[0001] This application relates to an indoor heat exchanger, an indoor machine, an outdoor
heat exchanger, an outdoor machine, and an air conditioner.
[0002] Currently, Hydro Fluoro Carbon (HFC) refrigerant (for example, R410A) are typically
used in the refrigerating cycle apparatuses of air conditioners. Unlike the conventional
Hydro Chloro Fluoro Carbon (HCFC) refrigerant such as R22, R410A does not damage the
ozone layer with zero Ozone Depletion Potential (ODP), provided, however, has high
Global Warming Potential (GWP). Thus, as part of an effort to prevent global warming,
the possibilities of shifting from HFC refrigerant with high GWP, such as R410A, to
HFC refrigerant with low GWP have been under examination. The candidates of the HFC
refrigerant with low GWP include R32 (CH
2F
2; difluoromethane).
[0003] However, when above R32 is used as refrigerant of air conditioners, compared with
the cases where R22, R410A, or R407C is used, the temperature of the refrigerant that
flows in the condenser (that is, the indoor heat exchanger during heating operation,
or the outdoor heat exchanger during cooling operation) becomes higher. Accordingly,
the surface temperature of the refrigerant inlet piping connected to the condenser
becomes high. In particular, when R32 is used as refrigerant of an air conditioner,
the surface temperature of the refrigerant inlet piping becomes higher by 20°C than
the surface temperature of the refrigerant inlet piping when R22, R410A, or R407C
is used as refrigerant (for example, refer to Unexamined Japanese Patent Application
Kokai Publication No.
2001-174075).
[0004] Indoor heat exchangers are attached with seal materials made of resin in order to
seal gaps other than the gaps between the fins so that air flows through only between
the fins (for example, refer to Unexamined Japanese Patent Application Kokai Publications
Nos.
H9-26153 and
H9-210388). Further, some outdoor heat exchangers are attached with a cushioning member made
of foamed styrol in order to prevent damages in case of falling when transporting
the products. Moreover, some outdoor heat exchangers are attached with band members
made of resin in order to fix a plurality of fin units to one another (for example,
refer to Unexamined Japanese Patent Application Kokai Publication No.
2012-163290).
[0005] When above R32 is used as refrigerant of air conditioners, if the refrigerant inlet
piping is connected in the vicinity of the above seal materials, cushioning member,
and band members, the heat of the refrigerant inlet piping is transferred to the members,
subjecting the members to be heated. As the members are heated, deterioration of the
sealing property of the seal materials, and degradation of the cushioning member and
band members are caused.
[0006] To prevent the surface temperature of the refrigerant inlet piping from rising due
to the use of R32 refrigerant, there can be considered to decrease the amount of the
refrigerant circulating the refrigerating cycle to an amount smaller than the standard
amount of refrigerant. Further, there can be considered to increase the flow amount
from the expansion valve, that is, to increase Cv value of the expansion valve (a
numerical value expressing the flow amount of water of 15.6°C flowing the valve at
certain differential pressure), by widening the opening of the expansion valve. However,
in either of the cases, the cooling and heating capabilities and operating efficiency
of air conditioners are possibly lowered.
[0007] In addition, there is no need to decrease the amount of the refrigerant circulating
the refrigerating cycle and to increase the Cv value of the expansion valve, if material
with high heat resistance is used for the seal materials, cushioning member, and band
members that are attached in the heat exchanger. However, since such a material with
high heat resistance is often relatively high-priced, the production costs of the
air conditioners are prone to be higher.
[0008] The present disclosure has been conceived to solve the above problem. The object
of the present disclosure is to suppress the lowering of the cooling and heating capabilities
and operating efficiency of air conditioners while keeping the production costs low.
[0009] In order to achieve the above object, an indoor heat exchanger (21) is characterized
by comprising: a first fin unit (41) that comprises a plurality of fins arranged side
by side; a first seal material (S1) that is arranged at one end of the first fin unit
(41) so as to prevent air from flowing out from the one end side; and a plurality
of heat transfer tubes (T) that are arranged to penetrate through the fins of the
first fin unit (41), wherein the heat transfer tubes (T) are characterized by comprising:
an inlet heat transfer tube (T1) that is connected to inlet piping (12) of refrigerant
that circulates through a refrigerating cycle when the refrigerating cycle is a heating
operation cycle, and a plurality of relay heat transfer tubes (T2), at least one of
which is arranged nearer the first seal material (S1) than the inlet heat transfer
tube (T1) is, and, through which the refrigerant that is flowed out from the inlet
heat transfer tube (T1) flows one after another.
[0010] According to the present disclosure, the inlet piping of the refrigerant is connected
to the inlet heat transfer tube that is located farther from the first seal material
than the relay heat transfer tubes are. As the relay heat transfer tubes are not directly
connected to the inlet piping, the surface temperature of the relay heat transfer
tubes become lower than the surface temperature of the inlet heat transfer tube. As
such, the high heat of the inlet piping cannot be transferred as easily to the first
seal material, suppressing lowering of the sealing property of the first seal material.
Moreover, there is no need to use seal materials made of high-priced, high heat resistance
material. As the result, lowering of the cooling and heating capabilities and operating
efficiency of the air conditioners can be suppressed, while keeping the production
costs low.
