer tubes penetrating through the plurality of fins. The
heat exchanger is configured in such a manner that the air-flow
resistance of an area facing the outer peripheral side of the fan
is larger than the air-flow resistance of an area facing a center
portion of the fan.
Inventors: |
SHIROTA; Mitsuhiro; (Tokyo,
JP) ; FUKUI; Tomoya; (Tokyo, JP) ; YAMADA;
Shoji; (Tokyo, JP) ; SAKODA; Kenichi; (Tokyo,
JP) ; KAGA; Kunihiko; (Tokyo, JP) ; MORI;
Takeshi; (Tokyo, JP) ; MICHIHATA; Satoshi;
(Tokyo, JP) ; TAKAMORI; Akira; (Tokyo, JP)
; SUZUKI; Shinichi; (Tokyo, JP) ; TANIKAWA;
Yoshinori; (Tokyo, JP) ; MATSUMOTO; Takashi;
(Tokyo, JP) |
Assignee: |
Mitsubishi Electric
Corporation
Chiyoda-ku
JP
|
Family ID: |
44735810 |
Appl. No.: |
13/196998 |
Filed: |
August 3, 2011 |
Current U.S.
Class: |
62/426 |
Current CPC
Class: |
F24F 1/0029 20130101;
F24F 1/0059 20130101; F24F 1/0033 20130101 |
Class at
Publication: |
62/426 |
International
Class: |
F25D 17/06 20060101
F25D017/06 |
Foreign Application Data
Date |
Code |
Application Number |
Aug 4, 2010 |
JP |
2010-175257 |
Claims
1. An indoor unit of an air-conditioning apparatus comprising: a
casing having a suction port formed on an upper portion and a
blow-out port formed on a lower side of a front surface portion; an
axial-flow or mixed-flow fan provided on the downstream side of the
suction port in the casing; and a heat exchanger provided in the
casing at a position on the downstream side of the fan and on the
upstream side of the blow-out port, wherein the heat exchanger
includes a plurality of fins arranged side by side with
predetermined gaps therebetween and a plurality of heat-transfer
tubes penetrating through the plurality of fins, and an air-flow
resistance of an area facing the outer peripheral side of the fan
is larger than an air-flow resistance of an area facing a center
portion of the fan.
2. The indoor unit of the air-conditioning apparatus of claim 1,
wherein the diameter of the heat-transfer tubes of the heat
exchanger arranged in the area facing the outer peripheral side of
the fan is larger than the diameter of the heat-transfer tubes
arranged in the area facing the center portion of the fan.
3. The indoor unit of the air-conditioning apparatus of claim 1,
wherein the distance between the adjacent heat-transfer tubes of
the heat exchanger arranged in the area facing the outer peripheral
side of the fan is smaller than those arranged in the area facing
the center portion of the fan.
4. The indoor unit of the air-conditioning apparatus of claim 1,
wherein R32 is used as a refrigerant.
5. The indoor unit of the air-conditioning apparatus of claim 4,
wherein the heat-transfer tube is a circular tube having a diameter
in a range from 3 mm to 7 mm.
6. The indoor unit of the air-conditioning apparatus of claim 4,
wherein the heat-transfer tube is a flat tube.
7. An indoor unit of an air-conditioning apparatus comprising: a
casing having a suction port formed on an upper portion and a
blow-out port formed on a lower side of a front surface portion; an
axial-flow or mixed-flow fan provided on the downstream side of the
suction port in the casing; and a heat exchanger provided in the
casing at a position on the downstream side of the fan and on the
upstream side of the blow-out port, wherein the heat exchanger
includes a plurality of fins arranged side by side with
predetermined gaps therebetween and a plurality of heat-transfer
tubes penetrating through the plurality of fins, the plurality of
heat-transfer tubes are circular tubes having a diameter in a range
from 3 mm to 7 mm, and R32 is used as a refrigerant.
8. An indoor unit of an air-conditioning apparatus comprising: a
casing having a suction port formed on an upper portion and a
blow-out port formed on a lower side of a front surface portion; an
axial-flow or mixed-flow fan provided on the downstream side of the
suction port in the casing; and a heat exchanger provided in the
casing at a position on the downstream side of the fan and on the
upstream side of the blow-out port, wherein the heat exchanger
includes a plurality of fins arranged side by side with
predetermined gaps therebetween and a plurality of heat-transfer
tubes penetrating through the plurality of fins; the plurality of
heat-transfer tubes are flat tubes, and R32 is used as a
refrigerant.
9. The indoor unit of the air-conditioning apparatus of claim 6,
wherein the heat exchanger is arranged so that the long sides of
the heat-transfer tubes agree with the directions of air flow.
10. The indoor unit of the air-conditioning apparatus of claim 1,
wherein the heat-transfer tubes and the fins are formed of aluminum
or aluminum alloy.
11. An air-conditioning unit comprising the indoor unit of claim 1.
Description
BACKGROUND OF THE INVENTION
[0001] 1. Field of the Invention
[0002] The present invention relates to an indoor unit having a fan
and a heat exchanger housed in a casing and an air-conditioning
apparatus having the indoor unit.
[0003] 2. Description of the Related Art
[0004] Conventionally, an indoor unit of an air-conditioning
apparatus having a fin and tube heat exchanger (a heat exchanger
having a plurality of fins arranged side by side with predetermined
gaps therebetween and a plurality of heat-transfer tubes provided
so as to penetrate through these fins) in a casing is known. An
example of the indoor unit of the conventional air-conditioning
apparatus as described above is one in which "a heat exchanger 4 is
provided so as to surround the front, top, and rear top of a fan
rotor 3. The heat exchanger 4 includes a number of radiating fins
attached to a heat-transfer tube which are folded back a plurality
of times at both left and right ends, and is configured to allow
air sucked from an upper inlet opening 10a and a front inlet
opening 11a by driving the fan rotor 3 to pass toward the fan rotor
3 and cause heat exchange with respect to a refrigerant passing
through the interior of the heat-transfer tube. The heat exchanger
4 is connected to a refrigerant piping from an outdoor unit via the
refrigerant piping." (see Japanese Unexamined Patent Application
Publication No. 2003-254552 (Paragraph 0004, FIG. 2)) has been
proposed.
[0005] In general, the heat exchanger is employed with most
material among each units which constitute the indoor unit of the
air-conditioning apparatus. As there is a current demand to save
resources and energy, downsizing the heat exchanger is therefore an
important issue.
SUMMARY OF THE INVENTION
[0006] In order to solve the above-described problem, it is an
object of the invention to provide an indoor unit of an
air-conditioning apparatus, in which a heat exchanger can be
downsized, and an air-conditioning apparatus having such an indoor
unit.
[0007] The indoor unit of the air-conditioning apparatus according
to the invention includes a casing having a suction port formed on
an upper portion and a blow-out port formed on a lower side of a
front surface portion, an axial-flow or mixed-flow fan provided on
the downstream side of the suction port in the casing, and a heat
exchanger provided in the casing at a position on the downstream
side of the fan and on the upstream side of the blow-out port. The
heat exchanger includes a plurality of fins arranged side by side
with predetermined gaps therebetween and a plurality of
heat-transfer tubes penetrating through a plurality of the fins.
