U.S. patent application number 13/700024 was filed with the patent office on 2013-03-21 for tube for heat exchanger, heat exchanger, and method for manufacturing tube for heat exchanger.
This patent application is currently assigned to Sanden Corporation. The applicant listed for this patent is Yusuke Iino, Yuuichi Matsumoto. Invention is credited to Yusuke Iino, Yuuichi Matsumoto.
Application Number | 20130068437 13/700024 |
Document ID | / |
Family ID | 45003778 |
Filed Date | 2013-03-21 |
United States Patent
Application |
20130068437 |
Kind Code |
A1 |
Matsumoto; Yuuichi ; et
al. |
March 21, 2013 |
Tube for Heat Exchanger, Heat Exchanger, and Method for
Manufacturing Tube for Heat Exchanger
Abstract
Provided is a tube for a heat exchanger in which drainage
performance of the tube and the fin is improved while preventing
the brazing failure. That is, provided is a tube (110) for a heat
exchanger, the tube through which a refrigerant flows being formed
into a flat plate shape, the tube including stepped portions (117
and 118) at both end portions (110a and 110b) in a refrigerant
flowing direction, respectively, in which the tube has a widthwise
length in a region on an end portion (110a or 110b) side with
respect to a position of each of the stepped portions (117 and
118), the widthwise length being smaller than a widthwise length in
a region between both the stepped portions (117 and 118), and in
which the tube further includes a drainage portion (119) at a
predetermined position between both the stepped portions (117 and
118) along the refrigerant flowing direction.
Inventors: |
Matsumoto; Yuuichi; (Gunma,
JP) ; Iino; Yusuke; (Gunma, JP) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Matsumoto; Yuuichi
Iino; Yusuke |
Gunma
Gunma |
|
JP
JP |
|
|
Assignee: |
Sanden Corporation
Gunma
JP
|
Family ID: |
45003778 |
Appl. No.: |
13/700024 |
Filed: |
May 11, 2011 |
PCT Filed: |
May 11, 2011 |
PCT NO: |
PCT/JP2011/060833 |
371 Date: |
November 26, 2012 |
Current U.S.
Class: |
165/177 ;
29/890.053 |
Current CPC
Class: |
F28F 1/00 20130101; F28D
1/05375 20130101; F28F 1/025 20130101; B21C 23/10 20130101; Y10T
29/49391 20150115; B21C 37/151 20130101; F28D 1/05316 20130101;
F28F 1/022 20130101; B21K 21/16 20130101; F28F 2255/08
20130101 |
Class at
Publication: |
165/177 ;
29/890.053 |
International
Class: |
F28F 1/00 20060101
F28F001/00; B21K 21/16 20060101 B21K021/16 |
Foreign Application Data
Date |
Code |
Application Number |
May 24, 2010 |
JP |
2010-118199 |
Claims
1. A tube for a heat exchanger, the tube through which a
refrigerant flows being formed into a flat plate shape, the tube
comprising stepped portions at both end portions in a refrigerant
flowing direction, respectively, wherein the tube has a widthwise
length in a region on an end portion side with respect to a
position of each of the stepped portions, the widthwise length
being defined in a longitudinal direction of a cross-section
orthogonal to the refrigerant flowing direction, the widthwise
length being smaller than a widthwise length in a region between
both the stepped portions, and wherein the tube further comprises a
drainage portion at a predetermined position between both the
stepped portions along the refrigerant flowing direction.
2. A tube for a heat exchanger according to claim 1, wherein the
widthwise length in the longitudinal direction of the cross-section
orthogonal to the refrigerant flowing direction of the region on
the end portion side with respect to the position of the each of
the stepped portions is formed to become smaller toward the end
portion.
3. A heat exchanger, comprising the tube for a heat exchanger
according to claim 1.