[0011] A more complete understanding of this application can be obtained when the following
detailed description is considered in conjunction with the following drawings, in
which:
FIG. 1 is a constitution diagram of the air conditioner according to an embodiment
of the present disclosure;
FIG. 2 is a section view of the indoor machine;
FIG. 3 is a perspective view schematically showing the indoor heat exchanger;
FIG. 4 is a perspective view of the indoor heat exchanger and the indoor machine chassis;
FIG. 5 is a section view of the indoor heat exchanger;
FIG. 6 is a perspective view of the indoor heat exchanger (part 1);
FIG. 7 is a perspective view of the indoor heat exchanger (part 2);
FIG. 8 is a section view of the outdoor machine;
FIG. 9 is a perspective view schematically showing the outdoor heat exchanger;
FIG. 10 is a perspective view of the outdoor heat exchanger and the outdoor machine
chassis;
FIG. 11 is a front view of the outdoor heat exchanger viewed from the arrow B of FIG.
10;
FIG. 12 is a perspective view of the outdoor heat exchanger (part 1);
FIG. 13 is a side view of the outdoor heat exchanger viewed from the arrow C of FIG.
10;
FIG. 14 is a perspective view of the outdoor heat exchanger (part 2); and
FIG. 15 is a graph showing a relationship between the number of the heat transfer
tubes through which R32 refrigerant that flowed in the condenser (the indoor heat
exchanger during heating operation, or the outdoor heat exchanger during cooling operation)
flows and the surface temperature of the heat transfer tubes.
[0012] The following will describe the air conditioner 10 according to the present embodiment
with reference to FIGS. 1 to 15.
[0013] As shown in FIG. 1, the air conditioner 10 according to the embodiment of the present
disclosure conditions the air of room R as the object of air conditioning by circulating
the refrigerant in the refrigerating cycle 100. The air conditioner 10 is a separate
type that has an indoor machine 20 and an outdoor machine 30. In addition to the indoor
machine 20 and the outdoor machine 30, the air conditioner 10 has gas communication
piping 11a and liquid communication piping 11b that connect the indoor machine 20
and the outdoor machine 30. The air conditioner 10 uses refrigerant that consists
only of R32 HFC refrigerant (CH
2F
2; difluoromethane). R32 is refrigerant that has smaller Global Warming Potential (GWP)
than R410A HFC refrigerant that is currently more widely used in air conditioners,
and, thus, has relatively smaller influence to global warming. However, without limiting
to R32 refrigerant, R32-rich refrigerant with an R32 content of over 50% may also
be used.
[0014] The indoor machine 20 is installed in the room R as the object of air conditioning,
and has an indoor heat exchanger 21 and an indoor blower 22.
[0015] The indoor heat exchanger 21 cools or heats the air of the room R as the object of
air conditioning by causing heat exchange between the refrigerant and the air of the
room R. For example, in the cooling operation, the indoor heat exchanger 21 functions
as an evaporator and evaporates the supplied refrigerant. As such, the indoor heat
exchanger 21 absorbs heat from the air around the indoor heat exchanger 21, thereby
cooling the air of the room R. Whereas, in the heating operation, the indoor heat
exchanger 21 functions as a condenser and condenses the flowing-in vapor refrigerant.
As such, the indoor heat exchanger 21 releases heat to the air around the indoor heat
exchanger 21, thereby heating the air of the room R.
[0016] The indoor blower 22 is installed in the vicinity of the indoor heat exchanger 21.
The indoor blower 22 generates air flow that passes through the indoor heat exchanger
21. Then, the indoor blower 22 supplies the air that was heat-exchanged by the generated
air flow to the room R as the object of air conditioning.
[0017] The outdoor machine 30 is installed outdoor, and has a compressor 31, a four-way
selector 32, an outdoor heat exchanger 33, an expansion valve 34, and an outdoor blower
35.
[0018] The compressor 31 is a device that compresses the supplied refrigerant. The compressor
31 converts the supplied refrigerant to high temperature and high pressure vapor refrigerant
by compressing the refrigerant. Then, the compressor 31 sends out the high temperature
and high pressure refrigerant to the four-way selector 32.
[0019] The four-way selector 32 is provided at the downstream side of the compressor 31.
The four-way selector 32 switches the circulation direction of the refrigerant in
the refrigerating cycle 100. The four-way selector 32 switches the refrigerating cycle
either to a heating operation cycle or a cooling operation cycle. The four-way selector
32 is controlled by the controller.
[0020] The outdoor heat exchanger 33 exchanges heat with air by evaporating or condensing
the supplied refrigerant to cool or heat the air. For example, in the cooling operation,
the outdoor heat exchanger 33 functions as a condenser and condenses the supplied
refrigerant. Whereas, in the heating operation, the outdoor heat exchanger 33 functions
as an evaporator and evaporates the supplied refrigerant.
[0021] The expansion valve 34 is a decompression device of which opening degree is changeable.
The expansion valve 34 is configured by, for example, an electronically controlled
expansion valve. The expansion valve 34 inflates the supplied refrigerant to decompress
the high pressure refrigerant to low pressure. Then, the expansion valve 34 sends
out the generated low pressure refrigerant.