The heat exchanger is configured in such a manner that the air-flow
resistance of an area facing an outer peripheral side of the fan is
larger than the air-flow resistance of an area facing a center
portion of the fan.
[0008] The air-conditioning apparatus according to the invention
includes the indoor unit described above.
[0009] In an axial-flow fan or a mixed-flow fan, the air volume
decreases the closer it becomes to the center portion of the fan
and, in contrast, increases the closer it becomes to the outer
peripheral side thereof. In other words, in the heat exchanger in
the area facing the axial-flow fan or a mixed-flow fan, the air
volume trying to pass through decreases as it approaches the area
facing the center portion of the fan and, in contrast, increases as
it approaches the area facing the outer peripheral side of the fan.
Therefore, the heat exchanger according to the invention is
configured to have a larger air-flow resistance in the range in
which the air volume trying to pass through increases (the area
facing the outer peripheral side of the fan) than in the range in
which the air volume trying to pass through decreases (the area
facing the center portion of the fan). Therefore, the wind
velocities (that is, the air volumes) in the respective ranges of
the heat exchanger are uniformized, so that the heat-exchange
capacity of the heat exchanger increases. Therefore, the heat
exchanger is downsized in the invention, so that resource saving
and energy saving of the indoor unit and the air-conditioning
apparatus provided with the indoor unit are achieved.
[0010] In particular, in the indoor unit according to the
invention, the fan is arranged on the upstream side of the heat
exchanger, and generation of a swirl flow or occurrence of
variations in wind velocity distribution of the air blown out from
the blow-out port is restrained. In the indoor unit as described
above, the height of the indoor unit increases, which may lead to a
restriction on installation. Therefore, the invention which
achieves a downsizing in the size of the heat exchanger is
specifically effective for the indoor unit according to the
invention in which the fan is arranged on the upstream side of the
heat exchanger.
BRIEF DESCRIPTION OF THE DRAWINGS
[0011] FIG. 1 is a vertical cross-sectional view illustrating an
indoor unit according to Embodiment 1 of the invention.
[0012] FIG. 2 is a perspective view illustrating the indoor unit
according to Embodiment 1 of the invention.
[0013] FIG. 3 is a perspective view of the indoor unit according to
Embodiment 1 of the invention when viewed from the front right
side.
[0014] FIG. 4 is a perspective view of the indoor unit according to
Embodiment 1 of the invention when viewed from the rear right
side.
[0015] FIG. 5 is a perspective view of the indoor unit according to
Embodiment 1 of the invention when viewed from the front left
side.
[0016] FIG. 6 is a perspective view illustrating a drain pan
according to Embodiment 1 of the invention.
[0017] FIG. 7 is a vertical cross-sectional view illustrating a dew
condensation forming position of the indoor unit according to
Embodiment 1 of the invention.
[0018] FIG. 8 is a configuration drawing illustrating a signal
processing device according to Embodiment 1 of the invention.
[0019] FIG. 9 is a vertical cross-sectional view illustrating
another example of the indoor unit of the air-conditioning
apparatus according to Embodiment 1 of the invention.
[0020] FIG. 10 is a vertical cross-sectional view illustrating
another example of the indoor unit according to Embodiment 1 of the
invention.
[0021] FIG. 11 is a vertical cross-sectional view illustrating
still another example of the indoor unit according to Embodiment 1
of the invention.
[0022] FIG. 12 is a vertical cross-sectional view illustrating
still another example of the indoor unit according to Embodiment 1
of the invention.
[0023] FIG. 13 is a vertical cross-sectional view illustrating
still another example of the indoor unit according to Embodiment 1
of the invention.
[0024] FIG. 14 is a vertical cross-sectional view illustrating the
indoor unit according to Embodiment 2 of the invention.
[0025] FIG. 15 is a vertical cross-sectional view illustrating the
indoor unit according to Embodiment 3 of the invention.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
[0026] Hereinafter, detailed embodiments of an air-conditioning
apparatus according to the invention (more specifically, an indoor
unit of the air-conditioning apparatus) will be described. In the
following embodiments, the invention will be described with a wall
indoor unit taken as an example. In the drawings showing respective
embodiments, part of the shapes or the sizes of each units (or the
components of each units) may be different.
Embodiment 1
<Basic Configuration>
[0027] FIG. 1 is a vertical cross-sectional view illustrating an
indoor unit (referred to as "indoor unit 100") of an
air-conditioning apparatus according to Embodiment 1 of the
invention. FIG. 2 is a perspective view illustrating the indoor
unit shown in FIG. 1. In the description of Embodiment 1 and other
embodiments described later, the left side in FIG. 1 is defined as
the front side of the indoor unit 100. Referring now to FIG. 1 and
FIG. 2, a configuration of the indoor unit 100 will be
described.
(General Configuration)
[0028] The indoor unit 100 supplies air-conditioned air to an area
to be air-conditioned such as an indoor space by utilizing a
refrigerating cycle circulating a refrigerant. The indoor unit 100
mainly includes a casing 1 formed with suction ports 2 for taking
in indoor air and a blow-out port 3 for supplying air-conditioned
air to the area to be air-conditioned, fans 20 housed in the casing
1 and configured to take in the indoor air from the suction ports 2
and blow out the air-conditioned air from the blow-out port 3, and
heat exchangers 50 disposed in air paths from the fans 20 to the
blow-out port 3 and configured to generate the air-conditioned air
by heat exchange between the refrigerant and the indoor air. In
these components, each of the air paths (an arrow Z in FIG. 1)
communicates with the interior of the casing 1. The suction ports 2
are formed so as to open at an upper portion of the casing 1. The
blow-out port 3 is formed so as to open at a lower portion of the
casing 1 (more specifically, on the lower side of a front surface
portion of the casing 1). The fans 20 are each disposed on the
downstream side of the suction ports 2 and the upstream side of the
heat exchangers 50, and, for example, axial-flow fans or mixed-flow
fans are employed.
[0029] Since the fans 20 are provided on the upstream side of the
heat exchangers 50 in the indoor unit 100 as configured above,
generation of a swirl flow of air blown out from the blow-out port
3 and occurrence of variation in wind velocity distribution can be
restrained in comparison with the indoor unit of the conventional
air-conditioning apparatus having the fan 20 at the blow-out port
3. Therefore, blowing of comfortable air to the area to be
air-conditioned is achieved. Since no complex structure such as a
fan is provided at the blow-out port 3, measures against dew
condensation formed at a boundary between warm air and cool air at
the time of a cooling operation can easily be implemented. In
addition, since a fan motor 30 is not exposed to air-conditioned
air, namely, cool air or warm air, a long operational life can be
provided.
(Fan)
[0030] In general, the indoor unit of the air-conditioning
apparatus has limitations in terms of installation space, so the
fan cannot be increased in size in many cases. Therefore, in order
to obtain a desired air volume, a plurality of fans of moderate
sizes are arranged in parallel. In the indoor unit 100 according to
Embodiment 1, three fans 20 are arranged in parallel along the
longitudinal direction of the casing 1 (that is, along the
longitudinal direction of the blow-out port 3) as shown in FIG. 2.