4. A method of manufacturing a tube for a heat exchanger, the
method comprising press-forming a tube for a heat exchanger, which
has a drainage portion formed therein at at least one widthwise
side end portion in a longitudinal direction of a cross-section
orthogonal to the refrigerant flowing direction along a refrigerant
flowing direction, to thereby flatten parts of the drainage portion
at both end portions in the refrigerant flowing direction so that a
width in the longitudinal direction of the cross-section orthogonal
to the refrigerant flowing direction of each part obtained by the
flattening is smaller than a width in the longitudinal direction of
a cross-section orthogonal to the refrigerant flowing direction
between both side end portions.
5. A heat exchanger, comprising the tube for a heat exchanger
according to claim 2.
Description
TECHNICAL FIELD
[0001] The present invention relates to a heat exchanger, and more
particularly, to a tube structure in a heat exchanger and a method
of manufacturing a tube for a heat exchanger.
BACKGROUND ART
[0002] Conventionally, heat exchangers have been utilized in, for
example, an air conditioning apparatus. The air conditioning
apparatus includes, for example, an indoor heat exchanger and an
outdoor heat exchanger. It is known that, in the indoor heat
exchanger in the case of cooling operation and in the outdoor heat
exchanger in the case of heating operation, condensed water is
easily generated through dew condensation. The condensed water is
liable to accumulate between a tube and a fin of the heat
exchanger, which may inhibit an air flow to cause not only
reduction in heat exchange efficiency, but also frost formation in
the outdoor heat exchanger during heating operation.
[0003] To address this problem, as described in, for example,
Patent Literature 1, there has been proposed a heat exchanger in
which, for drainage of condensed water accumulated in the heat
exchanger, a corrugated fin including an inclined portion and a
curved portion is arranged between heat exchange tube portions
(flat tubes) arranged in a vertical direction, and an elongated
depression for drainage extending in a longitudinal direction is
formed in a flat surface portion of a heat exchange tube portion on
the corrugated fin side.
[0004] With such a heat exchanger, it is conceived that, indeed,
the condensed water generated through dew condensation on the
surfaces of the flat heat-transfer tube and the corrugated fin is
guided downward through the elongated depression for drainage
formed in the flat surface portion of the heat exchange tube
portion.
CITATION LIST
Patent Literature
[0005] [PTL 1] Japanese Patent Application Laid-Open No. 7-190661
(claim 1, paragraph [0016], FIG. 4)
SUMMARY OF INVENTION
Technical Problem
[0006] In this case, the elongated depression provided in the flat
surface portion of the heat exchange tube portion is formed only in
a range excluding end portions of the heat exchange tube portion so
that, when the heat exchange tube portion is inserted into an
insertion hole of a header tank and brazed, airtightness between
the heat exchange tube portion and the header tank is not
inhibited. In this case, when the end potion of the heat exchange
tube portion, at which the elongated depression is not formed, is
accurately inserted into the insertion hole of the header tank, it
is conceived that the heat exchange tube portion is brazed without
the airtightness thereof being inhibited as described above.
[0007] However, when the end portion of the heat exchange tube
portion is inserted into the insertion hole of the header tank
deeper than expected, the insertion hole and the elongated
depression overlap with each other, which may cause brazing failure
such as inhibition of airtightness. Further, when the end portion
of the heat exchange tube portion is inserted shallower than
expected so as to prevent overlapping of the insertion hole with
the elongated depression, such brazing failure that a brazing
material blocks the flow path of the heat exchange tube portion may
occur.
[0008] The present invention has been made as a challenge to solve
such a problem described above, and has an object to provide a tube
for a heat exchanger in which drainage performance of the tube and
the fin is improved while preventing the brazing failure, and to
provide a heat exchanger and a method of manufacturing a tube for a
heat exchanger.
Solution to Problem
[0009] In order to meet the challenge as described above, a tube
for a heat exchanger according to the present invention and a tube
for a heat exchanger to be used in a heat exchanger according to
the present invention are each a tube for a heat exchanger, the
tube through which a refrigerant flows being formed into a flat
plate shape, the tube including stepped portions at both end
portions in a refrigerant flowing direction, respectively, in which
the tube has a widthwise length in a region on an end portion side
with respect to a position of each of the stepped portions, the
widthwise length being smaller than a widthwise length in a region
between both the stepped portions, and in which the tube further
includes a drainage portion at a predetermined position between
both the stepped portions along the refrigerant flowing direction.