[0022] The outdoor blower 35 is installed in the vicinity of the outdoor heat exchanger
33. The outdoor blower 35 generates an air flow that passes through the indoor heat
exchanger 21. Then, the outdoor blower 35 exhausts the air that is heat-exchanged
by the generated air flow to outdoor.
[0023] The refrigerating cycle 100 is configured by an indoor heat exchanger 21, a compressor
31, a four-way selector 32, an outdoor heat exchanger 33, an expansion valve 34, gas
communication piping 11a, liquid communication piping 11b, and the like.
[0024] FIG. 2 is a section view of the indoor machine 20. As shown in FIG. 2, the indoor
machine 20 further has an indoor machine chassis 23 that houses the indoor heat exchanger
21 and the indoor blower 22.
[0025] The indoor machine chassis 23 is equipped with air inlets 24, 25 for sucking the
air of the room R as the object of air conditioning, and an air outlet 26 for supplying
cold air or warm air to the room R. The air inlet 24 is formed on the upper surface
of the indoor machine chassis 23 (+Z side surface). The air inlet 25 and the air outlet
26 are formed at the lower side of the front panel 23a of the indoor machine chassis
23. Further, the air outlet 26 comprises a plurality of horizontal vanes 27 and a
plurality of vertical flaps 28. The horizontal vanes 27 regulate the horizontal direction
of air flowing out from the indoor blower 22. The vertical flap 28 regulates the vertical
direction of air flowing out from the indoor blower 22.
[0026] Further, the indoor machine chassis 23 is equipped with condensate receivers 29A,
29B. The condensate receivers 29A, 29B are receptacles that receive droplets that
are condensed by heat exchange of the indoor heat exchanger 21 in the cooling operation
and the like. The condensate receiver 29A and the condensate receiver 29B are connected
by a water channel, which is not shown, and the condensate water that the condensate
receiver 29B received flows into the condensate receiver 29A. Then, the condensate
water collected in the condensate receiver 29A is drained outside of the room R via
drain piping and the like.
[0027] The indoor blower 22 has a blower fan 22a and a fan motor that rotates the blower
fan 22a. In the present embodiment, the blower fan 22a of the indoor blower 22 is
configured by the cross flow fan. When the blower fan 22a of the indoor blower 22
rotates, air flow A that passes through the indoor heat exchanger 21 is generated.
Then, by the generated air flow A, the air from the indoor blower 22 passes through
an air channel 23b formed at the lower side of the indoor blower 22 (-Z side), and
is guided by the horizontal vane 27 and the vertical flap 28 to be blown out from
the air outlet 26. It should be noted that, in the present embodiment, the blower
fan 22a of the indoor blower 22 is configured by a cross flow fan, without limitation.
The type of the blower fan 22a depends on the form of the indoor machine 20. For example,
a turbo fan may be used according to the form of the indoor machine 20.
[0028] The indoor heat exchanger 21 is configured by fins and tube type heat exchangers,
and arranged to cover the indoor blower 22. The indoor heat exchanger 21 has a front-side
fin unit 41 characterized by comprising a plurality of fins, a back-side fin unit
42 characterized by comprising a plurality of fins, a plurality of heat transfer tubes
T through which the refrigerant flows, and seal materials S1 to S3. Further, as shown
in FIG. 3, the indoor heat exchanger 21 has hairpins 50 and U-shaped piping 51 that
connect the heat transfer tubes T.
[0029] FIG. 4 is a perspective view of the indoor heat exchanger and the indoor machine
chassis. It should be noted that the U-shaped piping 51 is omitted in FIG. 4. The
front-side fin unit 41 is arranged, as shown in FIGS. 2 and 4, on the front side of
the indoor blower 22 (-X side). The front-side fin unit 41 is configured by a plurality
of fins that are arranged in parallel to the X-Z plane at even intervals. The fins
are made of metal and formed in thin plate shapes. The gaps between the fins serve
as flow channels that the air sucked by the indoor blower 22 passes though. Further,
the front-side fin unit 41 has a plurality of through holes 45 that penetrate in the
Y axis direction.
[0030] The back-side fin unit 42 is arranged to cover the upper side (+Z side) and the back-side
(+X side) of the indoor blower 22. The back-side fin unit 42 is obliquely arranged
so that the upper side end (+Z side end) of the back-side fin unit 42 comes in the
close proximity to the upper side end (+Z side end) of the front-side fin unit 41.
In the same way as the front-side fin unit 41, the back-side fin unit 42 is configured
by a plurality of fins of thin metal plates that are arranged in parallel to the X-Z
plane at even intervals. The gaps between the fins serve as flow channels through
which the air sucked by the indoor blower 22 passes though. The back-side fin unit
42 has a plurality of through holes 45 that penetrate in the Y axis direction.
[0031] The heat transfer tubes T are pipes of which longitude direction is the Y axis direction.
The heat transfer tubes T are made of metal. The heat transfer tubes T are, as shown
in FIG. 2, inserted and fixed in the through holes 45 of the front-side fin unit 41
and the back-side fin unit 42. The heat transfer tubes T inserted in the through holes
45 are fixed in contact with the fins. The heat transfer tubes T are all formed in
the same shapes and dimensions. The total length of the heat transfer tubes T (length
in the Y axis direction) is, for example, 700 mm.