In order to obtain a desired heat-exchange capacity with the indoor
unit of the air-conditioning apparatus having typical dimensions,
three to four fans 20 are preferably provided. In the indoor unit
according to Embodiment 1, substantially equivalent air volumes can
be obtained from all of the fans 20 by configuring all of the fans
20 to have an identical shape and so as to operate all with the
same rotation speed.
[0031] In this configuration, by combining the number, the shape,
and the size of the fans 20 according to the required air volume
and the air-flow resistance in the interior of the indoor unit 100,
an optimal fan design for the indoor units 100 having various
specifications is achieved.
(Bell Mouth)
[0032] In the indoor unit 100 according to Embodiment 1, a
duct-like bell mouth 5 is arranged around each of the fans 20. The
bell mouth 5 is intended to guide intake air into and exhaust air
out of the fans smoothly. As shown in FIG. 2, for example, the bell
mouth 5 according to Embodiment 1 has a substantially circular
shape in plan view. In the vertical cross section, the bell mouth 5
according to Embodiment 1 has the following shape. An end portion
of an upper portion 5a has a substantially circular arc shape
extending outward and upward. A center portion 5b is a straight
portion of the bell mouth 5, having a constant diameter. An end
portion of a lower portion 5c has a substantially circular arc
shape extending outward and downward. An end portion (a circular
arc portion on the suction side) of the upper portion 5a of the
bell mouth 5 forms the suction port 2.
[0033] The bell mouth 5 may be formed integrally with, for example,
the casing 1 in order to reduce the number of components and
improve the strength. It is also possible, for example, to improve
maintainability by modularizing the bell mouth 5, the fan 20, and
the fan motor 30 so as to be detachably attachable to the casing
1.
[0034] In Embodiment 1, the end portion (the circular arc portion
on the suction side) of the upper portion 5a of the bell mouth 5 is
formed so as to have a uniform shape in terms of the
circumferential direction of an opening surface of the bell mouth
5. In other words, the bell mouth 5 does not have structures such
as a notch or a rib in the direction of rotation about an axis of
rotation 20a of the fan 20, and has a uniform shape in terms of
axial symmetry.
[0035] With the configuration of the bell mouth 5 as described
above, the end portion (the circular arc portion on the suction
side) of the upper portion 5a of the bell mouth 5 has a uniform
shape with respect to the rotation of the fan 20, and hence a
uniform flow of the suction flow of the fan 20 is also realized.
Therefore, the noise generated by a drift of the suction flow of
the fan 20 can be decreased.
(Partitioning Panel)
[0036] As shown in FIG. 2, the indoor unit 100 according to
Embodiment 1 is provided with partitioning panels 90 between the
adjacent fans 20. These partitioning panels 90 are installed
between the heat exchangers 50 and the fans 20. In other words, the
air paths between the heat exchangers 50 and the fans 20 are
divided into a plurality of air paths (three in Embodiment 1). The
partitioning panels 90 are arranged between the heat exchangers 50
and the fans 20, so each end portion that is in contact with the
heat exchanger 50 has a shape conforming to the shape of the heat
exchanger 50. More specifically, as shown in FIG. 1, the heat
exchanger 50 is arranged so as to form a substantially A-shape in a
vertical cross section from the front side to the back side of the
indoor unit 100 (that is, the vertical cross section when viewing
the indoor unit 100 from the right side, referred to as "right
vertical cross-section", hereinafter). Therefore, an end portion of
each of the partitioning panels 90 on the side of the heat
exchanger 50 also has a substantially A-shape.
[0037] The position of an end portion of each of the partitioning
panels 90 on the side of the fan 20 may be determined as follows,
for example. When the adjacent fans 20 are positioned sufficiently
away from each other to avoid influencing each other on the suction
side, the end portion of each of the partitioning panels 90 on the
side of the fan 20 may need only be extend to an exit surface of
the fan 20. However, in a case where the adjacent fans 20 are as
near to each other to influence each other on the suction side and,
in addition, in a case where the shape of the end portion (the
circular arc portion on the suction side) of the upper portion 5a
of the bell mouth 5 can be formed sufficiently large, the end
portion of each of the partitioning panels 90 on the side of the
fan 20 may extend up to the upstream side of the fan 20 (the
suction side) so that the adjacent air paths do not influence each
other (the adjacent fans 20 do not influence each other on the
suction side).
[0038] The partitioning panels 90 may be formed of various
materials. For example, the partitioning panels 90 may be formed of
a metal such as steel or aluminum. Also, for example, the
partitioning panels 90 may be formed of a resin. When the
partitioning panels 90 are formed of a material with a low melting
point such as a resin, however, since the heat exchangers 50 are
heated to high temperatures at the time of a heating operation,
formation of slight spaces between the partitioning panels 90 and
the heat exchangers 50 is recommended. When the partitioning panels
90 are formed of a material with a high melting point such as
aluminum or steel, the partitioning panels 90 may be arranged so as
to be in contact with the respective heat exchangers 50. If the
heat exchangers 50 are, for example, fin and tube heat exchangers,
the partitioning panels 90 may be inserted between the fins of the
heat exchangers 50.
[0039] As described above, the air path between the heat exchangers
50 and the fans 20 is divided into a plurality of air paths (three
in Embodiment 1). It is also possible to reduce the noise generated
in the ducts by providing sound-absorbing materials in these air
paths, that is, on the partitioning panels 90 or in the casing
1.
[0040] The divided air paths are each formed into a substantially
square shape of L1.times.L2. In other words, the widths of the
divided air paths are L1 and L2. Therefore, the air volume
generated by the fan 20 installed in the interior of the
substantially square shape of L1.times.L2, for example, reliably
passes through the heat exchanger 50 surrounded by an area defined
by L1 and L2 on the downstream side of the fan 20.
[0041] By dividing the air path in the casing 1 into the plurality
of air paths as described above, even when the flow field which is
generated by the fan 20 on the downstream side has a swirling
component, air blown out from each of the fans 20 is prevented from
moving freely in the longitudinal direction of the indoor unit 100
(the direction orthogonal to the plane of the paper of FIG. 1).
Therefore, the air blown out from the fan 20 can be made to pass
through the heat exchanger 50 in the area defined by L1 and L2 on
the downstream side of the fan 20. Consequently, variations in air
volume distribution of the air flowing into all the heat exchangers
50 in the longitudinal direction of the indoor unit 100 (the
direction orthogonal to the plane of the paper of FIG. 1) is
restrained, so that a high heat exchanging capacity can be
provided. Furthermore, by partitioning the interior of the casing 1
by using the partitioning panels 90, the mutual interference of the
swirl flows generated by the adjacent fans 20 can be prevented
between the fans 20 adjacent to each other. Therefore, an energy
loss of fluid due to the mutual interference of the swirl flows can
be prevented, and hence reduction of a pressure loss in the indoor
unit 100 is possible in addition to the improvement in the wind
velocity distribution. Each of the partitioning panels 90 does not
necessarily have to be formed of a single plate, and may be made up
of a plurality of plates. For example, the partitioning panel 90
may be divided into two parts on the side of a front side heat
exchanger 51 and on the side of a back side heat exchanger 55.
