U.S. patent application number 13/980600 was filed with the patent office on 2013-11-07 for heat exchanger and air conditioner.
This patent application is currently assigned to DAIKIN INDUSTRIES, LTD.. The applicant listed for this patent is Hirokazu Fujino, Masanori Jindou, Toshimitsu Kamada, Yoshimasa Kikuchi, Yoshio Oritani. Invention is credited to Hirokazu Fujino, Masanori Jindou, Toshimitsu Kamada, Yoshimasa Kikuchi, Yoshio Oritani.
Application Number | 20130292098 13/980600 |
Document ID | / |
Family ID | 46515545 |
Filed Date | 2013-11-07 |
United States Patent
Application |
20130292098 |
Kind Code |
A1 |
Jindou; Masanori ; et
al. |
November 7, 2013 |
HEAT EXCHANGER AND AIR CONDITIONER
Abstract
A plurality of flat tubes is, at one end thereof, connected to a
first header collecting pipe, and is, at the other end thereof,
connected to a second header collecting pipe. Some of the flat
tubes forms a main heat exchange part, and the other flat tubes
forms an auxiliary heat exchange part. The number of flat tubes of
the auxiliary heat exchange part is less than the number of flat
tubes of the main heat exchange part. The total cross-sectional
area of flow paths per flat tube provided in the auxiliary heat
exchange part is greater than the total cross-sectional area of
flow paths per flat tube provided in the main heat exchange
part.
Inventors: |
Jindou; Masanori; (Osaka,
JP) ; Oritani; Yoshio; (Osaka, JP) ; Fujino;
Hirokazu; (Osaka, JP) ; Kamada; Toshimitsu;
(Osaka, JP) ; Kikuchi; Yoshimasa; (Osaka,
JP) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Jindou; Masanori
Oritani; Yoshio
Fujino; Hirokazu
Kamada; Toshimitsu
Kikuchi; Yoshimasa |
Osaka
Osaka
Osaka
Osaka
Osaka |
|
JP
JP
JP
JP
JP |
|
|
Assignee: |
DAIKIN INDUSTRIES, LTD.
Osaka-shi, Osaka
JP
|
Family ID: |
46515545 |
Appl. No.: |
13/980600 |
Filed: |
January 23, 2012 |
PCT Filed: |
January 23, 2012 |
PCT NO: |
PCT/JP2012/000367 |
371 Date: |
July 19, 2013 |
Current U.S.
Class: |
165/143 ;
165/151 |
Current CPC
Class: |
F28D 1/05308 20130101;
F28F 2215/12 20130101; F28F 1/325 20130101; F28D 1/05391 20130101;
F28F 1/126 20130101; F28F 1/128 20130101; F25B 39/04 20130101; F28D
1/0417 20130101; F25B 2339/0444 20130101; F28F 1/30 20130101; F28F
1/022 20130101; F28F 2215/10 20130101; F25B 2500/01 20130101; F25B
39/028 20130101; F25B 40/02 20130101; F28F 13/06 20130101; F28F
2215/04 20130101; F28F 17/005 20130101 |
Class at
Publication: |
165/143 ;
165/151 |
International
Class: |
F28D 1/04 20060101
F28D001/04; F28F 1/30 20060101 F28F001/30; F28D 1/053 20060101
F28D001/053 |
Foreign Application Data
Date |
Code |
Application Number |
Jan 21, 2011 |
JP |
2011-011334 |
Claims
1-6. (canceled)
7. A heat exchanger including a plurality of flat tubes arranged in
a vertical direction and each formed with a plurality of flow paths
of fluid, and a plurality of fins configured to divide part between
adjacent ones of the flat tubes into a plurality of air passages
through each of which air flows, comprising: a first header
collecting pipe; and a second header collecting pipe, wherein each
flat tube is, at one end thereof, connected to the first header
collecting pipe, and is, at the other end thereof, connected to the
second header collecting pipe, some of the flat tubes form a main
heat exchange part, and the other flat tubes form an auxiliary heat
exchange part, the flat tubes forming the auxiliary heat exchange
part are fewer than the flat tubes forming the main heat exchange
part, a total cross-sectional area of the flow paths per flat tube
in the auxiliary heat exchange part is greater than a total
cross-sectional area of the flow paths per flat tube in the main
heat exchange part, and if the heat exchanger serves as a
condenser, refrigerant is condensed in the main heat exchange part,
and the refrigerant is sub-cooled in the auxiliary heat exchange
part.
8. The heat exchanger of claim 7, wherein a width (W2) of each flat
tube of the auxiliary heat exchange part is greater than a width
(W1) of each flat tube of the main heat exchange part, and the flow
paths per flat tube in the auxiliary heat exchange part is more
than the flow paths per flat tube in the main heat exchange
part.
9. The heat exchanger of claim 7, wherein each flow path is formed
with a plurality of grooves in a corresponding one of the flat
tubes of the main heat exchange part, and each flat tube of the
auxiliary heat exchange part is a bare pipe.
10. The heat exchanger of claim 7, wherein each fin is formed in
such a plate shape that a plurality of cut parts into each of which
a corresponding one of the flat tubes is inserted are provided, the
fins are arranged at predetermined intervals in an extension
direction of the flat tubes, each flat tube is sandwiched between
peripheral edge parts of a corresponding one of the cut parts of
the fins, and in each fin, part between adjacent ones of the cut
parts arranged in the vertical direction forms a heat transfer
part.
11. The heat exchanger of claim 10, wherein an end of each flat
tube in a width direction thereof is aligned with an end of a
corresponding one of the cut parts on an open side thereof.
12. An air conditioner, comprising: a refrigerant circuit provided
with the heat exchanger of claim 7, wherein refrigerant circulates
to perform a refrigeration cycle in the refrigerant circuit.
13. The heat exchanger of claim 8, wherein each flow path is formed
with a plurality of grooves in a corresponding one of the flat
tubes of the main heat exchange part, and each flat tube of the
auxiliary heat exchange part is a bare pipe.
14. The heat exchanger of claim 8, wherein each fin is formed in
such a plate shape that a plurality of cut parts into each of which
a corresponding one of the flat tubes is inserted are provided, the
fins are arranged at predetermined intervals in an extension
direction of the flat tubes, each flat tube is sandwiched between
peripheral edge parts of a corresponding one of the cut parts of
the fins, and in each fin, part between adjacent ones of the cut
parts arranged in the vertical direction forms a heat transfer
part.
15. The heat exchanger of claim 9, wherein each fin is formed in
such a plate shape that a plurality of cut parts into each of which
a corresponding one of the flat tubes is inserted are provided, the
fins are arranged at predetermined intervals in an extension
direction of the flat tubes, each flat tube is sandwiched between
peripheral edge parts of a corresponding one of the cut parts of
the fins, and in each fin, part between adjacent ones of the cut
parts arranged in the vertical direction forms a heat transfer
part.
16. The heat exchanger of claim 13, wherein each fin is formed in
such a plate shape that a plurality of cut parts into each of which
a corresponding one of the flat tubes is inserted are provided, the
fins are arranged at predetermined intervals in an extension
direction of the flat tubes, each flat tube is sandwiched between
peripheral edge parts of a corresponding one of the cut parts of
the fins, and in each fin, part between adjacent ones of the cut
parts arranged in the vertical direction forms a heat transfer
part.
17. The heat exchanger of claim 14, wherein an end of each flat
tube in a width direction thereof is aligned with an end of a
corresponding one of the cut parts on an open side thereof.
18. The heat exchanger of claim 15, wherein an end of each flat
tube in a width direction thereof is aligned with an end of a
corresponding one of the cut parts on an open side thereof.
19. The heat exchanger of claim 16, wherein an end of each flat
tube in a width direction thereof is aligned with an end of a
corresponding one of the cut parts on an open side thereof.
20. An air conditioner, comprising: a refrigerant circuit provided
with the heat exchanger of claim 8, wherein refrigerant circulates
to perform a refrigeration cycle in the refrigerant circuit.
21. An air conditioner, comprising: a refrigerant circuit provided
with the heat exchanger of claim 9, wherein refrigerant circulates
to perform a refrigeration cycle in the refrigerant circuit.
22. An air conditioner, comprising: a refrigerant circuit provided
with the heat exchanger of claim 10, wherein refrigerant circulates
to perform a refrigeration cycle in the refrigerant circuit.
23. An air conditioner, comprising: a refrigerant circuit provided
with the heat exchanger of claim 11, wherein refrigerant circulates
to perform a refrigeration cycle in the refrigerant circuit.
24. An air conditioner, comprising: a refrigerant circuit provided
with the heat exchanger of claim 13, wherein refrigerant circulates
to perform a refrigeration cycle in the refrigerant circuit.
25. An air conditioner, comprising: a refrigerant circuit provided
with the heat exchanger of claim 14, wherein refrigerant circulates
to perform a refrigeration cycle in the refrigerant circuit.
26. An air conditioner, comprising: a refrigerant circuit provided
with the heat exchanger of claim 15, wherein refrigerant circulates
to perform a refrigeration cycle in the refrigerant circuit.
Description
TECHNICAL FIELD
[0001] The present disclosure relates to a heat exchanger including
flat tubes and fins and configured to exchange heat between fluid
flowing through the flat tube and air, and to an air
conditioner.
BACKGROUND ART
[0002] Conventionally, a refrigerating apparatus has been known,
which is capable of performing a refrigeration cycle by refrigerant
circulating through a refrigerant circuit and performing an
operation for cooling a target object (e.g., air or water) with
refrigerant and an operation for heating the target object with
refrigerant. For example, Patent Document 1 discloses an air
conditioner including the refrigerating apparatus of this type. In
the air conditioner during an air-cooling operation for cooling
indoor air, an outdoor heat exchanger functions as a condenser, and
an indoor heat exchanger functions as an evaporator. On the other
hand, in the air conditioner during an air-heating operation for
heating indoor air, the indoor heat exchanger functions as the
condenser, and the outdoor heat exchanger functions as the
evaporator.
[0003] Patent Document 2 also discloses an air conditioner
configured to perform a refrigeration cycle. In a refrigerant
circuit of the air conditioner, an outdoor heat exchanger
configured to exchange heat between refrigerant and outdoor air is
provided. The outdoor heat exchanger is a heat exchanger including
two headers each formed in a cylindrical shape, and a plurality of
flat heat transfer pipes provided between the headers.