Further, the widthwise length of the region on the end portion side
with respect to the position of the each of the stepped portions is
formed to become smaller toward the end portion. Further, according
to the present invention, there is provided a method of
manufacturing a tube for a heat exchanger, the method including
press-forming a tube for a heat exchanger, which has a drainage
portion formed therein at at least one widthwise side end portion
along a refrigerant flowing direction, to thereby flatten parts of
the drainage portion at both end portions in the refrigerant
flowing direction so that a width of each part obtained by the
flattening is smaller than a width between both side end
portions.
Advantageous Effects of Invention
[0010] According to the present invention, it is possible to
provide the tube for a heat exchanger in which drainage performance
of the tube and the fin is improved while preventing the brazing
failure, and to provide the heat exchanger and the method of
manufacturing a tube for a heat exchanger.
BRIEF DESCRIPTION OF DRAWINGS
[0011] FIG. 1 is a schematic front view of a heat exchanger
according to an embodiment of the present invention.
[0012] FIG. 2A is a perspective view of a tube of the heat
exchanger according to the embodiment of the present invention.
[0013] FIG. 2B is a longitudinal end view of the tube.
[0014] FIG. 2C is a sectional view taken along the line A-A of FIG.
2A.
[0015] FIG. 3 is a perspective view of an unprocessed tube of the
heat exchanger according to the embodiment of the present
invention.
[0016] FIG. 4A is a schematic view illustrating a step of a method
of manufacturing a tube.
[0017] FIG. 4B is a schematic view illustrating a step of the
method of manufacturing a tube.
[0018] FIG. 4C is a schematic view illustrating a step of the
method of manufacturing a tube.
[0019] FIG. 4D is a schematic view illustrating a step of the
method of manufacturing a tube.
[0020] FIG. 5A is a perspective view of a tube of a heat exchanger
according to another embodiment of the present invention.
[0021] FIG. 5B is a sectional view taken along the line B-B of FIG.
5A.
[0022] FIG. 6 is a perspective view of an unprocessed tube of the
heat exchanger according to the another embodiment of the present
invention.
[0023] FIG. 7 is a configuration view illustrating an example of an
air conditioning apparatus including the heat exchangers.
DESCRIPTION OF EMBODIMENTS
[0024] In the following, embodiments of the present invention are
specifically described with reference to the drawings. For the sake
of convenience, parts having the same action and effect are denoted
by the same reference symbols, and description thereof is omitted
herein.
First Embodiment
[0025] As illustrated in FIG. 1, a heat exchanger 100 includes a
plurality of tubes 110 arranged in parallel to each other, through
which a refrigerant flows, and fins 120 each joined by brazing
between adjacent tubes 110. In the illustrated example, the
plurality of tubes 110 are communicated to hollow header tanks 130
and 135 at both ends of the plurality of tubes 110 in their
longitudinal direction (refrigerant flowing direction). The header
tank 130 provided on the upper side includes a refrigerant entrance
portion 130a provided on one end side, a refrigerant exit portion
130b provided on the other end side, and a partition plate 131
provided at a center thereof, for partitioning inside of the header
tank 130. With this, the refrigerant flowing in from the entrance
portion 130a of the header tank 130 flows through the tubes 110
(two tubes on the left side in FIG. 1) communicated on the entrance
portion 130a side with respect to the partition plate 131, and
flows into the header tank 135 provided on the lower side. Then,
the refrigerant exits from the header tank 135 to flow through the
tubes 110 (two tubes on the right side in FIG. 1) communicated on
the exit portion 130b side with respect to the partition plate, and
flows out from the exit portion 130b via the header tank 130. Note
that, FIG. 1 schematically illustrates the heat exchanger 100, and
is simplified for the sake of easy understanding of the
description.