Needless to say, it is preferable that no gap be formed at a joint
portion between the respective plates which constitute the
partitioning panel 90. By dividing the partitioning panel 90 into a
plurality of plates, assemblability of the partitioning panels 90
is improved.
(Fan Motor)
[0042] The fan 20 is driven and rotated by the fan motor 30. The
fan motor 30 to be used may be either of an inner-rotor type or an
outer-rotor type. In the case of the fan motor 30 of the
outer-rotor type, a motor having a structure in which a rotor is
integrated with a boss 21 of the fan 20 (the rotor is held by the
boss 21) is also employed. By setting the dimensions of the fan
motor 30 to be smaller than the dimensions of the boss 21 of the
fan 20, loss of airflow generated by the fan 20 can be prevented.
In addition, by disposing the motor in the interior of the boss 21,
an axial dimension can also be reduced. With the easily detachable
and attachable structure of the fan motor 30 and the fan 20,
cleanability is also improved.
[0043] By using a Brushless DC motor which is relatively high in
cost as the fan motor 30, improvement in efficiency, elongation of
service life, and improvement in controllability are achieved.
Needless to say, however, a primary function of an air-conditioning
apparatus is achieved even when motors of other types are
employed.
[0044] A circuit for driving the fan motor 30 may be integrated
with the fan motor 30, or may be provided externally for
dust-proofing measures and fire prevention measures.
[0045] The fan motor 30 is attached to the casing 1 using a motor
stay 16. In addition, by configuring the fan motor 30 to be of a
box-type fan motor (in which the fan 20, a housing, and the fan
motor 30 are integrally modularized) used for cooling a CPU and
configuring the fan motor 30 so as to be detachably attached to the
motor stay 16, maintainability can be improved, and accuracy of tip
clearance of the fan 20 can also be improved.
[0046] A drive circuit of the fan motor 30 may be provided either
in the interior of or on the exterior of the fan motor 30.
(Motor Stay)
[0047] The motor stay 16 is provided with a fixing member 17 and
supporting members 18. The fixing member 17 is a member to which
the fan motor 30 is attached. The supporting members 18 are members
configured to fix the fixing member 17 to the casing 1. The
supporting members 18 are, for example, rod-shaped members, and
extend, for example, radially from an outer peripheral portion of
the fixing member 17. As shown in FIG. 1, the supporting members 18
according to Embodiment 1 are extend approximately
horizontally.
(Heat Exchanger)
[0048] The heat exchangers 50 of the indoor unit 100 according to
Embodiment 1 are arranged on the downstream sides of the fans 20.
Fin and tube heat exchangers are preferably used as the heat
exchangers 50. The heat exchangers 50 are each divided by a line of
symmetry 50a in the right vertical cross section as shown in FIG.
1. The line of symmetry 50a divides the area substantially in the
center in the horizontal direction of which the heat exchanger 50
is installed in this cross section. In other words, the front side
heat exchanger 51 is arranged on the front side (the left side in
the plane of the paper in FIG. 1) with respect to the line of
symmetry 50a and the back side heat exchanger 55 is arranged on the
back side (the right side in the plane of the paper in FIG. 1) with
respect to the line of symmetry 50a, respectively. The front side
heat exchanger 51 and the back side heat exchanger 55 are arranged
in the casing 1 so that the distance between the front side heat
exchanger 51 and the back side heat exchanger 55 increases in the
direction of an air current, that is, so that the cross-sectional
shape of the heat exchanger 50 forms a substantially inverted
V-shape in the right vertical cross section. In other words, the
front side heat exchanger 51 and the back side heat exchanger 55
are arranged so as to be inclined with respect to the direction of
the air current supplied from the fan 20.
[0049] In addition, the heat exchanger 50 is characterized in that
the air path area of the back side heat exchanger 55 is larger than
the air path area of the front side heat exchanger 51. In other
words, the heat exchanger 50 is arranged so that the air volume of
the back side heat exchanger 55 is larger than the air volume of
the front side heat exchanger 51. In Embodiment 1, the length of
the back side heat exchanger 55 in the longitudinal direction is
larger than the length of the front side heat exchanger 51 in the
longitudinal direction in the right vertical cross section.
Accordingly, the air path area of the back side heat exchanger 55
is larger than the air path area of the front side heat exchanger
51. The rest of the configuration (such as the lengths in the depth
direction in FIG. 1) of the front side heat exchanger 51 and that
of the back side heat exchanger 55 are the same. In other words,
the heat conduction area of the back side heat exchanger 55 is
larger than the heat conduction area of the front side heat
exchanger 51. Also, the axis of rotation 20a of the fan 20 is
arranged above the line of symmetry 50a.
[0050] With the configuration of the heat exchanger 50 as described
above, the generation of the swirl flow of the air blown out from
the blow-out port 3 and the occurrence of a variation in wind
velocity distribution can be restrained in comparison with the
indoor unit of the conventional air-conditioning apparatus having
the fan at the blow-out port. Also, with the configuration of the
heat exchanger 50 as described above, the air volume of the back
side heat exchanger 55 is larger than the air volume of the front
side heat exchanger 51. Because of this difference in air volume,
when air currents having passed through the front side heat
exchanger 51 and the back side heat exchanger 55 merge, the merged
air current is curved toward the front side (the side of the
blow-out port 3). Therefore, necessity to curve the airflow steeply
in the vicinity of the blow-out port 3 is eliminated, and hence the
pressure loss in the vicinity of the blow-out port 3 can be
reduced.
[0051] In the indoor unit 100 according to Embodiment 1, the air
current flowing out from the back side heat exchanger 55 flows in
the direction from the back side to the front side. Therefore, in
the indoor unit 100 according to Embodiment 1, the air current
after having passed the heat exchanger 50 can be curved more easily
than in the case where the heat exchanger 50 is arranged in a
substantially V-shape in the right vertical cross section.
[0052] The indoor unit 100 includes the plurality of fans 20, which
often results in an increase in weight. When the weight of the
indoor unit 100 increases, a wall surface strong enough for
installing the indoor unit 100 is required, which leads to a
restriction of installation. Therefore, reduction of weight of the
heat exchanger 50 is preferred. In addition, in the indoor unit
100, since the fans 20 are arranged on the upstream sides of the
heat exchangers 50, the height of the indoor unit 100 is increased,
which often leads to a restriction of installation. Therefore,
downsizing of the heat exchanger 50 is preferred.
[0053] Accordingly, in Embodiment 1, the fin and tube heat
exchanger is employed as the heat exchanger 50 (the front side heat
exchanger 51 and the back side heat exchanger 55) to achieve
downsize of the heat exchanger 50. More specifically, the heat
exchanger 50 according to Embodiment 1 includes a plurality of fins
56 arranged side by side with predetermined gaps therebetween and a
plurality of heat-transfer tubes 57 penetrating through the fins
56. In Embodiment 1, the fins 56 are arranged side by side in the
horizontal direction of the casing 1 (the direction orthogonal to
the plane of the paper of FIG. 1). In other words, the
heat-transfer tubes 57 penetrate through the fins 56 along the
horizontal direction of the casing 1 (the direction orthogonal to
the plane of the paper of FIG. 1). In Embodiment 1, in order to
improve heat-transfer efficiency of the heat exchanger 50, two rows
of the heat-transfer tubes 57 are arranged in the direction of air
flow of the heat exchanger 50 (the width direction of the fins 56).