[0004] Moreover, Patent Document 3 also discloses a heat exchanger
including headers and flat heat transfer pipes. The heat exchanger
disclosed in Patent Document 3 functions as a condenser. In the
heat exchanger, a main heat exchange part for condensation and an
auxiliary heat exchange part for sub-cooling are formed. While
passing through the main heat exchange part, refrigerant flowing
into the heat exchanger is condensed into a substantially liquid
single-phase state. Then, the refrigerant flows into the auxiliary
heat exchange part, and is further cooled.
CITATION LIST
Patent Document
[0005] PATENT DOCUMENT 1: Japanese Patent Publication No.
2008-064447
[0006] PATENT DOCUMENT 2: Japanese Patent Publication No.
H09-014698
[0007] PATENT DOCUMENT 3: Japanese Patent Publication No.
2010-025447
SUMMARY OF THE INVENTION
Technical Problem
[0008] However, in the case where the main heat exchange part for
condensation and the auxiliary heat exchange part for sub-cooling
are formed in the heat exchanger including the headers and the flat
heat transfer pipes (flat tubes), the auxiliary heat exchange part
typically has flow paths fewer than those of the main heat exchange
part. Thus, there is a possibility that a flow velocity in the
auxiliary heat exchange part increases, and therefore a pressure
loss in the auxiliary heat exchange part increases.
[0009] The present disclosure has been made in view of the
foregoing, and it is an objective of the present disclosure to
reduce, in a heat exchanger in which headers and flat tubes are
provided and a main heat exchange part(s) for condensation and an
auxiliary heat exchange part(s) for sub-cooling are formed, a
pressure loss in the auxiliary heat exchange part.
Solution to the Problem
[0010] In order to solve the foregoing problem, a first aspect of
the invention is intended for a heat exchanger including a
plurality of flat tubes (53, 58) arranged in the vertical direction
such that side surfaces thereof face each other and each formed
with a plurality of flow paths (49) of fluid, and a plurality of
fins (54, 59) configured to divide part between adjacent ones of
the flat tubes (53, 58) into a plurality of air passages through
each of which air flows. The heat exchanger includes a first header
collecting pipe (51, 56); and a second header collecting pipe (52,
57). Each flat tube (53, 58) is, at one end thereof, connected to
the first header collecting pipe (51, 56), and is, at the other end
thereof; connected to the second header collecting pipe (52, 57).
Some of the flat tubes (53) form a main heat exchange part (50),
and the other flat tubes (58) form an auxiliary heat exchange part
(55). The flat tubes (58) forming the auxiliary heat exchange part
(55) are fewer than the flat tubes (53) forming the main heat
exchange part (50). The total cross-sectional area of flow paths
(49) per flat tube (58) in the auxiliary heat exchange part (55) is
greater than the total cross-sectional area of flow paths (49) per
flat tube (53) in the main heat exchange part (50). If the heat
exchanger serves as a condenser, refrigerant is condensed in the
main heat exchange part (50), and the refrigerant is sub-cooled in
the auxiliary heat exchange part (55).
[0011] In the foregoing configuration, the number of flat tubes
(58) forming the auxiliary heat exchange part (55) is less than the
number of flat tubes (53) forming the main heat exchange part (50).
However, the total cross-sectional area of flow paths (49) per flat
tube (58) in the auxiliary heat exchange part (55) is greater than
the total cross-sectional area of flow paths (49) per flat tube
(53) in the main heat exchange part (50). Thus, if the heat
exchanger serves as the condenser, the flow velocity of refrigerant
in the auxiliary heat exchange part (55) can be lowered as compared
to a heat exchanger in which a single type of flat tubes forms a
main heat exchange part and an auxiliary heat exchange part.
[0012] A second aspect of the invention is intended for the heat
exchanger of the first aspect of the invention, in which the width
(W2) of each flat tube (58) of the auxiliary heat exchange part
(55) is greater than the width (W1) of each flat tube (53) of the
main heat exchange part (50), and the flow paths per flat tube (58)
in the auxiliary heat exchange part (55) is more than the flow
paths per flat tube (53) in the main heat exchange part (50).
[0013] In the foregoing configuration, the number of flow paths per
flat tube (53, 58) and the width (W1, W2) of the flat tube (53, 58)
are adjusted to set the total cross-sectional area of flow paths
(49) per flat tube (53, 58).
[0014] A third aspect of the invention is intended for the heat
exchanger of the first or second aspect of the invention, in which
each flow path (49) is formed with a plurality of grooves in a
corresponding one of the flat tubes (53) of the main heat exchange
part (50), and each flat tube (58) of the auxiliary heat exchange
part (55) is a bare pipe.
[0015] In the foregoing configuration, since the grooves (49a) are
formed in the flat tube (53) for the main heat exchange part (50),
the surface area per refrigerant flow path (49) can be
increased.
[0016] A fourth aspect of the invention is intended for the heat
exchanger of any one of the first to third aspects of the
invention, in which each fin (236) is formed in such a plate shape
that a plurality of cut parts (245) into each of which a
corresponding one of the flat tubes (53, 58) is inserted are
provided, the fins (236) are arranged at predetermined intervals in
an extension direction of the flat tubes (53, 58), each flat tube
(53, 58) is sandwiched between peripheral edge parts of a
corresponding one of the cut parts (245) of the fins (236), and, in
each fin (236), part between adjacent ones of the cut parts (245)
arranged in the vertical direction forms a heat transfer part
(237).
[0017] In the foregoing configuration, the plurality of fins (236)
each formed in a plate shape are arranged at the predetermined
intervals in the extension direction of the flat tubes (53, 58). In
each fin (236), the plurality of cut parts (245) into each of which
a corresponding one of the flat tubes (53, 58) is inserted are
formed. The flat tube (53, 58) is sandwiched between the peripheral
edge parts of a corresponding one of the cut parts (245) of the fin
(236). Moreover, in the fin (236), the part between adjacent ones
of the cut parts (245) arranged in the vertical direction forms the
heat transfer part (237).
[0018] A fifth aspect of the invention is intended for the heat
exchanger of the fourth aspect of the invention, in which an end of
each flat tube (53, 58) in a width direction thereof is aligned
with an end of a corresponding one of the cut parts (245) on an
open side thereof.
[0019] In the foregoing configuration, the end of the flat tube
(53, 58) in the width direction thereof is aligned with the end of
the cut part (245) on the inlet side thereof. Thus, when a brazing
material for joining the fin (236) and the flat tube (53, 58)
together is applied, the brazing material can be easily set on a
side close to the cut part (245).
[0020] A sixth aspect of the invention is intended for an air
conditioner including a refrigerant circuit (20) provided with the
heat exchanger (40) of any one of claims 1-5. Refrigerant
circulates to perform a refrigeration cycle in the refrigerant
circuit (20).
[0021] In the foregoing configuration, the heat exchanger is
connected to the refrigerant circuit (20). In the heat exchanger,
refrigerant circulating through the refrigerant circuit (20) flows
through the flow paths (49) of the flat tubes (53, 58) to exchange
heat with air flowing through air passages.
Advantages of the Invention
[0022] According to the first aspect of the invention, if the heat
exchanger serves as the condenser, the flow velocity of refrigerant
in the auxiliary heat exchange part (55) can be lowered, and
therefore a pressure loss in the auxiliary heat exchange part (55)
can be reduced.
[0023] According to the second aspect of the invention, the total
cross-sectional area of flow paths (49) in the flat tube (53) for
the main heat exchange part (50) and the total cross-sectional area
of flow paths (49) in the flat tube (58) for the auxiliary heat
exchange part (55) can be easily set. For example, even if the flow
paths (49) for the main heat exchange part (50) and the auxiliary
heat exchange part (55) are different from each other in shape, and
it is difficult to identify the difference in shape of the flow
path (49) with eyes, the flat tube (53) for the main heat exchange
part (50) and the flat tube (58) for the auxiliary heat exchange
part (55) are different from each other in width (W1, W2), and
therefore both pipes (53, 58) can be easily identified with
eyes.
[0024] According to the third aspect of the invention, in the flat
tube (53) for the main heat exchange part (50), a heat exchange
efficiency in the main heat exchange part (50) can be improved.
Moreover, in the flat tube (58) for the auxiliary heat exchange
part (55), a pressure loss due to a pipe shape can be further
reduced.
[0025] According to the fifth aspect of the invention, the brazing
material for joining the fin (236) and the flat tube (53, 58)
together can be easily set, and therefore it can be further ensured
that the fin (236) and the flat tube (53, 58) can be joined
together. Moreover, the end of the flat tube (53, 58) is aligned
with the end of the cut part (245) on the open side thereof. Thus,
if the flat tubes (53, 58) having different widths are used, the
depth of the cut part (245) may be set corresponding to the flat
tube (58) having a greater width. That is, even if plural types of
flat tubes (53, 58) having different widths are used, the common
fin (236) can be used.
BRIEF DESCRIPTION OF THE DRAWINGS
[0026] FIG. 1 is a refrigerant circuit diagram of an air
conditioner of a first embodiment, and illustrates a state in an
air-cooling operation.
[0027] FIG. 2 is a refrigerant circuit diagram of the air
conditioner of the first embodiment, and illustrates a state in an
air-heating operation.
[0028] FIG. 3 is a schematic perspective view of a heat exchanger
unit forming an outdoor heat exchanger of the first embodiment.
[0029] FIG. 4 is a schematic front view of the heat exchanger unit
forming the outdoor heat exchanger of the first embodiment.
[0030] FIG. 5 is an enlarged perspective view of a main part of the
heat exchanger unit of the first embodiment in the state in which
part of the main part is not shown.
[0031] FIG. 6 is a schematic view illustrating an example of a
cross-sectional shape of a flat tube.
[0032] FIG. 7A is a view illustrating an example of a
cross-sectional shape of a refrigerant flow path in the flat tube
for a main heat exchange part. FIG. 7B is a view illustrating an
example of a cross-sectional shape of a refrigerant flow path in
the flat tube for an auxiliary heat exchange part.
[0033] FIG. 8 is an view illustrating part of a cross section of a
heat exchanger of a first variation of the first embodiment.
[0034] FIG. 9 is a schematic perspective view of a fin provided in
the heat exchanger of the first variation.
[0035] FIGS. 10A and 10B are views illustrating a heat transfer
part provided in the fin of the heat exchanger of the first
variation. FIG. 10A is the front view of the heat transfer part.
FIG. 10B is the cross-sectional view along a B-B line illustrated
in FIG. 10A.
[0036] FIG. 11A is a partial cross-sectional view of a heat
exchanger of a second variation. FIG. 11B is a cross-sectional view
of a fin along a V-V line illustrated in FIG. 11A.
[0037] FIG. 12 is a view illustrating part of a cross section of a
heat exchanger of a third variation of the first embodiment.