[0032] The heat transfer tubes T are arranged, as shown in FIG. 5, in two rows: a row that
is upwind with respect to the air flow A; and a row that is downwind with respect
thereto. The row pitch L1 that is an interval between the upwind row and the downwind
row is, for example, 12.7 mm. Further, the heat transfer tubes T are arranged at even
intervals (in particular, at stage pitch L2) from the upper side (+Z side) ends of
the front-side fin unit 41 and back-side fin unit 42 to the lower side (-Z side) ends
thereof. The stage pitch L2 is, for example, 20.4 mm.
[0033] The indoor heat exchanger 21 has paths P1, P2 through which the refrigerant flows.
It should be noted that the number of paths P1, P2 formed in the indoor heat exchanger
21 is arbitrary. In the present embodiment, an indoor heat exchanger 21 with two paths
P1, P2 is exemplified. The heat transfer tubes T at the ends of the paths P1, P2 are
referred to as the inlet heat transfer tubes T1 and outlet heat transfer tubes T3.
Further, a plurality of heat transfer tubes T that connect the inlet heat transfer
tubes T1 and the outlet heat transfer tubes T3 are referred to as the relay heat transfer
tubes T2. When the refrigerating cycle is the heating operation cycle, the refrigerant
flows in from the inlet heat transfer tubes T1, passes through the relay heat transfer
tubes T2, and flows out from the outlet heat transfer tubes T3. It should be noted
that when the refrigerating cycle is the cooling operation cycle, the flow of the
refrigerant circulating through the refrigerating cycle becomes reverse; the refrigerant
flows in from the outlet heat transfer tubes T3, passes through the relay heat transfer
tube T2, and flows out from the inlet heat transfer tubes T1.
[0034] As shown in FIGS. 5 and 6, the hairpins 50 are connected to the -Y side ends of the
heat transfer tubes T (the inlet heat transfer tubes T1, relay heat transfer tubes
T2, and outlet heat transfer tubes T3). The hairpins 50 are made of metal. The hairpins
50 are formed in a general U shape. The hairpins 50 are coupled in a manner in which
the hairpins 50 are exposed from the -Y side end plane of the front-side fin unit
41 and the back-side fin unit 42. The hairpins 50 are formed integrally to, for example,
two of the heat transfer tubes T.
[0035] As shown in FIGS. 5 and 7, the U-shaped piping 51 is connected to the +Y side ends
of the relay heat transfer tubes T2. The U-shaped piping 51 is made of metal. The
U-shaped piping 51 is coupled to the relay heat transfer tubes T2, for example, by
brazing.
[0036] The inlet piping 12 in which the refrigerant flows when the refrigerating cycle is
the heating operation cycle, is connected to the +Y side ends of the inlet heat transfer
tubes T1. Also, the outlet piping 13 in which the refrigerant flows when the refrigerating
cycle is the heating operation cycle, is connected to the outlet heat transfer tubes
T3.
[0037] The seal material S1, as shown in FIG. 5, is a member that seals a gap between the
front-side fin unit 41 and the back-side fin unit 42. The seal material S1 is attached
at the upper side (+Z side) ends of the front-side fin unit 41 and the back-side fin
unit 42 along the Y axis direction. As such, the air flow A is prevented from passing
though the gap between the front-side fin unit 41 and the back-side fin unit 42 without
passing through between the fins of the front-side fin unit 41 and the back-side fin
unit 42. The material of the seal material S 1 is, for example, resin or rubber. Preferably,
the material of the seal material S 1 is Ethylene Propylene Diene (EPDM) rubber foam
with one side being an adhesive face. The heat resistant temperature of the EPDM rubber
used for the seal material S 1 according to the present embodiment is approximately
100°C.
[0038] A plurality of relay heat transfer tubes T2 are arranged between the seal material
S 1 as configured as above and the inlet heat transfer tube T1 of path P1. In the
present embodiment, five relay heat transfer tubes T2 are arranged between the seal
material S 1 and the inlet heat transfer tube T1 (the five relay heat transfer tubes
T2 are, specifically, the relay heat transfer tubes T2-1, T2-2, T2-3, T2-4, T2a shown
in FIG. 5). As such, the relay heat transfer tubes T2 are arranged closer to the seal
material S1 than the inlet heat transfer tube T1 is. Further, for convenience of explanation,
the two relay heat transfer tubes T2 arranged nearest the seal material S 1 are defined
as the relay heat transfer tubes T2a. The relay heat transfer tubes T2a are respectively
arranged in the vicinity of the uppermost end (+Z side end) of the front-side fin
unit 41 and in the vicinity of the uppermost end (+Z side end) of the back-side fin
unit 42.
[0039] The seal material S2 is a member that seals the gap between the front-side fin unit
41 and the condensate receiver 29A of the indoor machine chassis 23. The seal material
S2 is attached along the Y axis direction at the lower side (-Z side) end of the front-side
fin unit 41. As such, the air flow A is prevented from passing through the lower side
of the front-side fin unit 41 without passing through between the fins of the front-side
fin unit 41. The material of the seal material S2 is, for example, resin or rubber.