The heat-transfer tubes 57 are arranged in a substantially zigzag
shape in right vertical cross section.
[0054] Downsizing of the heat exchanger 50 is achieved by
configuring the heat-transfer tubes 57 with circular tubes having a
small diameter (on the order of diameters ranging from 3 mm to 7
mm), and employing R32 as the refrigerant flowing through the
heat-transfer tubes 57 (the refrigerant used in the indoor unit 100
and in the air-conditioning apparatus having the indoor unit 100).
In other words, the heat exchanger 50 exchanges heat between the
refrigerant flowing in the interiors of the heat-transfer tubes 57
and the indoor air via the fins 56. Therefore, when the diameter of
the heat-transfer tubes 57 is reduced, with the same amount of
circulation of the refrigerant, the pressure loss of the
refrigerant is larger than that of the heat exchanger provided with
heat-transfer tubes having a large diameter. However, the latent
heat of evaporation of R32 is higher than that of R410A at the same
temperature, and hence the same capacity can be obtained with a
smaller amount of circulation of the refrigerant. Therefore, by
using R32, reduction of the amount of a refrigerant to be used is
made possible, and the pressure loss in the heat exchanger 50 can
be reduced. Therefore, by employing thin circular tubes as the
heat-transfer tubes 57, and using R32 as the refrigerant,
downsizing of the heat exchanger 50 is achieved.
[0055] Furthermore, in the heat exchanger 50 according to
Embodiment 1, a reduction in the weight of the heat exchanger 50 is
achieved by forming the fins 56 and the heat-transfer tubes 57 with
aluminum or aluminum alloy. And if the weight of the heat exchanger
50 does not cause a restriction of installation, the heat-transfer
tubes 57 may be formed of copper as a matter of course.
[0056] Although a decrease in the size and weight is attempted in
the heat exchanger 50 having the substantially inverted V-shape in
right vertical cross section in Embodiment 1, the shape of the heat
exchanger 50 is not limited thereto. The heat exchanger 50 made up
of the fins 56 and the heat-transfer tubes 57 may be formed as
shown below for example.
[0057] FIGS. 10 to 13 are vertical cross-sectional views showing
another example of the indoor unit according to Embodiment 1 of the
invention.
[0058] In right vertical cross section, for example, the heat
exchanger 50 made up of the fins 56 and the heat-transfer tubes 57
may be formed into a substantially N-shape (FIG. 10), a
substantially W-shape (FIG. 11), a substantially inverted N-shape
(FIG. 12), or a substantially M-shape (FIG. 13). In these cases, a
heat exchanger 51a and the heat exchanger 51b arranged on the front
side with respect to the line of symmetry 50a corresponds to the
front side heat exchanger 51. A heat exchanger 55a and a heat
exchanger 55b arranged on the back side with respect to the line of
symmetry 50a corresponds to the back side heat exchanger 55. With
the configuration of the heat exchanger 50 as in FIGS. 10 to 13,
the air volume passing through the heat exchanger 50 increases and
the heat-exchange capacity of the heat exchanger 50 is further
improved. Therefore, the heat exchanger 50 can further be
downsized.
(Finger Guard and Filter)
[0059] The indoor unit 100 according to Embodiment 1, a finger
guard 15 and a filter 10 are provided at the suction port 2. The
finger guard 15 is installed for the purpose of preventing the
rotating fan 20 from being touched. Therefore, the shape of the
finger guard 15 is arbitrary as long as the fan 20 is prevented
from being touched. For example, the shape of the finger guard 15
may be a lattice shape, or may be a circular shape made up of a
number of rings having different sizes. Alternatively, the finger
guard 15 may be formed either of materials such as resin or
metallic materials. However, when strength is required, it is
preferably formed of metal. The finger guard 15 is preferably
formed of materials and shapes as strong and thin as possible in
terms of reduction of air-flow resistance and retention of
strength. The filter 10 is provided for the purpose of preventing
dust from flowing into the interior of the indoor unit 100. The
filter 10 is provided in the casing 1 so as be detachable and
attachable. The indoor unit 100 according to Embodiment 1 includes
an automatic cleaning mechanism which cleans the filter 10
automatically.
(Wind Direction Control Vane)
[0060] The indoor unit 100 according to Embodiment 1 includes a
vertical wind direction control vane 70 (see FIG. 2) and a
horizontal wind-direction control vane (not shown), as a mechanism
which controls the blowing direction of the airflow at the blow-out
port 3.
(Drain Pan)
[0061] FIG. 3 is a perspective view of the indoor unit according to
Embodiment 1 of the invention when viewed from the front right
side. FIG. 4 is a perspective view of the same indoor unit when
viewed from the back right side. FIG. 5 is a perspective view of
the same indoor unit when viewed from the front left side. FIG. 6
is a perspective view illustrating a drain pan according to
Embodiment 1 of the invention. In order to facilitate understanding
of the shape of the drain pan, the right side of the indoor unit
100 is shown in cross section in FIG. 3 and FIG. 4, and the left
side of the indoor unit 100 is shown in cross section in FIG.
5.
[0062] Provided below a lower end portion of the front side heat
exchanger 51 (a front side end portion of the front side heat
exchanger 51) is a front side drain pan 110. Provided below a lower
end portion of the back side heat exchanger 55 (a back side end
portion of the back side heat exchanger 55) is a back side drain
pan 115. In Embodiment 1, the back side drain pan 115 and a back
side portion 1b of the casing 1 are integrally formed. In the back
side drain pan 115, connecting ports 116 to which a drain hose 117
is connected are provided on both a left side end portion and a
right side end portion. It is not necessary to connect the drain
hose 117 to both of the connecting ports 116, and the drain hose
117 may be connected to one of the connecting ports 116. For
example, when drawing of the drain hose 117 to the right side of
the indoor unit 100 is desired at the time of installation of the
indoor unit 100, the drain hose 117 is connected to the connecting
port 116 provided on the right side end portion of the back side
drain pan 115, and the connecting port 116 provided on the left
side end portion of the back side drain pan 115 may be closed with
a rubber cap or the like.
[0063] The front side drain pan 110 is arranged at a position
higher than the back side drain pan 115. Provided between the front
side drain pan 110 and the back side drain pan 115 on both of the
left side end portion and the right side end portion are drain
channels 111 which correspond to drain flow channels. The drain
channels 111 are each connected at an end portion on the front side
thereof to the front side drain pan 110, and are provided so as to
incline downward from the front side drain pan 110 toward the back
side drain pan 115. Also, formed at end portions of the drain
channels 111 on the back side are tongue portions 111a. The end
portions of the drain channels 111 on the back side are arranged so
as to extend over an upper surface of the back side drain pan
115.