[0038] FIGS. 13A and 13B are views illustrating a main part of a
fin of the heat exchanger of the third variation. FIG. 13A is the
front view of the fin. FIG. 13B is the cross-sectional view along a
G-G line illustrated in FIG. 13A.
[0039] FIG. 14A is a partial cross-sectional view of a heat
exchanger of a fourth variation. FIG. 14B is a cross-sectional view
of a fin along an X-X line illustrated in FIG. 14A.
[0040] FIG. 15 is a front view illustrating a schematic
configuration of an outdoor heat exchanger of a second
embodiment.
[0041] FIG. 16 is a partial cross-sectional view illustrating a
front side of the outdoor heat exchanger of the second
embodiment.
[0042] FIG. 17 is a front view illustrating a schematic
configuration of an outdoor heat exchanger of a third
embodiment.
[0043] FIG. 18 is a partial cross-sectional view illustrating a
front side of the outdoor heat exchanger of the third
embodiment.
[0044] FIG. 19 is a front view illustrating a schematic
configuration of an outdoor heat exchanger of a fourth
embodiment.
[0045] FIG. 20 is a partial cross-sectional view illustrating a
front side of the outdoor heat exchanger of the fourth
embodiment.
[0046] FIG. 21 is a front view illustrating a schematic
configuration of an outdoor heat exchanger of a fifth
embodiment.
[0047] FIG. 22 is a partial cross-sectional view illustrating a
front side of the outdoor heat exchanger of the fifth
embodiment.
[0048] FIG. 23 is a front view illustrating a schematic
configuration of an outdoor heat exchanger of a sixth
embodiment.
[0049] FIG. 24 is a partial cross-sectional view illustrating a
front side of the outdoor heat exchanger of the sixth
embodiment.
[0050] FIG. 25 is a partial cross-sectional view of an outdoor heat
exchanger of a seventh embodiment.
DESCRIPTION OF EMBODIMENTS
[0051] Embodiments of the present disclosure will be described
below with reference to drawings. Note that the embodiments
described below will be set forth merely for the purpose of
preferred examples in nature, and are not intended to limit the
scope, applications, and use of the invention.
First Embodiment of the Invention
[0052] A first embodiment of the present disclosure will be
described. The present embodiment is intended for an air
conditioner including a refrigerating apparatus.
Entire Configuration of Air Conditioner
[0053] FIG. 1 is a refrigerant circuit diagram of an air
conditioner (10) of the first embodiment of the present disclosure,
and illustrates a state in an air-cooling operation. Moreover, FIG.
2 is a refrigerant circuit diagram of the air conditioner (10) of
the first embodiment, and illustrates a state in an air-heating
operation. Referring to FIG. 1, the air conditioner (10) of the
present embodiment includes a single indoor unit (12) which is a
utilization-side unit, and a single outdoor unit (11) which is a
heat-source-side unit. In the air conditioner (10), the outdoor
unit (11) and the indoor unit (12) are connected together by pipes
to form a refrigerant circuit (20).
[0054] Note that the number of indoor units (12) and outdoor units
(11) has been set forth merely for the purpose of an example. That
is, in the air conditioner (10) of the present embodiment, a
plurality of indoor units (12) may be connected to a single outdoor
unit (11) to form a refrigerant circuit (20). Alternatively, a
plurality of outdoor units (11) and a plurality of indoor units
(12) may be connected together to form a refrigerant circuit
(20).
[0055] In the refrigerant circuit (20), the followings are
provided: a compressor (31); an outdoor heat exchanger (40) which
is a heat-source-side heat exchanger; an indoor heat exchanger (32)
which is a utilization-side heat exchanger; an expansion valve
(33); and a four-way valve (34). The compressor (31), the outdoor
heat exchanger (40), the expansion valve (33), and the four-way
valve (34) are accommodated in the outdoor unit (11). The indoor
heat exchanger (32) is accommodated in the indoor unit (12).
Although not shown in the figure, an outdoor fan configured to
supply outdoor air to the outdoor heat exchanger (40) is provided
in the outdoor unit (11), and an indoor fan configured to supply
indoor air to the indoor heat exchanger (32) is provided in the
indoor unit (12).
[0056] The compressor (31) is a hermetic rotary compressor or a
hermetic scroll compressor. In the refrigerant circuit (20), an
outlet pipe of the compressor (31) is connected to a first port of
the four-way valve (34) through a pipe, and an inlet pipe of the
compressor (31) is connected to a second port of the four-way valve
(34) through a pipe.
[0057] The outdoor heat exchanger (40) includes first and second
header members (46, 47) standing upright, and a plurality of heat
transfer pipes (hereinafter also referred to as "flat tubes") (53,
58). The outdoor heat exchanger (40) is configured to exchange heat
between refrigerant and outdoor air. The structure of the outdoor
heat exchanger (40) will be described in detail later. The indoor
heat exchanger (32) is a so-called "cross-fin type fin-and-tube
heat exchanger," and is configured to exchange heat between
refrigerant and indoor air.
[0058] The expansion valve (33) is a so-called "electronic
expansion valve (33)." The four-way valve (34) includes four ports,
and switches between a first state (state illustrated in FIG. 1) in
which the first port communicates with a third port and the second
port communicates with a fourth port and a second state (state
illustrated in FIG. 2) in which the first port communicates with
the fourth port and the second port communicates with the third
port.
[0059] In the refrigerant circuit (20), a first gas pipe (21), a
second gas pipe (22), and a liquid pipe (23) are provided. The
first gas pipe (21) is, at one end thereof, connected to the third
port of the four-way valve (34), and is, at the other end thereof,
connected to an upper end part of the first header member (46) of
the outdoor heat exchanger (40). The second gas pipe (22) is, at
one end thereof, connected to the fourth port of the four-way valve
(34), and is, at the other end thereof, connected to a gas end of
the indoor heat exchanger (32). The liquid pipe (23) is, at one end
thereof, connected to a lower end part of a first header collecting
pipe (56) which will be described later, and is, at the other end
thereof, connected to a liquid end of the indoor heat exchanger
(32). The expansion valve (33) is provided in the middle of the
liquid pipe (23).
Structure of Outdoor Heat Exchanger
[0060] The structure of the outdoor heat exchanger (40) will be
described in detail with reference to FIGS. 3, 4, and 5. FIG. 3 is
a schematic perspective view of a heat exchanger unit forming the
outdoor heat exchanger of the first embodiment. FIG. 4 is a
schematic front view of the heat exchanger unit forming the outdoor
heat exchanger of the first embodiment. FIG. 5 is an enlarged
perspective view of a main part of the heat exchanger unit of the
first embodiment in the state in which part of the main part is not
shown.
[0061] The outdoor heat exchanger (40) of the present embodiment
includes a single heat exchanger unit (45).
[0062] Referring to FIGS. 3 and 4, the heat exchanger unit (45)
forming the outdoor heat exchanger (40) includes the single first
header member (46), the single second header member (47), the
plurality of heat transfer pipes (53, 58), and a plurality of fins
(54, 59). The first header member (46), the second header member
(47), the flat tubes (53, 58), and the fins (54, 59) are members
made of an aluminum alloy, and are joined together by brazing. The
fin (54, 59) divides part between adjacent ones of the flat tubes
(53, 58) into a plurality of air passages through each of which air
flows.
[0063] The first header member (46) and the second header member
(47) are each formed in an elongated hollow cylindrical shape
closed at both ends thereof. In FIG. 4, the first header member
(46) stands upright at the left of the heat exchanger unit (45),
and the second header member (47) stands upright at the right of
the heat exchanger unit (45). That is, the first header member (46)
and the second header member (47) are mounted in such an attitude
that the axial directions thereof are along the vertical
direction.
[0064] Referring to FIG. 5, the heat transfer pipes (53, 58) are
each formed in a flat shape, and a plurality of refrigerant flow
paths (49) are fanned in line in each of the heat transfer pipes
(53, 58). The heat transfer pipes (53, 58) are hereinafter also
referred to as "flat tubes." FIG. 6 is a schematic view
illustrating an example of a cross-sectional shape of the flat tube
(53, 58). In this example, the width (W2) of the flat tube (58) is,
referring to FIG. 6, greater than the width (W1) of the flat tube
(53). Moreover, the number of flow paths per flat tube (58) is
greater than the number of flow paths per flat tube (53).
[0065] FIG. 7A is a view illustrating an example of a
cross-sectional shape of the refrigerant flow path (49) in the flat
tube (53) for a main heat exchange part (50) which will be
described later, and FIG. 7B is a view illustrating an example of a
cross-sectional shape of the refrigerant flow path (49) in the flat
tube (58) for an auxiliary heat exchange part (55) which will be
described later. In the example illustrated in FIGS. 7A and 7B, a
plurality of grooves (49a) are formed in each of the refrigerant
flow paths (49) of the flat tube (53), whereas the flat tube (58)
is a so-called "bare pipe (smooth inner pipe)" having a circular
cross section. That is, no groove (49a) is formed in each of the
refrigerant flow paths (49) of the flat tube (58). Note that, in
this example, each of the refrigerant flow paths (49) of the flat
tube (58) has a diameter of about 0.5 mm. Needless to say, such
cross-sectional shapes of the refrigerant flow path (49) are set
forth merely for the purpose of examples, and other shapes (e.g., a
rectangular cross section illustrated in FIG. 6) may be
employed.
[0066] In the heat exchanger unit (45), the flat tubes (53, 58) are
arranged at predetermined intervals in the axial direction of the
first and second header members (46, 47) in such an attitude that
the axial direction of the flat tube (53, 58) is along the
horizontal direction and side surfaces of the flat tubes (53, 58)
face each other. That is, in the heat exchanger unit (45), the flat
tubes (53, 58) are arranged parallel to each other between the
first header member (46) and the second header member (47). One end
part of the flat tube (53, 58) is inserted into the first header
member (46), and the other end part of the flat tube (53, 58) is
inserted into the second header member (47). Each of the
refrigerant flow paths (49) in the flat tube (53, 58) communicates,
at one end thereof, with an internal space of the first header
member (46), and communicates, at the other end thereof, with an
internal space of the second header member (47).
[0067] The fin (54, 59) is provided between adjacent ones of the
flat tubes (53, 58). The fin (54, 59) is formed in a corrugated
plate shape meandering up and down, and is mounted in such an
attitude that a ridge line of such a wave shape is along the
front-back direction (direction perpendicular to the plane of paper
of FIG. 4) of the heat exchanger unit (45). In the heat exchanger
unit (45), air passes in the direction perpendicular to the plane
of paper of FIG. 4.