In the same way as the material of the seal material S1, the material of the seal
material S2 is preferably Ethylene Propylene Diene (EPDM) rubber foam with one side
being an adhesive face. The heat resistant temperature of the EPDM rubber used for
the seal material S2 according to the present embodiment is approximately 100°C.
[0040] A plurality of relay heat transfer tubes T2 are arranged between the seal material
S2 as configured as above and the inlet heat transfer tubes T1. In the present embodiment,
three relay heat transfer tubes T2 are arranged between the seal material S2 and the
inlet heat transfer tube T1 (the three relay heat transfer tubes T2 are, specifically,
the relay heat transfer tubes T2-5, T2-6, T2b shown in FIG. 5). As such, the relay
heat transfer tubes T2 are arranged closer to the seal material S2 than the inlet
heat transfer tube T1 is. Hereinafter, for convenience of explanation, the two relay
heat transfer tubes T2 arranged near the seal material S2 are defined as the relay
heat transfer tubes T2b. The two relay heat transfer tubes T2b are arranged in the
vicinity of the lowermost end (-Z side end) of the front-side fin unit 41.
[0041] The seal material S3 is a member that seals the gap between the back-side fin unit
42 and the condensate receiver 29B of the indoor machine chassis 23. The seal material
S3 is attached along the Y axis direction at the lower side (-Z side) end of the back-side
fin unit 42. As such, the air flow A is prevented from passing through the lower side
of the back-side fin unit 42 without passing through between the fins of the back-side
fin unit 42. The material of the seal material S3 is, for example, resin or rubber.
In the same way as the material of the seal materials S 1 and S2, the material of
the seal material S3 is preferably Ethylene Propylene Diene (EPDM) rubber foam with
one side being an adhesive face. The heat resistant temperature of the EPDM rubber
used for the seal material S3 according to the present embodiment is approximately
100°C.
[0042] A relay heat transfer tube T2 is arranged closer to the seal material S3 as configured
as above than the inlet heat transfer tube T1 is. Hereinafter, for convenience of
explanation, the relay heat transfer tube T2 arranged in the vicinity of the seal
material S3 is defined as the relay heat transfer tube T2c. The relay heat transfer
tube T2c is arranged in the vicinity of the lowermost end (-Z side end) of the back-side
fin unit 42.
[0043] It should be noted that, the EPDM rubber foam used for the material of the seal materials
S 1-S3 in the present embodiment is the one used for general indoor machines 20, which
is relatively low cost material.
[0044] If the above described gaps exist without having the seal materials S 1-S3, in the
cooling operation, the air that has been heat-exchanged through the indoor heat exchanger
21 and has low temperature and low moisture and the air that passed through the gaps
and has not been heat-exchanged are mixed in the air channel 23b and the like of the
indoor machine 20 as shown in FIG. 2. Then, the moisture content in the air that has
not been heat-exchanged is cooled below the dew point, condensed, and adheres as dews
to the components inside the air channel 23b (for example, the indoor blower 22).
The dews are discharged from the air outlet 26 and may possibly damage furniture and
electrical appliances around the indoor machine 20. To prevent this, the seal materials
S1-S3 are essential members.
[0045] FIG. 8 is a section view of the outdoor machine 30. The outdoor machine 30 has, as
shown in FIG. 8, a compressor 31, an outdoor heat exchanger 33, and an outdoor blower
35, as well as an outdoor machine chassis 36 that houses the compressor 31, the outdoor
heat exchanger 33, and the outdoor blower 35.
[0046] The outdoor machine chassis 36 is formed in a general rectangular parallelopiped.
The outdoor machine chassis 36 has a partitioning plate 37 that partitions the interior
into two spaces. The partitioning plate 37 is formed in a manner in which the partitioning
plate 37 extends and protrudes from the bottom surface of the outdoor machine chassis
36 in the vertical direction (+Z direction). This partitioning plate 37 partitions
the interior of the outdoor machine chassis 36 into a machine room M that houses the
compressor 31 and the like and a blower room F that houses the outdoor blower 35 and
the like. The machine room M is formed on the +Y side of the inner space in the outdoor
machine chassis 36, whereas the blower room F is formed on the -Y side of the inner
space in the outdoor machine chassis 36. The partitioning plate 37 is equipped for
preventing rainwater due to wind, rain, and the like from infiltrating the machine
room M through the blower room F.
[0047] The outdoor blower 35 is installed in the vicinity of the outdoor heat exchanger
33, and has a blower fan 35a and a fan motor 35b that rotates the blower fan 35a.
The outdoor blower 35 generates an air flow that passes through the outdoor heat exchanger
33 by rotation of the blower fan 35a. Then, the outdoor blower 35 discharges the air
that was heat-exchanged by the generated air flow to outdoor. In the present embodiment,
the blower fan 35a is configured by a propeller fan that sucks air from the back side
or lateral sides. Further, the outdoor blower 35 has one or two blower fans 35a.