[0064] When the indoor air is cooled by the heat exchangers 50 at
the time of cooling operation, dew condensation forms on the heat
exchangers 50. Then, dew on the front side heat exchanger 51 drops
from the lower end portion of the front side heat exchanger 51, and
is collected by the front side drain pan 110. Dew on the back side
heat exchanger 55 drops from the lower end portion of the back side
heat exchanger 55, and is collected by the back side drain pan
115.
[0065] Since the front side drain pan 110 is provided at a position
higher than the back side drain pan 115 in Embodiment 1, the drain
water collected by the front side drain pan 110 flows through the
drain channel 111 toward the back side drain pan 115. Then, the
drain water drops down from the tongue portion 111a of the drain
channel 111 to the back side drain pan 115, and is collected by the
back side drain pan 115. The drain water collected by the back side
drain pan 115 passes through the drain hose 117, and is drained to
the outside of the casing 1 (the indoor unit 100).
[0066] As in Embodiment 1, by providing the front side drain pan
110 at a position higher than the back side drain pan 115, the
drain water collected by both of the drain pans can be gathered in
the back side drain pan 115 (the drain pan arranged on the backmost
side of the casing 1). Therefore, by providing the connecting port
116 of the drain hose 117 in the back side drain pan 115, the drain
water collected in the front side drain pan 110 and the back side
drain pan 115 can be drained to the outside of the casing 1. When
performing maintenance (cleaning of the heat exchangers 50 and the
like) of the indoor unit 100 by opening the front side portion or
the like of the casing 1, there is, therefore, no need to detach
and attach the drain pan having the drain hose 117 connected
thereto, thus workability such as maintenance is improved.
[0067] Since the drain channels 111 are provided on both the left
side end portion and the right side end portion, even when the
indoor unit 100 is installed in an inclined state, the drain water
collected in the front side drain pan 110 can be guided reliably to
the back side drain pan 115. Since the connecting ports to which
the drain hoses 117 are to be connected are provided on both the
left side end portion and the right side end portion, the drawing
direction of the hose can be selected according to the conditions
of the indoor unit 100 in installation, so that workability when
installing the indoor unit 100 is improved. Also, since the drain
channels 111 are provided so as to extend over the back side drain
pan 115 (that is, since a connecting mechanism is not necessary
between the drain channel 111 and the back side drain pan 115),
attachment and detachment of the front side drain pan 110 is
facilitated, and hence maintainability is further improved.
[0068] It is also possible to connect the back side end of the
drain channels 111 to the back side drain pan 115 and arrange the
drain channels 111 so that the front side drain pan 110 extends
over the drain channels 111. In this configuration as well, the
same effects as the configuration in which the drain channels 111
are arranged so as to extend over the back side drain pan 115 are
achieved. The front side drain pan 110 does not necessarily have to
be provided at a higher position than the back side drain pan 115,
and the drain water collected in both drain pans can be drained
from the drain hose connected to the back side drain pan 115 even
when the front side drain pan 110 and the back side drain pan 115
are provided at the same level.
(Nozzle)
[0069] The indoor unit 100 according to Embodiment 1 is configured
in such a manner that an opening length dl of a nozzle 6 on the
suction side (a throttle length dl between the drain pans defined
by a portion between the front side drain pan 110 and the back side
drain pan 115) is defined to be larger than an opening length d2
(the length of the blow-out port 3) of the nozzle 6 on the blow-out
side. In other words, the nozzle 6 of the indoor unit 100 has
opening lengths which satisfy d1>d2.
[0070] The reason why the nozzle 6 is configured to have opening
lengths of d1>d2 is as follows. Since the value d2 affects the
distribution distance of the airflow, which is one of basic
functions of the indoor unit, the opening length d2 of the indoor
unit 100 according to Embodiment 1 is assumed to be a comparable
length with the blow-out port of the conventional indoor unit in
the description given below.
[0071] By setting the dimensions of the nozzle 6 in the vertical
cross section to be d1>d2, the air path is widened, and an angle
A of the heat exchanger 50 arranged on the upstream side (the angle
formed between the front side heat exchanger 51 an the back side
heat exchanger 55 on the downstream side of the heat exchanger 50)
can be widened. Therefore, the wind velocity distribution generated
in the heat exchanger 50 is reduced, and the air path of the
downstream side of the heat exchanger 50 can be widened, whereby
reduction of pressure loss in the entire indoor unit 100 can be
achieved. In addition, the deviation of the wind velocity
distribution generated in the vicinity of the inlet portion of the
nozzle 6 can be unified and guided to the blow-out port by the
effect of flow contraction.
[0072] For example, when d1=d2, the deviation of the wind velocity
distribution generated in the vicinity of the inlet portion of the
nozzle 6 (for example, a flow deviated toward the back side) is
reflected directly in the deviation of the wind velocity
distribution at the blow-out port 3. In other words, when d1=d2,
air is blown out from the blow-out port 3 still having the
deviation in the wind velocity distribution. When d1<d2 is
satisfied, for example, the contraction flow loss is increased when
airflows passed through the front side heat exchanger 51 and the
back side heat exchanger 55 merge in the vicinity of the inlet
portion of the nozzle 6. Therefore, when d1<d2 is satisfied, a
loss corresponding to the contraction flow loss is generated unless
otherwise a diffusion effect at the blow-out port 3 cannot be
obtained.
(ANC)
[0073] In the indoor unit 100 according to Embodiment 1, an active
silencing mechanism is provided as shown in FIG. 1.
[0074] More specifically, the silencing mechanism of the indoor
unit 100 according to Embodiment 1 includes a noise detection
microphone 161, a control speaker 181, a silencing effect detection
microphone 191, and a signal processing device 201. The noise
detection microphone 161 is a noise detection device configured to
detect an operation sound (noise) of the indoor unit 100 including
a blast sound of the fan 20. The noise detection microphone 161 is
arranged between the fan 20 and the heat exchanger 50. In
Embodiment 1, the noise detection microphone 161 is provided on the
front surface portion in the casing 1. The control speaker 181 is a
control sound output device configured to output a control sound
with respect to the noise. The control speaker 181 is arranged
below the noise detection microphone 161 and above the heat
exchanger 50. In Embodiment 1, the control speaker 181 is provided
on the front surface portion in the casing 1 so as to face the
center of the air path. The silencing effect detection microphone
191 is a silencing effect detection device configured to detect the
silencing effect using the control sound. The silencing effect
detection microphone 191, being intended to detect a noise coming
from the blow-out port 3, is provided in the vicinity of the
blow-out port 3. The silencing effect detection microphone 191 is
attached at a position avoiding the airflow so as not to be exposed
to the air coming out from the blow-out port 3. The signal
processing device 201 is a control sound generating device
configured to cause the control speaker 181 to output the control
sound on the basis of the results of detection by the noise
detection microphone 161 and the silencing effect detection
microphone 191.
[0075] FIG. 8 is a configuration drawing illustrating a signal
processing device according to Embodiment 1 of the invention.
Electric signals supplied from the noise detection microphone 161
and the silencing effect detection microphone 191 are amplified by
a microphone amplifier 151, and are converted from analogue signals
to digital signals by an A/D converter 152. The converted digital
signals are input to an FIR filter 158 and an LMS algorithm 159. In
the FIR filter 158, a control signal, which is corrected to cause a
noise with the same amplitude as and an opposite phase from the
detected noise by the noise detection microphone 161 when the noise
reaches a position where the silencing effect detection microphone
191 is installed, and is converted from a digital signal to an
analogue signal by an D/A converter 154, then is amplified by an
amplifier 155, and then is emitted as the control sound from the
control speaker 181.