[0068] Referring to FIG. 4, a discoid partition plate (48) is
provided in the first header member (46). The internal space of the
first header member (46) is horizontally divided by the partition
plate (48). On the other hand, the internal space of the second
header member (47) is a single undivided space.
[0069] In the heat exchanger unit (45), the upper part relative to
the partition plate (48) forms the main heat exchange part (50),
and the lower part relative to the partition plate (48) forms the
auxiliary heat exchange part (55).
[0070] Specifically, in the first header member (46), the upper
part relative to the partition plate (48) forms a first header
collecting pipe (51) of the main heat exchange part (50), and the
lower part relative to the partition plate (48) forms the first
header collecting pipe (56) of the auxiliary heat exchange part
(55). Of the flat tubes (53, 58) provided in the heat exchanger
unit (45), the flat tubes (53) connected to the first header
collecting pipe (51) of the main heat exchange part (50) are for
the main heat exchange part (50), and the flat tubes (58) connected
to the first header collecting pipe (56) of the auxiliary heat
exchange part (55) are for the auxiliary heat exchange part (55).
Of the fins (54, 59) provided in the heat exchanger unit (45), the
fins (54) each provided between adjacent ones of the flat tubes
(53) of the main heat exchange part (50) are for the main heat
exchange part (50), and the fins (59) each provided between
adjacent ones of the flat tubes (58) of the auxiliary heat exchange
part (55) are for the auxiliary heat exchange part (55). In the
second header member (47), part of the second header member (47) to
which the flat tubes (53) of the main heat exchange part (50) are
inserted forms a second header collecting pipe (52) of the main
heat exchange part (50), and part of the second header member (47)
to which the flat tubes (58) of the auxiliary heat exchange part
(55) arc inserted forms a second header collecting pipe (57) of the
auxiliary heat exchange part (55).
[0071] In the outdoor heat exchanger (40), the width (W1) of the
flat tube (53) of the main heat exchange part (50), the number of
refrigerant flow paths (49), the cross-sectional area of the
refrigerant flow path (49), the number of flat tubes (53), etc. are
determined based on requirements of a heat exchange capacity
required for air-cooing and air-heating. In general, the number of
flat tubes (53, 58) which can be provided in the outdoor heat
exchanger (40) is limited. Thus, e.g., the number of flat tubes
(58) is the number obtained by subtracting the number of flat tubes
(53) from the maximum possible number. Then, based on the
determined number of flat tubes (53, 58), the width (W2) of the
flat tube (58), the number of refrigerant flow paths (49), and the
cross-sectional area of the refrigerant flow path (49) are set
depending on the capacity required for the auxiliary heat exchange
part (55).
[0072] Specifically, in the outdoor heat exchanger (40) of the
present embodiment, the number of flat tubes (58) of the auxiliary
heat exchange part (55) is less than the number of flat tubes (53)
of the main heat exchange part (50). The total cross-sectional area
of refrigerant flow paths (49) per flat tube (58) provided in the
auxiliary heat exchange part (55) is greater than the total
cross-sectional area of refrigerant flow paths (49) per flat tube
(53) provided in the main heat exchange part (50).
[0073] In this example, sixty flat tubes (53, 58) are provided in
the outdoor heat exchanger (40). The number of flat tubes (58) of
the auxiliary heat exchange part (55) is ten, and the number of
flat tubes (53) of the main heat exchange part (50) is fifty. That
is, the number of flat tubes (58) of the auxiliary heat exchange
part (55) is one-fifth of the number of flat tubes (53) of the main
heat exchange part (50). Note that the number of flat tubes (53,
58) illustrated in FIGS. 3 and 4 is different from the actual
number of flat tubes (53, 58) provided in the outdoor heat
exchanger (40).
[0074] As described above, in the refrigerant circuit (20), the
first gas pipe (21) is connected to the upper end part of the first
header member (46), and the liquid pipe (23) is connected to a
lower end part of the first header member (46) (see FIG. 1). That
is, in the outdoor heat exchanger (40), the first gas pipe (21) is
connected to the first header collecting pipe (51) of the main heat
exchange part (50), and the liquid pipe (23) is connected to the
first header collecting pipe (56) of the auxiliary heat exchange
part (55).
Operations
[0075] The operations of the air conditioner (10) will be
described. The air conditioner (10) performs the air-cooling
operation which is a cooling process and the air-heating operation
which is a heating process.
Air-Cooling Operation
[0076] The process in the air-cooling operation of the air
conditioner (10) will be described with reference to FIG. 1.
[0077] In the air-cooling operation, the four-way valve (34) is set
at the first state. Moreover, the degree of opening of the
expansion valve (33) is adjusted such that the degree of superheat
of refrigerant flowing out from the gas end of the indoor heat
exchanger (32) reaches a predetermined target value (e.g.,
5.degree. C.). Further, in the air-cooling operation, outdoor air
is supplied to the outdoor heat exchanger (40) by the outdoor fan,
and indoor air is supplied to the indoor heat exchanger (32) by the
indoor fan.
[0078] In the refrigerant circuit (20), refrigerant discharged from
the compressor (31) passes through the four-way valve (34) and the
first gas pipe (21) in this order, and then flows into the first
header collecting pipe (51) of the main heat exchange part (50).
The refrigerant flowing into the first header collecting pipe (51)
flows into the flat tubes (53) of the main heat exchange part (50).
While passing through each of the refrigerant flow paths (49) of
the flat tubes (53), the refrigerant is condensed by dissipating
heat to outdoor air. After passing through the flat tubes (53), the
refrigerant flows into the second header collecting pipe (52) of
the main heat exchange part (50), and then flows down to the second
header collecting pipe (57) of the auxiliary heat exchange part
(55). The refrigerant flowing into the second header collecting
pipe (57) flows into the flat tubes (58) of the auxiliary heat
exchange part (55). While passing through each of the refrigerant
flow paths (49) of the flat tubes (58), the refrigerant enters a
sub-cooling state by dissipating heat to outdoor air. After passing
through the flat tubes (58), the refrigerant flows into the first
header collecting pipe (56) of the auxiliary heat exchange part
(55).
[0079] The refrigerant flowing into the liquid pipe (23) from the
first header collecting pipe (56) of the auxiliary heat exchange
part (55) is expanded (i.e., the pressure of refrigerant is
reduced) upon passage of the expansion valve (33), and then flows
into the liquid end of the indoor heat exchanger (32). The
refrigerant flowing into the indoor heat exchanger (32) is
evaporated by absorbing heat from indoor air. The indoor unit (12)
supplies taken indoor air to the indoor heat exchanger (32), and
sends indoor air cooled by the indoor heat exchanger (32) back to a
room.
[0080] The refrigerant evaporated in the indoor heat exchanger (32)
flows into the second gas pipe (22) from the gas end of the indoor
heat exchanger (32). Subsequently, the refrigerant is sucked into
the compressor (31) through the four-way valve (34). The compressor
(31) compresses the taken refrigerant and then discharge the
compressed refrigerant.
Air-Heating Operation
[0081] The process in the air-heating operation of the air
conditioner (10) will be described with reference to FIG. 2.
[0082] In the air-heating operation, the four-way valve (34) is set
at the second state. Moreover, the degree of opening of the
expansion valve (33) is adjusted such that the degree of superheat
of refrigerant flowing out from the outdoor heat exchanger (40)
reaches a predetermined target value (e.g., 5.degree. C.). Further,
in the air-heating operation, outdoor air is supplied to the
outdoor heat exchanger (40) by the outdoor fan, and indoor air is
supplied to the indoor heat exchanger (32) by the indoor fan.
[0083] In the refrigerant circuit (20), refrigerant discharged from
the compressor (31) passes through the four-way valve (34) and the
second gas pipe (22) in this order, and then flows into the gas end
of the indoor heat exchanger (32). The refrigerant flowing into the
indoor heat exchanger (32) is condensed by dissipating heat to
indoor air. The indoor unit (12) supplies taken indoor air to the
indoor heat exchanger (32), and sends indoor air heated by the
indoor heat exchanger (32) back to a room.
[0084] The refrigerant flowing into the liquid pipe (23) from the
liquid end of the indoor heat exchanger (32) is expanded (i.e., the
pressure of refrigerant is reduced) upon passage of the expansion
valve (33), and then flows into the first header collecting pipe
(56) of the auxiliary heat exchange part (55). The refrigerant
flowing into the first header collecting pipe (56) of the auxiliary
heat exchange part (55) flows into the flat tubes (58) of the
auxiliary heat exchange part (55). While passing through the
refrigerant flow paths (49), the refrigerant flowing into each of
the flat tubes (58) absorbs heat from outdoor air, and part of the
refrigerant is evaporated. The refrigerant evaporated in the flat
tubes (58) flows into the second header collecting pipe (52), and
then flows into the flat tubes (53) of the main heat exchange part
(50). While passing through the refrigerant flow paths (49), the
refrigerant flowing into each of the flat tubes (53) is evaporated
by absorbing heat from outdoor air.
[0085] After passing through the flat tubes (53) of the main heat
exchange part (50), the refrigerant flows into the first header
collecting pipe (51) of the main heat exchange part (50), and then
flows into the first gas pipe (21). After passing through the
four-way valve (34), the refrigerant flowing through the first gas
pipe (21) is sucked into the compressor (31). The compressor (31)
compresses the taken refrigerant and discharges the compressed
refrigerant.
Advantages of the Present Embodiment
[0086] In the present embodiment, the number of flat tubes (58)
forming the auxiliary heat exchange part (55) is less than the
number of flat tubes (53) forming the main heat exchange part (50).
However, the total cross-sectional area of refrigerant flow paths
(49) per flat tube (58) provided in the auxiliary heat exchange
part (55) is greater than the total cross-sectional area of
refrigerant flow paths (49) per flat tube (53) provided in the main
heat exchange part (50). Thus, in the case where the heat exchanger
serves as a condenser, the flow velocity of refrigerant in the
auxiliary heat exchange part (55) can be lowered as compared to,
e.g., a heat exchanger (hereinafter, for the sake of simplicity of
description, referred to as a "conventional heat exchanger") in
which a single type of flat tubes fauns a main heat exchanger part
and an auxiliary heat exchange part. Consequently, according to the
present embodiment, a pressure loss in the auxiliary heat exchange
part (55) can be reduced.
[0087] In the present embodiment, the number of flow paths per flat
tube (53, 58) and the width (W1, W2) of the flat tube (53, 58) are
adjusted so that the total cross-sectional area of refrigerant flow
paths (49) per flat tube (53, 58) can be set. Thus, the total
cross-sectional area of refrigerant flow paths (49) in the flat
tube (53) for the main heat exchange part (50) and the total
cross-sectional area of refrigerant flow paths (49) in the flat
tube (58) for the auxiliary heat exchange part (55) can be easily
set.