[0026] The fin 120 is a so-called corrugated fin and is made of a
metal having high heat conductivity, such as aluminum. The fin 120
includes a flat portion 121 having a flat plate shape and a bent
portion 122 bent with a predetermined curvature radius, which are
formed alternately in the longitudinal direction. The bent portion
122 is a part to be joined to a flat surface 115 of the tube 110,
and includes a first bent portion 122a to be joined to the flat
surface 115 of one of the opposing tubes 110, and a second bent
portion 122b to be joined to the flat surface 115 of the other of
the opposing tubes 110 (see FIG. 1). In the illustrated example,
the flat portion 121 is smoothly and continuously provided to the
bent portion 122 (122a and 122b) formed into a semi-circular arc
shape in cross section. With this, adjacent flat portions 121 are
provided in parallel to each other. Further, when the fin 120 is
joined to the tube 110, the flat portion 121 becomes perpendicular
to the longitudinal direction of the tube 110.
[0027] As illustrated in FIG. 2A, the tube 110 is formed into a
flat hollow plate shape and is made of a metal having high heat
conductivity, such as aluminum. Further, in an inside space, a
plurality of partition portions 113 are provided so that a
plurality of refrigerant flow paths 111 extending in a longitudinal
direction are arranged in parallel in a width direction (lateral
direction). As illustrated in FIG. 1, the plurality of tubes 110
are equally arranged in parallel at predetermined intervals so that
the flat surfaces 115 thereof are opposed to each other, and the
fin 120 is joined to the opposing flat surfaces 115 of the adjacent
tubes 110. The tube 110 has two longitudinal end portions 110a and
110b, which are inserted into insertion holes provided in the
header tanks 130 and 135, respectively, and are brazed. Note that,
the insertion ports are provided in conformity with the shape of
both the end portions 110a and 110b of the tube 110.
[0028] In each of both widthwise (lateral) end portions of the tube
110, a stepped portion 117 and a stepped portion 118 are formed on
one end side (end portion 110a side) and the other end side (end
portion 110b side) in the refrigerant flowing direction
(longitudinal direction), respectively. Further, the widthwise
length of a region further on the one end side (end portion 110a
side) with respect to the position of the stepped portion 117 is
smaller than the widthwise length of a region between the stepped
portion 117 and the stepped portion 118 by the length of the
stepped portion 117 (see FIGS. 2A and 2B). Further, similarly, the
widthwise length of a region further on the other end side (end
portion 110b side) with respect to the position of the stepped
portion 118 is smaller than the widthwise length of the region
between the stepped portion 117 and the stepped portion 118 by the
length of the stepped portion 118.
[0029] An outer shape of the region further on each end portion
110a or 110b side with respect to the position of the stepped
portion 117 or 118 is a simple shape that is formed of linear
portions 114 formed by the flat surfaces 115 and 115, and
semi-circular arc portions 116 and 116 formed at both ends of the
linear portions 114. Note that, the widthwise length of the region
further on each end portion side with respect to the position of
the stepped portion 117 or 118 may become smaller toward the end
portion from the position of each stepped portion 117 or 118 to
form a tapered shape in plan view.
[0030] Between the stepped portion 117 and the stepped portion 118,
a drainage portion 119 is provided at a predetermined position in
the refrigerant flowing direction. In the illustrated example, the
stepped portions 117 and 118 are provided at predetermined
positions between both the end portions 110a and 110b in the
refrigerant flowing direction, and the groove-shaped drainage
portion 119 is formed between the stepped portions 117 and 118.
Further, as illustrated in FIG. 2C, the tube 110 has two widthwise
ends that are formed into semi-circular arc portions 112 having a
semi-circular arc shape. The above-mentioned drainage portion 119
is arranged at a boundary between the semi-circular arc portion 112
and the flat surface 115.
[0031] The drainage portion 119 is formed in the tube 110 as
described above, and hence, even when the fin 120 is joined to the
tube 110, the drainage portion 119 is not blocked by the fin 120.