[0048] In the same way as the indoor heat exchanger 21, the outdoor heat exchanger 33 is
configured by a fin and tube heat exchanger. The outdoor heat exchanger 33 is arranged
to cover the lateral side (-Y side) and the back side (+X side) of the outdoor blower
35. The outdoor heat exchanger 33 has a front-side fin unit 43 characterized by comprising
a plurality of fins, a back-side fin unit 44 characterized by comprising a plurality
of fins, a cushioning member 60, and band members 71, 72. Further, as shown in FIG.
9, the outdoor heat exchanger 33 has a plurality of heat transfer tubes T, hairpins
50, and U-shaped piping 51, through which the refrigerant flows.
[0049] FIG. 10 is a perspective view of the outdoor heat exchanger 33 and the outdoor machine
chassis 36. It should be noted that the hairpins 50 and U-shaped piping 51 are omitted
in FIG. 10. As shown in FIG. 10, the front-side fin unit 43 has a plurality of fins.
The fins are made of metal and formed in thin plate shapes. The front-side fin unit
43 is configured by a plurality of fins that are arranged side by side at even intervals.
The front-side fin unit 43 is formed in a general L shape when viewed in X-Y cross
section. Further, the front-side fin unit 43 has a plurality of through holes.
[0050] The back-side fin unit 44 is arranged to abut the front-side fin unit 43. The back-side
fin unit 44 has a plurality of fins. The fins are made of metal formed in thin plate
shapes. The back-side fin unit 44 is configured by arranging the fins at even intervals.
The back-side fin unit 44 is formed in a general L shape when viewed in X-Y cross
section. Further, the back-side fin unit 44 has a plurality of through holes.
[0051] As shown in FIG. 9, the heat transfer tubes T are pipes made of metal. As can be
seen from FIG. 10, the heat transfer tubes T are inserted and fixed in the through
holes of the front-side fin unit 43 and the back-side fin unit 44. The heat transfer
tubes T are formed to have the same inner/outer diameters and the total length to
one another. The total length of the heat transfer tubes T is, for example, 700 mm.
[0052] Further, the heat transfer tubes T are arranged, as shown in FIG. 11, in two rows:
a row that is upwind with respect to the air flow A; and a row that is downwind with
respect thereto. The row pitch L1 that is an interval between the upwind row and the
downwind row is, for example, 12.7 mm. Further, the heat transfer tubes T are arranged
at even intervals (in particular, at stage pitch L2) from the upper side (+Z side)
ends of the front-side fin unit 43 and the back-side fin unit 44 to the lower side
(-Z side) ends thereof along the Z axis direction. The stage pitch L2 is, for example,
20.4 mm.
[0053] The outdoor heat exchanger 33 has paths P3-P6 that are channels through which the
refrigerant flows. It should be noted that the number of paths P3-P6 formed in the
outdoor heat exchanger 33 is arbitrary. In the present embodiment, the outdoor heat
exchanger 33 with four paths P3-P6 is exemplified. Hereinafter, the heat transfer
tubes T at the end of the paths P3-P6 are defined as the inlet heat transfer tubes
T1 and outlet heat transfer tubes T3. Further, a plurality of heat transfer tubes
T that connect the inlet heat transfer tubes T1 and the outlet heat transfer tubes
T3 are defined as the relay heat transfer tubes T2. When the refrigerating cycle is
the cooling operation cycle, the refrigerant flows in from the inlet heat transfer
tubes T1, passes through the relay heat transfer tubes T2, and flows out from the
outlet heat transfer tubes T3. It should be noted that, when the refrigerating cycle
is the heating operation cycle, the flow of the refrigerant circulating through the
refrigerating cycle becomes reverse; the refrigerant flows in from the outlet heat
transfer tubes T3, passes through the relay heat transfer tubes T2, and flows out
from the inlet heat transfer tubes T1.
[0054] As shown in FIGS. 11 and 12, the generally U-shaped hairpins 50 are connected to
the -X side ends of the heat transfer tubes T (the inlet heat transfer tubes T1, relay
heat transfer tubes T2, and outlet heat transfer tubes T3). The hairpins 50 are arranged
in a manner in which the hairpins 50 are exposed from the -X side end plane of the
front-side fin unit 43 and the back-side fin unit 44. The hairpins 50 are formed integrally
to, for example, two of the heat transfer tubes T.
[0055] As shown in FIGS. 13 and 14, the U-shaped piping 51 is connected to the +Y side ends
of the relay heat transfer tubes T2. The U-shaped piping 51 is coupled to the relay
heat transfer tubes T, for example, by brazing.
[0056] The inlet piping 14 that the refrigerant flows in when the refrigerating cycle is
the cooling operation cycle, is connected to the +Y side ends of the inlet heat transfer
tubes T1. Also, the outlet piping 15 that the refrigerant flows in when the refrigerating
cycle is the cooling operation cycle, is connected to the outlet heat transfer tubes
T3.
[0057] The cushioning member 60 is arranged, as shown in FIGS. 8 and 10, between the inner
wall surface of the outdoor machine chassis 36 and the outdoor heat exchanger 33.