[0088] In the present embodiment, the grooves (49a) are formed in
each of the refrigerant flow paths (49) of the flat tube (53) in
the main heat exchange part (50). Thus, in the flat tube (53), the
surface area per refrigerant flow path (49) can be increased. That
is, a heat exchange efficiency in the main heat exchange part (50)
can be improved.
[0089] Since the flat tube (58) of the auxiliary heat exchange part
(55) is the so-called "bare pipe," a pressure loss due to a pipe
shape can be reduced as compared to the flat tube (53) of the main
heat exchange part (50).
[0090] The refrigerant flow path (49) has, as described above, an
extremely-small diameter. Thus, when the outdoor heat exchanger
(40) is manufactured at a factory, if, e.g., flat tubes having the
same width form a main heat exchange part and an auxiliary heat
exchange part, it is difficult to identify, with eyes, the
presence/absence of the grooves (49a) of the refrigerant flow path
(49). However, in the present embodiment, since the flat tube (53)
for the main heat exchange part (50) and the flat tube (58) for the
auxiliary heat exchange part (55) have the different widths (W1,
W2), the presence/absence of the grooves (49a) of the refrigerant
flow path (49) can be easily identified.
First Variation of First Embodiment
[0091] The configuration of the fins (54, 59) has been set forth
merely for the purpose of an example, and various types of fins may
be employed for the heat exchanger (40). For example, a fin
illustrated in FIG. 8 may be employed, instead of the fins (54,
59). FIG. 8 is a view illustrating part of a cross section of a
heat exchanger (40) of a first variation of the first embodiment. A
fin (235) is a corrugated fin meandering up and down, and is
arranged between adjacent ones of flat tubes (heat transfer pipes)
(53, 58) which are respectively at the top and bottom of the fin
(235). Although will be described in detail later, a plurality of
heat transfer parts (237) and a plurality of middle plate parts
(241) are formed in the fin (235). In the fin (235), the middle
plate parts (241) are joined to the flat tube (53, 58) by
brazing.
Configuration of Fin
[0092] FIG. 9 is a schematic perspective view of the fin (235)
provided in the heat exchanger (40) of the first variation.
Referring to FIG. 9, the fin (235) is the corrugated fin formed in
such a manner that a metal plate having a uniform width is bent,
and is in the shape meandering up and down. In the fin (235), the
heat transfer parts (237) and the middle plate parts (241) are
alternately formed along an extension direction of the flat tube
(53, 58). That is, in the fin (235), the plurality of heat transfer
parts (237) arranged in the extension direction of the flat tube
(53, 58) are provided between the adjacent ones of the flat tubes
(53, 58). Moreover, in the fin (235), protruding plate parts (242)
are foamed. Note that louvers (250, 260, 270) and a water guide rib
(271) which will be described later are not shown in FIG. 9.
[0093] The heat transfer part (237) is a plate-shaped part
extending from one of adjacent ones of the flat tubes (53, 58) to
the other one of the adjacent ones of the flat tubes (53, 58). In
the heat transfer part (237), an end part thereof on a windward
side is a front edge (238). Although not shown in FIG. 9, the
plurality of louvers (250, 260) are formed in the heat transfer
part (237). The middle plate part (241) is a plate-shaped part
along flat side surfaces of the flat tubes (53, 58), and is
continuous to upper ends of adjacent ones of the heat transfer
parts (237) or lower ends of adjacent ones of the heat transfer
parts (237). The angle formed between the heat transfer part (237)
and the middle plate part (241) is the substantially right
angle.
[0094] The protruding plate part (242) is a plate-shaped part
continuously formed with an end part of the heat transfer part
(237) on a leeward side. The protruding plate part (242) is formed
in a vertically-elongated plate shape, and protrudes beyond the
flat tube (53, 58) toward the leeward side. An upper end of the
protruding plate part (242) upwardly protrudes beyond the upper end
of the heat transfer part (237), and a lower end of the protruding
plate part (242) downwardly protrudes beyond the lower end of the
heat transfer part (237). Referring to FIG. 8, in the outdoor heat
exchanger (40), adjacent ones of the protruding plate parts (242)
of the fins (235) sandwiching the flat tube (53, 58) at the top and
bottom thereof contact each other. In the protruding plate part
(242) of the fin (235), the water guide rib (271) is formed. The
water guide rib (271) is an elongated recessed groove vertically
extending along an end part of the protruding plate part (242) on
the leeward side.
[0095] FIGS. 10A and 10B are views illustrating the heat transfer
part (237) provided in the fin (235) of the outdoor heat exchanger
(40) of the first variation. FIG. 10A is a front view of the heat
exchange part, and FIG. 10B is a cross-sectional view along a B-B
line illustrated in FIG. 10A. Referring to FIGS. 10A and 10B, in
the heat transfer part (237) and the protruding plate part (242) of
the fin (235), the plurality of louvers (250, 260, 270) are formed.
The louver (250, 260, 270) is formed in such a manner that part of
the heat transfer part (237) or the protruding plate part (242) is
cut and is folded up. That is, the louvers (250, 260, 270) are
formed in such a manner that a plurality of slit-shaped cut is
formed in the heat transfer part (237) and the protruding plate
part (242) and part between adjacent ones of the cuts is
plastically deformed by twisting.
Second Variation of First Embodiment
[0096] FIG. 11A is a partial cross-sectional view of a heat
exchanger (40) of a second variation, and FIG. 11B is a
cross-sectional view of a fin along a V-V line illustrated in FIG.
11A. In this example, a plurality of waffle parts (251, 252, 253)
are formed, instead of the louvers (250, 260, 270) described in the
first variation. Referring to FIGS. 11A and 11B, in a heat transfer
part (237) and a protruding plate part (242) of a fin (235), the
plurality of waffle parts (251, 252, 253) are fanned. The waffle
part (251, 252, 253) is a protrusion protruding toward a side on
which an air passage is formed and formed in a vertically elongated
shape. The waffle parts (251, 252, 253) are formed in such a manner
that part of the heat transfer part (237) is plastically deformed
by, e.g., pressing. The waffle part (251, 252, 253) extends in a
direction inclined relative to the vertical direction such that a
lower end part of the waffle part (251, 252, 253) is positioned on
the leeward side relative to an upper end part thereof.
[0097] The waffle part (251, 252, 253) has a pair of
vertically-elongated trapezoidal surfaces (254) and a pair of flat
upper and lower triangular surfaces (255). The trapezoidal surfaces
(254) are adjacent to each other in an air passage direction so as
to form a ridge part (256) forming a ridge line. The triangular
surfaces (255) are formed respectively at the top and bottom of the
ridge part (256).
[0098] In the heat transfer part (237), the plurality of waffle
parts (251, 252, 253) are formed so as to be arranged from the
windward side to the leeward side. The waffle parts (251, 252, 253)
are the single windward-side waffle part (251) formed on the
windward side of the heat transfer part (237), the two leeward-side
waffle parts (253) formed on the leeward side of the heat transfer
part (237), and the single middle waffle part (252) formed between
the windward-side waffle part (251) and the leeward-side waffle
part (253). Of the waffle parts (251, 252, 253), the windward-side
waffle part (251) is a windward-side protrusion formed on the most
windward side. Of the waffle parts (251, 252, 253), the
leeward-side waffle part (253) is a leeward-side protrusion formed
on the most leeward side.
[0099] An upper end of the windward-side waffle part (251) is
positioned lower than that of the leeward-side waffle part (253).
Moreover, an upper end of the middle waffle part (252) and the
upper end of the leeward-side waffle part (253) are at the
substantially same height. The upper end of the windward-side
waffle part (251), the upper end of the middle waffle part (252),
and the upper ends of the leeward-side waffle part (253) are
substantially parallel to a flat surface of a flat tube (53, 58)
provided on an upper side thereof.
[0100] A lower end of the windward-side waffle part (251) is
positioned higher than that of the leeward-side waffle part (253).
The lower end of the windward-side waffle part (251) is inclined
such that part of the lower end of the windward-side waffle part
(251) on the leeward side is positioned lower than that on the
windward side. A lower end of the middle waffle part (252) is also
inclined such that part of the lower end of the middle waffle part
(252) on the leeward side is positioned lower than that on the
windward side. The lower end of the leeward-side waffle parts (253)
are substantially parallel to the flat surface of the flat tube
(53, 58).
Third Variation of First Embodiment
[0101] A fin illustrated in FIG. 12 may be employed, instead of the
fins (54, 59). FIG. 12 is a view illustrating part of a cross
section of a heat exchanger (40) of a third variation of the first
embodiment.
Configuration of Fin
[0102] Referring to FIG. 12, a fin (236) is an elongated
plate-shaped fin formed in such a manner that a metal plate is
pressed. In the fin (236), a plurality of elongated cut parts (245)
each extending from a front edge (238) of the fin (236) in a width
direction of the fin (236) are formed. In the fin (236), the cut
parts (245) are formed at predetermined intervals in a longitudinal
direction of the fin (236). Part of the cut part (245) on the
leeward side forms a pipe insertion part (246). The pipe insertion
part (246) has a vertical width substantially equal to the
thickness of a flat tube (53, 58). Moreover, the length (depth) of
the pipe insertion part (246) is substantially equal to the width
of the flat tube (58) having a greater width. Since the depth of
the pipe insertion part (246) corresponds, as described above, to
the width of the flat tube (58) having a greater width, a single
type of fins (236) can be used. That is, plural types of molds are
not necessarily prepared for manufacturing of the fins (236), and
reduction in manufacturing cost can be expected. The flat tube (53,
58) is inserted into a corresponding one of the pipe insertion
parts (246) of the fin (236), and is joined to a peripheral edge
part of the pipe insertion part (246) by brazing. In the present
embodiment, an end of the flat tube (53, 58) in a width direction
thereof is aligned with an end of the cut part (245) on an open
side thereof. Since the length of the pipe insertion part (246)
corresponds to the width (W2) of the flat tube (58), a clearance is
formed on a closed side of the pipe insertion part (246) in the
state in which the flat tube (53) is inserted into the pipe
insertion part (246).
[0103] For example, the fin (236) and the flat tube (53, 58) are
brazed with each other as follows. First, a side of the fin (236)
close to the cut part (245) (i.e., the left side as viewed in FIG.