[0076] In a case where the air-conditioning apparatus is in cooling
operation, for example, as shown in FIG. 7, the temperature in an
area B between the heat exchanger 50 and the blow-out port 3 is
lowered due to cool air, thereby causing dew condensation to appear
as water droplets from water vapor in the air. Therefore, in the
indoor unit 100, a water trap or the like (not shown) is attached
in the vicinity of the blow-out port 3 for preventing the water
droplets from coming out from the blow-out port 3. The area where
the noise detection microphone 161 and the control speaker 181 are
arranged, which is on the upstream side of the heat exchanger 50 is
not subjected to dew condensation, because it is located on the
upstream side of the area to be cooled by cool air.
[0077] Subsequently, a method of restraining an operating sound of
the indoor unit 100 will be described. The operating sound (noise)
including the blast sound of the fan 20 in the indoor unit 100 that
is detected by the noise detection microphone 161 attached between
the fan 20 and the heat exchanger 50 is converted into a digital
signal via the microphone amplifier 151 and the ND converter 152,
and is supplied to the FIR filter 158 and the LMS algorithm
159.
[0078] A tap coefficient of the FIR filter 158 is updated
sequentially by the LMS algorithm 159. The tap coefficient is
updated by the LMS algorithm 159 according to an expression 1 (h
(n+1)=h(n)+2 .mu.e(n).times.(n)), and is updated to an optimal tap
coefficient so as to cause an error signal e to approach zero.
[0079] In the expression shown above, h is a tap coefficient of the
filter, e is the error signal, x is a filter input signal, and .mu.
is a step size parameter, and the step size parameter .mu. is used
for controlling the update amount of the filter coefficient at
every sampling.
[0080] In this manner, the digital signal passed through the FIR
filter 158 whose tap coefficient is updated by the LMS algorithm
159 is converted into an analogue signal by the D/A converter 154,
is amplified by the amplifier 155, and is released into the air
path in the indoor unit 100 as the control sound from the control
speaker 181 attached between the fan 20 and the heat exchanger
50.
[0081] And the silencing effect detection microphone 191, attached
to a lower end of the indoor unit 100 on the outer wall of the
blow-out port 3 so as to avoid wind blown out from the blow-out
port 3, detects a sound which has been propagated from the fan 20
to the air path coming out from the blow-out port, the sound after
having been interfered by the control sound released from the
control speaker 181.
[0082] Since the sound detected by the silencing effect detection
microphone 191 is input to the error signal of the LMS algorithm
159 described above, the tap coefficient of the FIR filter 158 is
updated so as to cause the sound after the interference to approach
zero. Consequently, the noise in the vicinity of the blow-out port
3 can be restrained by the control sound having passed through the
FIR filter 158.
[0083] In this manner, in the indoor unit 100 to which an active
silencing method is applied, the noise detection microphone 161 and
the control speaker 181 are arranged between the fan 20 and the
heat exchanger 50, and the silencing effect detection microphone
191 is attached to a position avoiding the airflow from the
blow-out port 3. Therefore, since it is not necessary to attach
members required for active silencing to area B which is subjected
to dew condensation, water droplets dropping on the control speaker
181, the noise detection microphone 161, and the silencing effect
detection microphone 191 is prevented, and hence deterioration of
silencing capabilities or defects of the speaker or the microphone
can be prevented.
[0084] The positions where the noise detection microphone 161, the
control speaker 181, and the silencing effect detection microphone
191 are attached shown in Embodiment 1 are only examples. For
example, as shown in FIG. 9, the silencing effect detection
microphone 191 may be arranged between the fan 20 and the heat
exchanger 50 together with the noise detection microphone 161 and
the control speaker 181. Although the microphone is exemplified as
detecting means for detecting the noise or the silencing effect
after having cancelled the noise using the control sound, it may be
an acceleration sensor or the like for sensing vibrations of the
casing. Alternatively, it is also possible to understand the sound
as turbulence of air current, and detect the noise or the silencing
effect after having cancelled the noise by the control sound as
turbulence of the air current. In other words, a flow velocity
sensor which detects the air current or a hot-wire probe may be
used as the detecting means for detecting the noise or the
silencing effect after having cancelled the noise using the control
sound. It is also possible to detect the air current by increasing
a gain of the microphone.
[0085] Although the FIR filter 158 and the LMS algorithm 159 are
employed in the signal processing device 201 in Embodiment 1, any
adaptive signal processing circuit may be employed as long as it
causes the sound detected by the silencing effect detection
microphone 191 to approach zero, and also may be one in which a
filtered-X algorithm generally used in the active silencing method
is applicable. In addition, the signal processing device 201 may be
configured to generate the control signal using a fixed tap
coefficient instead of employing adaptive signal processing. And
further, the signal processing device 201 may be an analogue signal
processing circuit instead of the digital signal processing
circuit.
[0086] In addition, in Embodiment 1, the heat exchanger 50 disposed
to cool air which forms due condensation has been described, but
the invention can be applied also to a case where the heat
exchanger 50 of a level which does not cause dew condensation is
arranged, and has effects to prevent deterioration of performances
of the noise detection microphone 161, the control speaker 181, the
silencing effect detection microphone 191, and the like without
considering the presence or absence of occurrence of due
condensation due to the heat exchanger 50.
Embodiment 2
(Flat Tube)
[0087] In Embodiment 1, the heat-transfer tubes 57 are each formed
of a circular tube. The invention is not limited thereto, and the
heat-transfer tubes 57 can be formed of a flat tube as a matter of
course. In Embodiment 2, points which are different from Embodiment
1 described above will be described principally, and the same
components as Embodiment 1 are assigned with the same numbers.
[0088] FIG. 14 is a vertical cross-sectional view illustrating the
indoor unit according to Embodiment 2 of the invention.
[0089] The heat exchanger 50 according to Embodiment 2 includes
heat-transfer tubes 57 formed of a flat tube. The rest of the
configuration are the same as the heat exchanger 50 shown in
Embodiment 1. In Embodiment 2, R32 is employed as a refrigerant
flowing through the heat-transfer tubes 57 (the refrigerant used in
the indoor unit 100 and the air-conditioning apparatus having the
indoor unit 100) as in Embodiment 1.
[0090] The heat exchanger 50 in which the flat tube-shaped
heat-transfer tubes 57 are employed has a narrower flow channel for
the refrigerant in comparison with the heat exchanger in which the
circular heat-transfer tubes are employed. Therefore, the heat
exchanger 50 in which the flat tube-shaped heat-transfer tubes 57
are employed is subjected to a larger pressure loss of the
refrigerant in comparison with the heat exchanger in which the
circular heat-transfer tubes are employed in the same amount of
circulation of the refrigerant. However, the latent heat of
evaporation of R32 is higher than that of R410A at the same
temperature, and hence the same capacity can be achieved with a
smaller amount of circulation of the refrigerant. Therefore, by
using R32, reduction of the amount of a refrigerant to be used is
made possible, so that the pressure loss in the heat exchanger 50
can be reduced. Therefore, by employing the flat tubes as the
heat-transfer tubes 57, and using R32 as the refrigerant,
downsizing of the heat exchanger 50 is achieved.