As such, the cushioning member 60 prevents the interference of the outdoor heat exchanger
33 to the outdoor machine chassis 36 while transporting the outdoor machine 30, and
prevents damages in case of falling when transporting the products. In the present
embodiment, the cushioning member 60 is arranged in the vicinity of the upper side
of the -X side end plane of the front-side fin unit 43 of the outdoor heat exchanger
33. The material of the cushioning member 60 is, for example, foamed styrol material.
The heat resistant temperature of the foamed styrol material used for the cushioning
member 60 according to the present embodiment is approximately 80°C.
[0058] It should be noted that the foamed styrol material used for the cushioning member
60 in the present embodiment is the one used for general outdoor machines 30, which
has relatively high commercial availability and is low cost.
[0059] As shown in FIG. 11, a plurality of relay heat transfer tubes T2 are arranged between
the cushioning member 60 as configured as described above and the inlet heat transfer
tube T1 of path P3. In the present embodiment, five relay heat transfer tubes T2 are
arranged between the cushioning member 60 and the inlet heat transfer tube T1 (the
five relay heat transfer tubes T2 are, specifically, relay heat transfer tubes T2-7,
T2-8, T2-9, T2-10, T2d shown in FIG. 11). As such, the relay heat transfer tubes T2
of path P3 are arranged closer to the cushioning member 60 than the inlet heat transfer
tube T1 of path P3 is. Hereinafter, for convenience of explanation, the relay heat
transfer tube T2 arranged near the cushioning member 60 is referred to as the relay
heat transfer tube T2d. The relay heat transfer tube T2d is arranged on the lower
side (-Z side) of the cushioning member 60.
[0060] The band member 71 fixes the front-side fin unit 43 and the back-side fin unit 44
to one another as shown in FIGS. 11 and 12. The band member 71 is a string like member
that ties the hairpins 50 of path P5 to one another. The material of the band member
71 is, for example, nylon, and preferably 6,6 nylon. The heat resistant temperature
of 6,6 nylon used for the band members 71 according to the present embodiment is approximately
85°C.
[0061] As shown in FIG. 11, four relay heat transfer tubes T2 are arranged between the band
member 71 as configured as described above and the inlet heat transfer tube T1 of
path P5 (the four relay heat transfer tubes T2 are, specifically, relay heat transfer
tubes T2-11, T2-12, T2f, T2e shown in FIG. 11). As such, the relay heat transfer tubes
T2 of path P5 are arranged closer to the band member 71 than the inlet heat transfer
tube T1 of path P5 is. Hereinafter, for convenience of explanation, the relay heat
transfer tube T2 arranged near the band member 71 is defined to as the relay heat
transfer tube T2e.
[0062] In the same way as the band member 71, the band member 72 is used to fix the front-side
fin unit 43 and the back-side fin unit 44 to one another as shown in FIG. 13. The
band member 72 is a string like member that ties the U-shaped piping 51 of path P5
to one another. The material of the band member 72 is, for example, nylon. Preferably,
the material is 6,6 nylon in the same way as the band member 71. The heat resistant
temperature of 6,6 nylon used for the band member 72 according to the present embodiment
is approximately 85°C.
[0063] Three relay heat transfer tubes T2 are arranged between the band member 72 as configured
as described above and the inlet heat transfer tube T1 of path P5 (the three relay
heat transfer tubes T2 are, specifically, relay heat transfer tubes T2-11, T2-12,
T2f shown in FIG. 13). As such, the relay heat transfer tubes T2 of path P5 are arranged
closer to the band member 72 than the inlet heat transfer tube T1 of path P5 is. It
should be noted that, for convenience of explanation, the relay heat transfer tube
T2 arranged near the band member 72 is defined as the relay heat transfer tube T2f.
[0064] It should be noted that 6,6 nylon used for the band members 71, 72 is the one used
for general outdoor heat exchangers 33, which has relatively high commercial availability
and is low cost.
[0065] The air conditioner 10 as configured as described above conditions the air of the
room R as the object of air conditioning by performing the cooling operation and the
heating operation. The following will describe the refrigerating cycle operation of
the air conditioner 10 using FIG. 1. The solid arrow in FIG. 1 indicates the flow
of the refrigerant in the cooling operation. Further, the dotted arrow in FIG. 1 indicates
the flow of the refrigerant in the heating operation.
[0066] In the cooling operation, the four-way selector 32 can switch so that the refrigerant
from the compressor 31 is sent out to the outdoor heat exchanger 33. Then, the refrigerant
flows as indicated by the solid arrow in FIG. 1. In such a case, the outdoor heat
exchanger 33 functions as a condenser, whereas the indoor heat exchanger 21 functions
as an evaporator.
[0067] When the refrigerant flows in the compressor 31, the supplied refrigerant is first
compressed by the compressor 31. Then, the pressure and specific enthalpy of the refrigerant
increase to be converted to high temperature and high pressure vapor refrigerant,
which is sent out from the compressor 31. The vapor refrigerant sent out from the
compressor 31 passes through the four-way selector 32 and flows in the outdoor heat
exchanger 33. In particular, the refrigerant flows in the paths P3-P6 of the outdoor
heat exchanger 33 through a flow divider tube, as shown in FIGS. 11 and 13.