12) faces up. Then, the end of the flat tube (53, 58) in the width
direction thereof is set so as to be aligned with the end of the
inlet side of the cut part (245) on the open side thereof, more
specifically an end of the pipe insertion part (246) on an open
side thereof (i.e., the left end as viewed in FIG. 12). A brazing
material is applied in a linear shape at a position (A) illustrated
in FIG. 12. Note that the application position (A) is illustrated
only for one of the flat tubes (53) in FIG. 12, but the same
applies to the other flat tubes (53, 58). If an attempt is made to
cause the flat tube (53) to contact the deepest part of the pipe
insertion part (246), the brazing material drops, upon brazing,
into the pipe insertion part (246), and therefore it is difficult
to set the brazing material. However, in the present embodiment,
since the end of the flat tube (53, 58) in the width direction
thereof is aligned with the end of the cut part (245) on the open
side thereof as described above, the brazing material can be easily
set.
[0104] Subsequently, e.g., the heat exchanger (40) is placed in a
heating furnace (not shown in the figure), and the brazing material
is melted. This allows the brazing material to flow along the flat
tube (53, 58), and therefore the fin (236) and the flat tube (53,
58) are joined together.
[0105] In the fin (236), part between adjacent ones of the cut
parts (245) fauns a heat transfer part (237), and part of the pipe
insertion part (246) on the leeward side forms a leeward-side plate
part (247). That is, in the fin (236), a plurality of heat transfer
parts (237) adjacent to each other with the flat tube (53, 58)
being interposed between adjacent ones of the heat transfer parts
(237), and a single leeward-side plate part (247) continuously
formed in end parts of the heat transfer parts (237) on the leeward
side are provided. In the heat exchanger (40), each of the heat
transfer parts (237) of the fin (236) is arranged between adjacent
ones of the flat tubes (53, 58) arranged in the vertical direction,
and the leeward-side plate part (247) protrudes beyond the flat
tubes (53, 58) toward the leeward side.
[0106] FIGS. 13A and 13B are views illustrating a main part of the
fin (236) of the heat exchanger (40) of the third variation. FIG.
13A is a front view of the fin (236), and FIG. 13B is a
cross-sectional view along a G-G line illustrated in FIG. 13A.
Referring to FIG. 13, in the heat transfer part (237) and the
leeward-side plate part (247), a plurality of louvers (250, 260)
are formed. The louver (250, 260) is formed in such a manner that
part of the heat transfer part (237) or the leeward-side plate part
(247) is cut and is folded up.
Fourth Variation of First Embodiment
[0107] FIG. 14A is a partial cross-sectional view of a heat
exchanger (40) of a fourth variation, and FIG. 14B is a
cross-sectional view of a fin (236) along an X-X line illustrated
in FIG. 14A. In this example, waffle parts (251, 252, 253) are,
instead of the louvers (250, 260), formed in the plate-shaped fin
described in the third variation. The waffle parts (251, 252, 253)
has a configuration similar to that described in the second
variation.
Second Embodiment of the Invention
[0108] An outdoor heat exchanger of a second embodiment of the
present disclosure will be described. FIG. 15 is a front view
illustrating a schematic configuration of the outdoor heat
exchanger (40) of the second embodiment. Moreover, FIG. 16 is a
partial cross-sectional view illustrating a front side of the
outdoor heat exchanger (40) of the second embodiment.
[0109] Referring to FIG. 15, the outdoor heat exchanger (40) is
divided into three heat exchange parts (350a-350c). Specifically,
in the outdoor heat exchanger (40), the first exchange part (350a),
the second exchange part (350b), and the third exchange part (350c)
are formed in this order from the bottom to the top.
[0110] Referring to FIG. 16, in each of a first header collecting
pipe (360) and a second header collecting pipe (370), three
communication spaces (361a-361c, 371a-371c) are formed in such a
manner that each of inner spaces of the first header collecting
pipe (360) and the second header collecting pipe (370) is divided
by partition plates (339).
[0111] The communication space (361a-361c) of the first header
collecting pipe (360) is further horizontally divided by a
partition plate (339). In the communication space (361a-361c) of
the first header collecting pipe (360), the lower space is a lower
space (362a-362c) which is a first space, and the upper space is an
upper space (363a-363c) which is a second space.
[0112] The exchange part (350a-350c) of the outdoor heat exchanger
(40) is divided into a main heat exchange region (main heat
exchange part) (351a-351c) and an auxiliary heat exchange region
(auxiliary heat exchange part) (352a-352c). In the exchange part
(350a-350c), eleven flat tubes (53) communicating with a
corresponding one of the upper spaces (363a-363c) of the first
header collecting pipe (360) form the main heat exchange part
(351a-351c), and three flat tubes (58) communicating with a
corresponding one of the lower spaces (362a-362c) of the first
header collecting pipe (360) form the auxiliary heat exchange part
(352a-352c).
[0113] In the present embodiment, the width of the flat tube (58)
provided in the auxiliary heat exchange part (352a-352c) is, as in
the first embodiment, greater than that of the flat tube (53)
provided in the main heat exchange part (351a-351c). Moreover, the
number of flow paths per flat tube (58) provided in the auxiliary
heat exchange part (352a-352c) is greater than the number of flow
paths per flat tube (53) provided in the main heat exchange part
(351a-351c). In this example, fins (corrugated fins) (235) are
employed as fins. Needless to say, the fins (54, 59) described in
the first embodiment or the fins (236) described in the other
variations may be employed.
[0114] Referring to FIG. 15, in the outdoor heat exchanger (40), a
liquid connection member (380) and a gas header (385) are provided.
The liquid connection member (380) and the gas header (385) are
attached to the first header collecting pipe (360).
[0115] The liquid connection member (380) includes a single
distributor (381) and three thin pipes (382a-382c). A pipe
connecting between the outdoor heat exchanger (40) and an expansion
valve (33) is connected to a lower end part of the distributor
(381). The thin pipe (382a-382c) is, at one end thereof, connected
to an upper end part of the distributor (381). In the distributor
(381), the pipe connected to the lower end part thereof and the
thin pipes (382a-382c) communicate with each other. The thin pipe
(382a-382c) is, at the other end, connected to the first header
collecting pipe (360), and communicates with a corresponding one of
the lower spaces (362a-362c).
[0116] The gas header (385) includes a single main pipe part (386)
and three connection pipe parts (387a-387c). The main pipe part
(386) is formed in a pipe shape curving in an inverted U-shape at
an upper part thereof and having a relatively-large diameter. A
pipe connecting between the outdoor heat exchanger (40) and a third
port of a four-way valve (34) is connected to an upper end part of
the main pipe part (386). A lower end part of the main pipe part
(386) is closed. The connection pipe parts (387a-387c) laterally
protrude from a straight part of the main pipe part (386).
[0117] According to the foregoing configuration, in the outdoor
heat exchanger (40) of the present embodiment, refrigerant flows in
a direction indicated by arrows illustrated in FIG. 15 in an
air-cooling operation. In an air-heating operation, refrigerant
flows in a direction opposite to the direction indicated by the
arrows illustrated in FIG. 15.
Third Embodiment of the Invention
[0118] An outdoor heat exchanger of a third embodiment of the
present disclosure will be described. FIG. 17 is a front view
illustrating a schematic configuration of the outdoor heat
exchanger (40) of the third embodiment. Moreover, FIG. 18 is a
partial cross-sectional view illustrating a front side of the
outdoor heat exchanger (40) of the third embodiment.
[0119] Referring to FIGS. 17 and 18, the outdoor heat exchanger
(40) includes a single first header collecting pipe (460), a single
second header collecting pipe (470), a plurality of flat tubes (53,
58), and a plurality of fins (235).
[0120] Referring to FIG. 17, the flat tubes (53, 58) of the outdoor
heat exchanger (40) are divided for two upper and lower heat
exchange regions (451, 452). That is, in the outdoor heat exchanger
(40), the upper heat exchange region (451) and the lower heat
exchange region (452) are formed. The heat exchange region (451,
452) is horizontally divided into three heat exchange parts
(451a-451c, 452a-452c). Specifically, in the upper heat exchange
region (451), the first main heat exchange part (451a), the second
main heat exchange part (451b), and the third main heat exchange
part (451c) are formed in this order from the bottom to the top. In
the lower heat exchange region (452), the first auxiliary heat
exchange part (452a), the second auxiliary heat exchange part
(452b), and the third auxiliary heat exchange part (452c) are
formed in this order from the bottom to the top. As in the
foregoing, in the outdoor heat exchanger (40) of the present
embodiment, the upper heat exchange region (451) and the lower heat
exchange region (452) are each divided into the plurality of heat
exchange parts (451a-451c, 452a-452c), the number of which is the
same between the upper heat exchange region (451) and the lower
heat exchange region (452). Referring to FIG. 18, the main heat
exchange part (451a-451c) includes eleven flat tube (53), and the
auxiliary heat exchange part (452a-452c) includes three flat tubes
(58). Note that the number of heat exchange parts (451a-451c,
452a-452c) formed in the heat exchange region (451, 452) may be two
or may be equal to or greater than four.
[0121] In the present embodiment, the width of the flat tube (58)
provided in the auxiliary heat exchange part (452a-452c) is, as in
the first embodiment, greater than that of the flat tube (53)
provided in the main heat exchange part (451a-451c). Moreover, the
number of flow paths per flat tube (58) provided in the auxiliary
heat exchange part (452a-452c) is greater than the number of flow
paths per flat tube (53) provided in the main heat exchange part
(451a-451c).
[0122] Internal spaces of the first header collecting pipe (460)
and the second header collecting pipe (470) are each horizontally
divided by a plurality of partition plates (439).
[0123] Specifically, the internal space of the first header
collecting pipe (460) is divided into an upper space (461)
corresponding to the upper heat exchange region (451) and a lower
space (462) corresponding to the lower heat exchange region (452).
The upper space (461) is a single space corresponding to all of the
main heat exchange parts (451a-451c). That is, the upper space
(461) communicates with all of the flat tubes (53) of the main heat
exchange parts (451a-451c). The lower space (462) is, by the
partition plates (439), further horizontally divided into
communication spaces (462a-462c) corresponding to the auxiliary
heat exchange parts (452a-452c) such that the number (i.e., three)
of the communication spaces (462a-462c) is the same as that of the
auxiliary heat exchange parts (452a-452c).
[0124] That is, in the lower space (462), the first communication
space (462a) communicating with the flat tubes (58) of the first
auxiliary heat exchange part (452a), the second communication space
(462b) communicating with the flat tubes (58) of the second
auxiliary heat exchange part (452b), and the third communication
space (462c) communicating with the flat tubes (58) of the third
auxiliary heat exchange part (452c) are formed.