With this, condensed water accumulated inside the fin 120 or
between the fin 120 and the tube 110 is drained downward through
the drainage portion 119.
[0032] Further, the region further on each end portion side with
respect to the position of the stepped portion 117 or 118 is not
provided with the drainage portion and has a simple shape.
Therefore, brazing failure hardly occurs when the tube 110 is
inserted into the header tanks 130 and 135 and brazed.
[0033] Further, the width of the insertion hole for the tube 110,
which is provided in each of the header tanks 130 and 135, is
provided in conformity with the width of the region of the tube 110
further on each end portion side with respect to the position of
the stepped portion 117 or 118, and hence, when the tube 110 is
inserted to reach a predetermined position (position of the stepped
portion 117 or 118), the stepped portion abuts against the
insertion hole, and the tube 110 cannot be inserted any more. With
this, the drainage portion 119 and the insertion port are prevented
from overlapping with each other, and hence the brazing failure
hardly occurs.
[0034] Further, when the tube 110 is processed so that its width
becomes narrower toward each end portion from the position of the
stepped portion 117 or 118, the end portion of the tube 110 can be
easily inserted into the insertion port of each of the header tanks
130 and 135.
[0035] A method of manufacturing the tube 110 is described with
reference to FIGS. 3 and 4. An unprocessed tube 140 illustrated in
FIG. 3 is formed by, for example, extrusion molding to have an
outer shape formed of linear portions 144 formed by flat surfaces
145 and 145, and semi-circular arc portions 142 and 142 formed at
both ends of the linear portions 144. Further, a drainage portion
149 is formed across an entire longitudinal region at a boundary
between the semi-circular arc portion 142 and the flat surface 145.
Note that, a distance (widthwise length) between one semi-circular
arc portion 142 to the other semi-circular arc portion 142 is the
widthwise length of the tube 110 in the region between the stepped
portion 117 and the stepped portion 118.
[0036] Such an unprocessed tube 140 is fixed to a press forming
machine, and predetermined regions on sides of both lengthwise end
portions 140a and 140b are pressed in the width direction by a pair
of dies 150 and 150 each having a depression portion corresponding
to the outer shape of the region further on each end portion 110a
or 110b side with respect to the position of the stepped portion
117 or 118 (FIGS. 4A and 4B). With this, in the predetermined
regions of the unprocessed tube 140 on the sides of both the end
portions 140a and 140b, the drainage portion 149 is squashed to be
flattened. Thus, a predetermined region of the semi-circular arc
portion 142 becomes the semi-circular arc portion 116 (FIG. 4C).
The unprocessed tube thus formed is removed from the dies to become
the tube 110 (FIG. 4D).
Second Embodiment
[0037] FIG. 5 illustrates a tube 210 of a heat exchanger 200
according to a second embodiment of the present invention. Note
that, the tube 210 of the second embodiment illustrated in FIG. 5
has a configuration in which the tube 210 having a structure
different from that of the tube 110 of the heat exchanger 100 of
the first embodiment is provided. Therefore, description other than
that of the tube 210 is omitted herein.
[0038] The tube 210 is formed into a flat hollow plate shape and is
made of a metal having high heat conductivity, such as aluminum.
Further, in an inside space, a plurality of partition portions 213
are provided so that a plurality of refrigerant flow paths 211
extending in a longitudinal direction are arranged in parallel in a
lateral direction (width direction).
[0039] In each of both widthwise (lateral) end portions of the tube
210, a stepped portion 217 and a stepped portion 218 are formed on
one end side (end portion 210a side) and the other end side (end
portion 210b side) in the refrigerant flowing direction
(longitudinal direction), respectively. Further, the widthwise
length of a region further on the one end side (end portion 210a
side) with respect to the position of the stepped portion 217 is
formed smaller than the widthwise length of a region between the
stepped portion 217 and the stepped portion 218. Further,
similarly, the widthwise length of a region further on the other
end side (end portion 210b side) with respect to the position of
the stepped portion 218 is formed smaller than the widthwise length
of the region between the stepped portion 217 and the stepped
portion 218.