[0091] The heat exchanger 50 in Embodiment 2 is arranged so that
the long sides of the heat-transfer tubes 57 agree with the
direction of the air flow. More specifically, the air-flow
directions of the heat exchanger 50 (the direction of air flowing
in the heat exchanger 50) when the fan 20 is driven are as
indicated by hollow arrows in FIG. 14. The heat exchanger 50 in
Embodiment 2 is arranged so that the long sides of the
heat-transfer tubes 57 agree with the directions of air flow.
Accordingly, the air-flow resistance of the heat exchanger 50 is
reduced, and hence a power of the fan 20 can be held down, thereby
reducing the power consumption of the fan 20. In addition, since
the air-flow resistance of the heat exchanger 50 is lowered, the
distances between the adjacent heat-transfer tubes 57 can be
reduced (narrowed). Therefore, the heat exchanger 50 can further be
downsized.
[0092] In the heat exchanger 50 according to Embodiment 2, the fin
56 and the heat-transfer tubes 57 may be also formed of aluminum or
aluminum alloy. Accordingly, weight reduction of the heat exchanger
50 is achieved.
Embodiment 3
(Density of Heat-Transfer Tubes)
[0093] The heat exchanger 50 may also be downsized with the
configuration of the heat exchanger 50 as described below. In
Embodiment 3, points which are different from Embodiment 1 and
Embodiment 2 described above will be described principally, and the
same components as in Embodiment 1 and Embodiment 2 are assigned
with the same numbers.
[0094] FIG. 15 is a vertical cross-sectional view illustrating the
indoor unit according to Embodiment 3 of the invention.
[0095] In the fan 20, which is an axial-flow fan or a mixed-flow
fan, the air volume decreases the closer it becomes to the center
portion of the fan and, in contrast, increases the closer it
becomes to the outer peripheral side thereof. In other words, in
the heat exchanger 50 in the area facing the fan 20, the air volume
trying to pass through decreases as it approaches an area facing
the center portion of the fan 20 and, in contrast, increases as it
approaches an area facing the outer peripheral side of the fan 20.
Therefore, the heat exchanger 50 according to Embodiment 3 is
configured to have a larger air-flow resistance in the range in
which the air volume trying to pass through is large (the area
facing the outer peripheral side of the fan 20) than in the range
in which the air volume trying to pass through is small (the area
facing the center portion of the fan 20).
[0096] More specifically, in the heat exchanger 50 according to
Embodiment 3 having a right vertical cross section in a
substantially inverted V-shape, the air-flow resistance increases
gradually from a back side end portion of the front side heat
exchanger 51 to a front side end portion of the front side heat
exchanger 51. Also, the air-flow resistance increases gradually
from the front side end portion of the back side heat exchanger 55
to the back side end portion of the back side heat exchanger 55. In
Embodiment 3, the air-flow resistance is adjusted by adjusting the
distance between the adjacent heat-transfer tubes 57. In other
words, in the heat exchanger 50 according to Embodiment 3 having
the right vertical cross section in the substantially inverted
V-shape, the distance between the adjacent heat-transfer tubes 57
decreases gradually from the back side end portion of the front
side heat exchanger 51 to the front side end portion of the front
side heat exchanger 51. Also, the distance between the adjacent
heat-transfer tubes 57 decreases gradually from the front side end
portion of the back side heat exchanger 55 to the back side end
portion of the back side heat exchanger 55.
[0097] With the configuration of the heat exchanger 50 as described
above, the wind velocities (that is, the air volumes) in the
respective ranges of the heat exchanger 50 is uniformized, so that
the heat-exchange capacity of the heat exchanger 50 increases.
Therefore, the heat exchanger 50 can be downsized.
[0098] In Embodiment 3, the air-flow resistance is adjusted by
adjusting the distance between the adjacent heat-transfer tubes 57.
However, the air-flow resistance may be adjusted by changing the
diameter of the heat-transfer tubes 57. In other words, in the heat
exchanger 50 according to Embodiment 3 having the right vertical
cross section in the substantially inverted V-shape, the diameter
of the heat-transfer tubes 57 may be increased gradually from the
back side end portion of the front side heat exchanger 51 to the
front side end portion of the front side heat exchanger 51. Also,
the diameter of the heat-transfer tubes 57 may be increased
gradually from the front side end portion of the back side heat
exchanger 55 to the back side end portion of the back side heat
exchanger 55.
[0099] It is not necessary to gradually increase the air-flow
resistance of the heat exchanger 50 from the area facing the center
portion of the fan 20 to the area facing the outer peripheral side
of the fan 20. For example, the air-flow resistance of the heat
exchanger 50 may be increased step by step from the area facing the
center portion of the fan 20 to the area facing the outer
peripheral side of the fan 20. In other words, what is essential is
that the air-flow resistance of the area facing the outer
peripheral side of the fan 20 is larger than the air-flow
resistance of the area facing the center portion of the fan 20.
[0100] The heat-transfer tubes 57 of the heat exchanger 50
according to Embodiment 3 may be formed of a circular tube having a
small diameter (diameters on the order from 3 mm to 7 mm) as shown
in Embodiment 1 or may be formed of a flat tube as shown in
Embodiment 2. In this case, by employing R32 as the refrigerant,
further downsizing of the heat exchanger 50 is achieved. In a case
of forming the heat-transfer tubes 57 with the flat tube, further
downsizing of the heat exchanger 50 is achieved by arranging the
heat exchanger 50 so that the long sides of the flat tubes agree
with the directions of air flow.
[0101] In the heat exchanger 50 according to Embodiment 3, the fin
56 and the heat-transfer tubes 57 may also be formed of aluminum or
aluminum alloy. Accordingly, weight reduction of the heat exchanger
50 is achieved.
REFERENCE SIGNS LIST
[0102] casing, 1b back side portion, 2 suction port, 3 blow-out
port, 5 bell mouth, 5a upper portion, 5b center portion, 5c lower
portion, 6 nozzle, filter, 15 finger guard, 16 motor stay, 17 fixed
member, 18 supporting member, 20 fan, 20a axis of rotation, 21
boss, 30 fan motor, 50 heat exchanger, 50a line of symmetry, 51
front side heat exchanger, 51a heat exchanger, 51b heat exchanger,
55 back side heat exchanger, 55a heat exchanger, 55b heat
exchanger, 56 fin, 57 heat-transfer tube, 70 vertical wind
direction control vane, 90 partitioning panel, 100 indoor unit, 110
front side drain pan, 111 drain channel, 111a tongue portion, 115
back side drain pan, 116 connecting port, 117 drain hose, 151
microphone amplifier, 152 A/D converter, 154 D/A converter, 155
amplifier, 158 FIR filter, 159 LMS algorithm, 161 noise detection
microphone, 181 control speaker, 191 silencing effect detection
microphone, 201 signal processing device
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