[0125] The internal space of the second header collecting pipe
(470) is horizontally divided into five communication spaces
(471a-471c). Specifically, the internal space of the second header
collecting pipe (470) is divided into the four communication spaces
(471a, 471b, 471d, 471e) corresponding to the main heat exchange
parts (451b, 451c) and the auxiliary heat exchange parts (452a,
452b) other than the first main heat exchange part (451a)
positioned lowermost in the upper heat exchange region (451) and
the third auxiliary heat exchange part (452c) positioned uppermost
in the lower heat exchange region (452), and into the single
communication space (471c) corresponding to both of the first main
heat exchange part (451a) and the third auxiliary heat exchange
part (452c). That is, in the internal space of the second header
collecting pipe (470), the first communication space (471a)
communicating with the flat tubes (58) of the first auxiliary heat
exchange part (452a), the second communication space (471b)
communicating with the flat tubes (58) of the second auxiliary heat
exchange part (452b), the third communication space (471c)
communicating with the flat tubes (53, 58) of both of the third
auxiliary heat exchange part (452c) and the first main heat
exchange part (451a), the fourth communication space (471d)
communicating with the flat tubes (53) of the second main heat
exchange part (451b), and the fifth communication space (471e)
communicating with the flat tubes (53) of the third main heat
exchange part (451c) arc formed.
[0126] In the second header collecting pipe (470), the fourth
communication space (471d) and the fifth communication space (471e)
are paired respectively with the first communication space (471a)
and the second communication space (471b). Specifically, the first
communication space (471a) and the fourth communication space
(471d) are paired together, and the second communication space
(471b) and the fifth communication space (471e) are paired
together. Moreover, in the second header collecting pipe (470), a
first communication pipe (472) connecting between the first
communication space (471a) and the fourth communication space
(471d) and a second communication pipe (473) connecting between the
second communication space (471b) and the fifth communication space
(471e) are provided. That is, in the outdoor heat exchanger (40) of
the present embodiment, the first main heat exchange part (451a)
and the third auxiliary heat exchange part (452c) are paired
together, the second main heat exchange part (451b) and the first
auxiliary heat exchange part (452a) are paired together, and the
third main heat exchange part (451c) and the second auxiliary heat
exchange part (452b) are paired together. Note that the number of
pairs of the heat exchange parts (451a-451e, 452a-452c) formed in
the outdoor heat exchanger (40) is suitably set depending on the
height of the outdoor heat exchanger (40) such that the total
height of the main heat exchange part (451a-451c) and the auxiliary
heat exchange part (452a-452c) which are to be paired together is
equal to or lower than about 350 mm (preferably about 300-350
mm)
[0127] As in the foregoing, in the internal space of the second
header collecting pipe (470), the communication spaces (471c, 471d,
471e) corresponding to the main heat exchange parts (451a-451c) of
the upper heat exchange region (451) are formed such that the
number thereof (e.g., three) is the same as that of the main heat
exchange parts (451a-451c). Moreover, the communication spaces
(471a, 471b, 471c) corresponding to the auxiliary heat exchange
parts (452a-452c) of the lower heat exchange region (452) are
formed such that the number thereof (e.g., three) is the same as
that of the auxiliary heat exchange parts (452a-452c). Further, the
communication spaces (471c, 471d, 471e) corresponding to the upper
heat exchange region (451) and the communication spaces (471a,
471b, 471c) corresponding to the lower heat exchange region (452)
communicate with each other.
[0128] Referring to FIG. 17, in the outdoor heat exchanger (40), a
liquid connection member (480) and a gas connection member (485)
are provided. The liquid connection member (480) and the gas
connection member (485) are attached to the first header collecting
pipe (460).
[0129] The liquid connection member (480) includes a single
distributor (481) and three thin pipes (482a-482c). A pipe
connecting between the outdoor heat exchanger (40) and an expansion
valve (33) is connected to a lower end part of the distributor
(481). The thin pipe (482a-482c) is, at one end thereof, connected
to an upper end part of the distributor (481). In the distributor
(481), the pipe connected to the lower end part and the thin pipes
(482a-482c) communicate with each other. The thin pipe (482a-482c)
is, at the other end thereof, connected to the lower space (462) of
the first header collecting pipe (460), and communicates with a
corresponding one of the communication spaces (462a-462c).
[0130] Referring to FIG. 18, the thin pipe (482a-482c) opens at
part of a corresponding one of the communication spaces (462a-462c)
close to a lower end thereof. That is, the first thin pipe (482a)
opens at part of the first communication space (462a) close to the
lower end thereof, the second thin pipe (482b) opens at part of the
second communication space (462b) close to the lower end thereof,
and the third thin pipe (482c) opens at part of the third
communication space (462c) close to the lower end thereof. Note
that the length of the thin pipe (482a-482c) is independently set
such that the difference in flow rate of refrigerant flowing into
the auxiliary heat exchange parts (452a-452c) is reduced as much as
possible.
[0131] The gas connection member (485) is formed of a single pipe
having a relatively-large diameter. The gas connection member (485)
is, at one end thereof, connected to a pipe connecting between the
outdoor heat exchanger (40) and a third port of a four-way valve
(34).
[0132] The gas connection member (485) opens, at the other end
thereof, part of the upper space (461) close to an upper end
thereof in the first header collecting pipe (460).
[0133] According to the foregoing configuration, in the outdoor
heat exchanger (40) of the present embodiment, refrigerant flows in
a direction indicated by arrows illustrated in FIG. 17 in an
air-cooling operation. In an air-heating operation, refrigerant
flows in a direction opposite to the direction indicated by the
arrows illustrated in FIG. 17.
Fourth Embodiment of the Invention
[0134] An outdoor heat exchanger of a fourth embodiment of the
present disclosure will be described. FIG. 19 is a front view
illustrating a schematic configuration of the outdoor heat
exchanger (40) of the fourth embodiment. Moreover, FIG. 20 is a
partial cross-sectional view illustrating a front side of the
outdoor heat exchanger (40) of the fourth embodiment.
[0135] Referring to FIG. 19, flat tubes (53, 58) of the outdoor
heat exchanger (40) are, as in the third embodiment, horizontally
divided for an upper heat exchange region (451) and a lower heat
exchange region (452). The upper heat exchange region (451) is
divided into three main heat exchange parts (451a-451c) arranged in
the vertical direction, and the lower heat exchange region (452) is
formed of a single auxiliary heat exchange part (452a). That is, in
the upper heat exchange region (451), the first main heat exchange
part (451a), the second main heat exchange part (451b), and the
third main heat exchange part (451c) are formed in this order from
the bottom to the top. Referring to FIG. 20, the main heat exchange
part (451a-451c) includes eleven flat tubes (53), and the auxiliary
heat exchange part (452a) includes nine flat tubes (58). Note that
the number of main heat exchange parts (451a-451c) formed in the
upper heat exchange region (451) may be two or may be equal to or
greater than four.
[0136] Internal spaces of a first header collecting pipe (460) and
a second header collecting pipe (470) are each horizontally divided
by partition plates (439).
[0137] In the present embodiment, the width of the flat tube (58)
provided in the auxiliary heat exchange part (452a) is, as in the
first embodiment, greater than that of the flat tube (53) provided
in the main heat exchange part (451a-451c). Moreover, the number of
flow paths per flat tube (58) provided in the auxiliary heat
exchange part (452a) is greater than the number of flow paths per
flat tube (53) provided in the main heat exchange part
(451a-451c).
[0138] Specifically, the internal space of the first header
collecting pipe (460) is divided into an upper space (461)
corresponding to the upper heat exchange region (451), and a lower
space (462) (communication space (462a)) corresponding to the lower
heat exchange region (452). The upper space (461) is a single space
corresponding to all of the main heat exchange parts (451a-451c).
That is, the upper space (461) communicates with all of the flat
tubes (53) of the main heat exchange parts (451a-451c). The lower
space (462) (communication space (462a)) is a single space
corresponding to the single auxiliary heat exchange part (452a),
and communicates with the flat tubes (58) of the auxiliary heat
exchange part (452a).
[0139] The internal space of the second header collecting pipe
(470) is horizontally divided into four communication spaces
(471a-471d). Specifically, the internal space of the second header
collecting pipe (470) is divided into three communication spaces
(471b, 471c, 471d) corresponding respectively to the main heat
exchange parts (451a-451c) of the upper heat exchange region (451),
and a single communication space (471a) corresponding to the
auxiliary heat exchange part (452a) of the lower heat exchange
region (452). That is, in the internal space of the second header
collecting pipe (470), the first communication space (471a)
communicating with the flat tubes (58) of the auxiliary heat
exchange part (452a), the second communication space (471b)
communicating with the flat tubes (53) of the first main heat
exchange part (451a), the third communication space (471c)
communicating with the flat tubes (53) of the second main heat
exchange part (451b), and the fourth communication space (471d)
communicating with the flat tubes (53) of the third main heat
exchange part (451c) are formed.
[0140] In the second header collecting pipe (470), a communication
member (475) is provided. The communication member (475) includes a
single distributor (476), a single main pipe (477), and three thin
pipes (478a-478c). The main pipe (477) is, at one end thereof,
connected to a lower end part of the distributor (476), and is, at
the other end thereof, connected to the first communication space
(471a) of the second header collecting pipe (470). The thin pipe
(478a-478c) is, at one end thereof, connected to an upper end part
of the distributor (476). In the distributor (476), the main pipe
(477) and the thin pipes (478a-478c) communicate with each other.
The thin pipe (478a-478c) communicates, at the other end thereof,
with a corresponding one of the second to fourth communication
spaces (471b-471d) of the second header collecting pipe (470).
[0141] Referring to FIG. 20, the thin pipe (478a-478c) opens at
part of a corresponding one of the second to fourth communication
spaces (471b-471d) close to a lower end thereof. That is, the thin
pipe (478a) opens at part of the second communication space (471b)
close to the lower end thereof, the thin pipe (478b) opens at part
of the third communication space (471c) close to the lower end
thereof, and the thin pipe (478c) opens at part of the fourth
communication space (471d) close to the lower end thereof. Note
that the length of the thin pipe (478a-478c) is independently set
such that the difference in flow rate of refrigerant flowing into
the main heat exchange parts (451a-451c) is reduced as much as
possible. As described above, the communication member (475) of the
second header collecting pipe (470) is connected so as to branch
from the communication space (471a) into the second to fourth
communication spaces (471b-471d) corresponding respectively to the
main heat exchange parts (451a-451c). That is, in the second header
collecting pipe (470), the communication space (471a) corresponding
to the lower heat exchange region (452) and the communication space
(471b-471d) corresponding to the upper heat exchange region (451)
communicate with each other.