[0040] An outer shape of the region further on each end portion
210a or 210b side with respect to the position of the stepped
portion 217 or 218 is a simple shape that is formed of linear
portions 214 formed by the flat surfaces 215 and 215, and
semi-circular arc portions 216 formed at both ends of the linear
portions 214. Further, the widthwise length of the region further
on each end portion 210a or 210b side with respect to the position
of the stepped portion 217 or 218 becomes smaller toward the end
portion 210a or 210b from the position of each stepped portion 217
or 218 (unrecognizable in the figures), and hence the end portion
210a or 210b of the tube 210 can easily be inserted into the
insertion port of each of the header tanks 130 and 135.
[0041] Between the stepped portion 217 and the stepped portion 218,
a drainage portion 219 is provided at a predetermined position in
the refrigerant flowing direction. As illustrated in FIGS. 5A and
5B, the stepped portions 217 and 218 are provided at predetermined
positions between both the end portions in the refrigerant flowing
direction, and the drainage portion 219 having a cutout shape
continuously provided in the refrigerant flowing direction is
formed between the stepped portions 217 and 218. Note that, a
region on the outer side in the width direction with respect to the
drainage portion 219 is formed to have a semi-circular arc shape
(semi-circular arc portion 212), and has a curvature radius smaller
than the curvature radius of the semi-circular arc portion 216 on
the end portion side.
[0042] The drainage portion 219 is formed in the tube 210 as
described above, and hence, even when the fin 220 is joined to the
tube 210, the drainage portion 219 is not blocked by the fin 120.
With this, condensed water accumulated inside the fin 120 or
between the fin 120 and the tube 210 is drained downward through
the drainage portion 219.
[0043] Further, the region further on each end portion 210a or 210b
side with respect to the position of the stepped portion 217 or 218
is not provided with the drainage portion 219 and has a simple
shape. Therefore, brazing failure hardly occurs when the tube 210
is inserted into the header tanks 130 and 135 and brazed.
[0044] Further, the width of the insertion hole for the tube 210,
which is provided in each of the header tanks 130 and 135, is
provided in conformity with the width of the region of the tube 210
further on each end portion side with respect to the position of
the stepped portion 217 or 218, and hence, when the tube 210 is
inserted to reach a predetermined position (position of the stepped
portion 217 or 218), the stepped portion abuts against the
insertion hole, and the tube 210 cannot be inserted any more. With
this, the drainage portion 219 and the insertion port are prevented
from overlapping with each other, and hence the brazing failure
hardly occurs.
[0045] A method of manufacturing the tube 210 is similar to that
for the tube 210 in the first embodiment, and the tube 210 is
manufactured by press forming an unprocessed tube 240 illustrated
in FIG. 6. Note that, the unprocessed tube 240 has an outer shape
formed of linear portions formed by flat surfaces 245 and 245, and
semi-circular arc portions 242 and 242 formed at both ends of the
linear portions. Further, the curvature radius of the semi-circular
arc portion 242 is formed to be smaller than a half of a thickness
of the unprocessed tube, and a continuous cutout portion 249 is
formed across the entire longitudinal region at a boundary between
the semi-circular arc portion 242 and the flat surface 245. Note
that, a distance from one semi-circular arc portion 242 to the
other semi-circular arc portion 242 is the widthwise length of the
tube 210 in the region between the stepped portion 217 and the
stepped portion 218.
[0046] (Usage Example)
[0047] As an example in which the heat exchangers (100 and 200)
exemplified in the above-mentioned first and second embodiments are
used, FIG. 7 illustrates an overall configuration view of an air
conditioning apparatus 1 provided in an electric vehicle, for
example. This air conditioning apparatus 1 utilizes a so-called
heat pump cycle, and switches cooling and heating by switching,
with a four-way valve 13, the flow of the refrigerant from a
compressor 11 with respect to an out-vehicle heat exchanger 100A
and an in-vehicle heat exchanger 100B. Note that, the heat
exchanger 100A and the heat exchanger 100B each correspond to any
one of the heat exchangers 100 and 200, and in this case,
description is made of a case where the heat exchanger 100A and the
heat exchanger 100B each correspond to the heat exchanger 100 of
the first embodiment.