[0142] Referring to FIG. 19, in the outdoor heat exchanger (40), a
liquid connection member (486) and a gas connection member (485)
are provided. The liquid connection member (486) and the gas
connection member (485) are attached to the first header collecting
pipe (460). The liquid connection member (486) is formed of a
single pipe having a relatively-large diameter. A pipe connecting
between the outdoor heat exchanger (40) and an expansion valve (33)
is connected to one end of the liquid connection member (486). The
liquid connection member (486) opens, at the other end thereof; at
part of the lower space (462) (communication space (462a)) close to
a lower end thereof in the first header collecting pipe (460). The
gas connection member (485) is formed of a single pipe having a
relatively-large diameter. A pipe connecting between the outdoor
heat exchanger (40) and a third port of a four-way valve (34) is
connected to one end of the gas connection member (485). The gas
connection member (485) opens, at the other end thereof, at part of
the upper space (461) close to an upper end thereof in the first
header collecting pipe (460).
[0143] According to the foregoing configuration, in the outdoor
heat exchanger (40) of the present embodiment, refrigerant flows in
a direction indicated by arrows illustrated in FIG. 19 in an
air-cooling operation. In an air-heating operation, refrigerant
flows in a direction opposite to the direction indicated by the
arrows illustrated in FIG. 19.
Fifth Embodiment of the Invention
[0144] A fifth embodiment of the present disclosure will be
described. The present embodiment is configured in such a manner
that the configuration of the second header collecting pipe (470)
of the outdoor heat exchanger (40) of the third embodiment is
changed. The other configuration is similar to that of the third
embodiment. In the present embodiment, only a configuration of a
second header collecting pipe (470) of an outdoor heat exchanger
(40) will be described with reference to FIGS. 21 and 22.
[0145] FIG. 21 is a front view illustrating the schematic
configuration of the outdoor heat exchanger (40) of the fifth
embodiment. Moreover, FIG. 22 is a partial cross-sectional view
illustrating a front side of the outdoor heat exchanger (40) of the
fifth embodiment. Referring to FIG. 22, an internal space of the
second header collecting pipe (470) of the outdoor heat exchanger
(40) is vertically divided into three communication spaces
(471a-471c) by two partition plates (439). Specifically, in the
internal space of the second header collecting pipe (470), the
first communication space (471a), the second communication space
(471b), and the third communication space (471c) are formed in this
order from the right as viewed in FIG. 22. The first communication
space (471a) communicates with flat tubes (53) of a third main heat
exchange part (451c) and flat tubes (58) of a first auxiliary heat
exchange part (452a). The second communication space (471b)
communicates with flat tubes (53) of a second main heat exchange
part (451b) and flat tubes (58) of a second auxiliary heat exchange
part (452b). The third communication space (471c) communicates with
flat tubes (53) of a first main heat exchange part (451a) and flat
tubes (58) of a third auxiliary heat exchange part (452c). In the
outdoor heat exchanger (40), the third main heat exchange part
(451c) and the first auxiliary heat exchange part (452a) are paired
together, the second main heat exchange part (451b) and the second
auxiliary heat exchange part (452b) are paired together, and the
first main heat exchange part (451a) and the third auxiliary heat
exchange part (452c) are paired together.
[0146] That is, in the second header collecting pipe (470) of the
outdoor heat exchanger (40) of the present embodiment, the main
heat exchange part (451a-451c) in an upper heat exchange region
(451) is paired with a corresponding one of the auxiliary heat
exchange parts (452a-452c) in a lower heat exchange region (452).
The communication space (471a-471c) for a corresponding one of the
pairs of heat exchange parts (451a-451c, 452a-452c) is formed such
that the number (e.g., three) of communication spaces (471a-471c)
is the same as the number of pairs. As described above, in the
second header collecting pipe (470), the flat tubes (53, 58) of the
pair of main heat exchange part (451a-451c) and auxiliary heat
exchange part (452a-452c) directly communicate with each other in
the internal space of the second header collecting pipe (470).
[0147] In the present embodiment, the width of the flat tube (58)
provided in the auxiliary heat exchange part (452a-452c) is, as in
the first embodiment, greater than that of the flat tube (53)
provided in the main heat exchange part (451a-451c). Moreover, the
number of flow paths per flat tube (58) provided in the auxiliary
heat exchange part (452a-452c) is greater than the number of flow
paths per flat tube (53) provided in the main heat exchange part
(451a-451c).
[0148] According to the foregoing configuration, in the outdoor
heat exchanger (40) of the present embodiment, refrigerant flows in
a direction indicated by arrows illustrated in FIG. 21 in an
air-cooling operation. In an air-heating operation, refrigerant
flows in a direction opposite to the direction indicated by the
arrows illustrated in FIG. 21.
Sixth Embodiment of the Invention
[0149] A sixth embodiment of the present disclosure will be
described. The present embodiment is configured in such a manner
that the configuration of the outdoor heat exchanger (40) of the
third embodiment is changed. Differences in the outdoor heat
exchanger (40) between the present embodiment and the third
embodiment will be described with reference to FIGS. 23 and 24.
[0150] An internal space of a second header collecting pipe (470)
of the present embodiment is, as in the third embodiment,
horizontally divided into five communication spaces (471a-471e). In
the second header collecting pipe (470) of the present embodiment,
the first communication space (471a) and the fifth communication
space (471e) are paired together, and the second communication
space (471b) and the fourth communication space (471d) are paired
together. Moreover, in the second header collecting pipe (470), a
first communication pipe (472) connecting between the second
communication space (471b) and the fourth communication space
(471d) and a second communication pipe (473) connecting between the
first communication space (471a) and the fifth communication space
(471e) are provided. That is, in the outdoor heat exchanger (40) of
the present embodiment, a first main heat exchange part (451a) and
a third auxiliary heat exchange part (452c) are paired together, a
second main heat exchange part (451b) and a second auxiliary heat
exchange part (452b) are paired together, and a third main heat
exchange part (451c) and a first auxiliary heat exchange part
(452a) are paired together.
[0151] In the outdoor heat exchanger (40) of the present
embodiment, a connection position of a gas connection member (485)
in a first header collecting pipe (460) is changed. Specifically,
the gas connection member (485) opens at a middle part of an upper
space (461) (i.e., at the middle of the upper space (461) in the
vertical direction) in the first header collecting pipe (460).
Further, referring to FIG. 24, in the outdoor heat exchanger (40)
of the present embodiment, the inner diameter B1 of the first
header collecting pipe (460) is greater than the inner diameter B2
of the second header collecting pipe (470). Such a configuration
allows gas refrigerant flowing into the upper space (461) of the
first header collecting pipe (460) through the gas connection
member (485) to be equally distributed into the three main heat
exchange parts (451a-451c).
[0152] In the outdoor heat exchanger (40) of the present
embodiment, the inner diameters of the header collecting pipes
(460, 470) may be equal to each other, and the gas connection
member (485) may open at part of the upper space (461) close to an
upper end thereof in the first header collecting pipe (460).
Seventh Embodiment of the Invention
[0153] FIG. 25 is a partial cross-sectional view of an outdoor heat
exchanger (40) of a seventh embodiment. In the present embodiment,
the width of a flat tube (53) of a main heat exchange part (50) and
the width of a flat tube (58) of an auxiliary heat exchange part
(55) are equal to each other. Moreover, as in the foregoing
embodiments, the number of flat tubes (58) of the auxiliary heat
exchange part (55) is less than the number of flat tubes (53) of
the main heat exchange part (50). Further, the total
cross-sectional area of refrigerant flow paths (49) per flat tube
(58) provided in the auxiliary heat exchange part (55) is greater
than the total cross-sectional area of refrigerant flow paths (49)
per flat tube (53) provided in the main heat exchange part (50).
Although not shown in FIG. 25, the foregoing bare pipe (smooth
inner pipe as illustrated in FIG. 7B) is, in the present
embodiment, employed as the flat tube (53) of the main heat
exchange part (50), and each of the refrigerant flow paths (49) has
a circular cross section. On the other hand, in the flat tube (58)
of the auxiliary heat exchange part (55), a plurality of grooves
are formed in each of the refrigerant flow paths (49) (see FIG.
7A). In such a configuration, the flow velocity of refrigerant in
the auxiliary heat exchange part (55) can be lowered. Thus, in the
present embodiment, a pressure loss in the auxiliary heat exchange
part (55) can be also reduced.
Eighth Embodiment of the Invention
[0154] In an outdoor heat exchanger (40) of an eighth embodiment,
the width of a flat tube (53) of a main heat exchange part (50) and
the width of a flat tube (58) of an auxiliary heat exchange part
(55) are equal to each other. Moreover, the number of flat tubes
(58) of the auxiliary heat exchange part (55) is less than the
number of flat tubes (53) of the main heat exchange part (50).
[0155] Further, the total cross-sectional area of refrigerant flow
paths (49) per flat tube (58) provided in the auxiliary heat
exchange part (55) is greater than the total cross-sectional area
of refrigerant flow paths (49) per flat tube (53) provided in the
main heat exchange part (50). Specifically, the number of
refrigerant flow paths (49) in the flat tube (53) of the main heat
exchange part (50) is less than the number of refrigerant flow
paths (49) in the flat tube (58) of the auxiliary heat exchange
part (55). In such a configuration, the flow velocity of
refrigerant in the auxiliary heat exchange part (55) can be
lowered. Thus, in the present embodiment, a pressure loss in the
auxiliary heat exchange part (55) can be also reduced. Note that
each of the refrigerant flow paths (49) of the heat transfer pipe
(53, 58) in the main heat exchange part (50) or the auxiliary heat
exchange part (55) may be provided with or without grooves (see
FIGS. 7A and 7B).
[0156] Note that, in each of the outdoor heat exchangers (40) of
the second to eighth embodiments, various fins such as the fins
(54, 59, 235, 236) described in the first embodiment and the
variations thereof may be employed.
INDUSTRIAL APPLICABILITY
[0157] The present disclosure is useful as the heat exchanger
including the flat tubes and the fins and configured to exchange
heat between fluid flowing through the flat tube and air and as the
air conditioner.
DESCRIPTION OF REFERENCE CHARACTERS
[0158] 10 Air Conditioner [0159] 40 Outdoor Heat Exchanger (Heat
Exchanger) [0160] 49 Refrigerant Flow Path (Flow Path) [0161] 50
Main Heat Exchange Part [0162] 51, 56 First Header Collecting Pipe
[0163] 52, 57 Second Header Collecting Pipe [0164] 53 Flat tube
[0165] 54, 59 Fin [0166] 55 Auxiliary Heat Exchange Part [0167] 58
Flat tube
* * * * *