[0048] In the illustrated example, the four-way valve 13 is
connected to an ejection port 11a of the compressor 11. With this,
the compressor 11, the in-vehicle heat exchanger 100B, and the
out-vehicle heat exchanger 100A are connected as follows. That is,
in a case where the four-way valve 13 is connected in a state as
indicated by broken lines (heating operation), the refrigerant
ejected from the compressor 11 flows into the in-vehicle heat
exchanger 100B, and the refrigerant that has passed through the
in-vehicle heat exchanger 100B flows into the out-vehicle heat
exchanger 100A via an expansion valve 15 so that the refrigerant
returns to an intake port 11b of the compressor 11 via the four-way
valve 13. Further, in a case where the four-way valve 13 is
connected in a state as indicated by solid lines (cooling
operation), the refrigerant ejected from the compressor 11 flows
into the out-vehicle heat exchanger 100A, and the refrigerant that
has passed through the out-vehicle heat exchanger 100A flows into
the in-vehicle heat exchanger 100B via the expansion valve 15 so
that the refrigerant returns to the intake port 11b of the
compressor 11 via the four-way valve 13. Note that, a cooling fan
17 is provided adjacent to the out-vehicle heat exchanger 100A.
[0049] In an in-vehicle unit of the air conditioning apparatus 1, a
damper 21 for intake air switching and a blower 23 are provided on
an upstream side of a ventilating duct 20 provided with the heat
exchanger 100B. Further, on a downstream side of the ventilating
duct 20, a heater unit 25 for heating assistance is provided, and
an amount of air passing through the heater unit 25 is adjusted by
a damper 27 for discharge air switching. Outlet ports 29a, 29b, and
29c of the ventilating duct 20 are for DEF, FACE, and FOOT,
respectively, and dampers 30a, 30b, and 30c respectively provided
thereto can adjust the amount of air to be discharged from the
outlet ports 29a, 29b, and 29c.
[0050] In such an air conditioning apparatus 1, even when condensed
water generated through dew condensation adheres to the in-vehicle
heat exchanger 100B in the case of cooling operation, the condensed
water is drained through the drainage portion 119 provided in the
tube 110 of the heat exchanger 100B. Further, even when condensed
water adheres to the out-vehicle heat exchanger 100A in the case of
heating operation, the condensed water is drained through the
drainage portion 119 provided in the tube 110 of the heat exchanger
100A.
[0051] The embodiments of the present invention have been described
above in detail with reference to the drawings, but specific
configurations are not limited to those embodiments, and the
present invention also encompasses design changes and the like
without departing from the gist of the present invention. Further,
mutual use of technologies among the above-mentioned embodiments is
possible as long as the objects, the configurations, and the like
do not have particular contradictions and problems. For example,
description is made of an example in which both the widthwise ends
of the tube have a semi-circular arc shape, but the present
invention is not limited thereto. Both the widthwise ends of the
tube may have a shape that is not curved, such as a rectangular
shape.
[0052] Further, description is made of an example in which the
drainage portion is provided in each widthwise end portion of the
tube, but the present invention is not limited thereto, and the
drainage portion may be formed only on one widthwise end side of
the tube. In this case, it is known that a larger amount of
condensed water adheres to the end portion of the tube on the
windward side, and hence it is preferred that the heat exchanger be
configured so that air is blown by a fan from the side on which the
drainage portion is provided.
REFERENCE SIGNS LIST
[0053] 100 heat exchanger [0054] 110 tube (tube for heat exchanger)
[0055] 110a end portion [0056] 110b end portion [0057] 117 stepped
portion [0058] 118 stepped portion [0059] 119 drainage portion
[0060] 120 fin
* * * * *