[0068] In the present embodiment, R32 is used as refrigerant. Thus, the temperature of the
refrigerant becomes higher than the cases, for example, when R22 and the like is used
as refrigerant. As the result, the surface temperature of the inlet piping 14 of the
outdoor heat exchanger 33 becomes higher by approximately 20°C than the temperature
of the inlet piping when R22 is used as refrigerant. In particular, when R32 is used
as refrigerant, the surface temperature of the inlet piping 14 becomes around 110°C.
[0069] FIG. 15 is a graph indicating a relationship between the number of the heat transfer
tubes T through which the R32 refrigerant flowing in the condenser (the indoor heat
exchanger 21 in the heating operation, and the outdoor heat exchanger 33 in the cooling
operation) passes and the surface temperature of the heat transfer tubes T. The number
of the heat transfer tubes T in the horizontal axis of FIG. 15, is a value indicating
the first heat transfer tube T (inlet heat transfer tube T1) that the refrigerant
flowing in the condenser passes through as "1;" the second heat transfer tube T as
"2;" the third heat transfer tube T as "3;" the fourth heat transfer tube T as "4."
It should be noted that the graph shown in FIG. 15 is a case where the heat transfer
tubes T of total length 700 mm is used with the row pitch L1, between the heat transfer
tubes T, of 12.7 mm and the stage pitch L2 of 20.4 mm. As can be seen from FIG. 15,
the temperature of the first heat transfer tube T (inlet heat transfer tube T1) is
around 110°C. Accordingly, the temperature of the second heat transfer tube T (relay
heat transfer tube T2) and later becomes lower. In particular, the temperature of
the second heat transfer tube T (relay heat transfer tube T2) decreases to around
92°C, and the temperature of the third heat transfer tube T (relay heat transfer tube
T2) decreases to as low as around 75°C. Then, the heat transfer tubes T (relay heat
transfer tubes T2) after fourth heat transfer tube T become stable around 70°C. It
should be noted that, as the row pitch L1 and the stage pitch L2 are sufficiently
smaller than the total length of the heat transfer tubes T, the same result as the
graph of FIG. 15 can be obtained even in a case where there is somewhat changes in
the dimensions of the row pitch L1 and the stage pitch L2.
[0070] As shown in FIG. 11, five relay heat transfer tubes T2 are arranged between the cushioning
member 60 and the inlet heat transfer tube T1 of path P3. Thus, the relay heat transfer
tube T2d nearest the cushioning member 60 corresponds to the sixth heat transfer tube
T that the refrigerant flows through. Referring to FIG. 15, the temperature of the
relay heat transfer tube T2d is around 70°C. Further, four relay heat transfer tubes
T2 are arranged between the band member 71 and the inlet heat transfer tube T1 of
path P5. Thus, the relay heat transfer tube T2e nearest the band member 71 corresponds
to the fifth heat transfer tube T that the refrigerant flows through. Therefore, referring
to FIG. 15, it can be seen that the temperature of the relay heat transfer tube T2e
becomes around 70°C.
[0071] As shown in FIG. 13, three relay heat transfer tubes T2 are arranged between the
band member 71 and the inlet heat transfer tube T1 of path P5. Thus, the relay heat
transfer tube T2f near the band member 72 corresponds to the fourth heat transfer
tube T that the refrigerant flows through. Referring to FIG. 15, it can be seen that
the temperature of the relay heat transfer tube T2f becomes around 70°C.
[0072] Returning to FIG. 1, if the vapor refrigerant flows in the outdoor heat exchanger
33, the refrigerant is condensed by heat-exchanging with the outside air (outdoor
air) supplied by the outdoor blower 35. Then, the specific enthalpy of the refrigerant
falls while maintaining certain pressure. As such, the vapor refrigerant is converted
to low temperature and high pressure liquid refrigerant. Then, the liquid refrigerant
is sent out from the outdoor heat exchanger 33.
[0073] When the liquid refrigerant flows in the expansion valve 34, the liquid refrigerant
is inflated by the expansion valve 34. Then, the liquid refrigerant is decompressed
while maintaining certain specific enthalpy to be converted to a low pressure state.
Then, this liquid refrigerant is sent out from the expansion valve 34.
[0074] The liquid refrigerant sent out from the expansion valve 34 passes through the liquid
communication piping 11lb, flows in the refrigerant flow channel of the indoor machine
20, then, flows in the indoor heat exchanger 21. In particular, the refrigerant flows
in the paths P1, P2 of the indoor heat exchanger 21 through the flow divider tube
as shown in FIG. 5.
[0075] Returning to FIG. 1, when the liquid refrigerant flows in the indoor heat exchanger
21, the refrigerant is evaporated by heat-exchanging with the air, supplied by the
indoor blower 22, of the room R as the object of air conditioning. Then, the specific
enthalpy of the refrigerant increases while maintaining certain pressure. As such,
the refrigerant is converted to high temperature and low pressure heated vapor refrigerant.
Also, the above heat exchange cools the air of the room R. As the result, the room
temperature of the room R as the object of air conditioning decreases.
[0076] The heated vapor refrigerant that was sent out from the indoor heat exchanger 21
passes through the gas communication piping 11a, and flows in the refrigerant flow
channel of the outdoor machine 30, then, flows in again the compressor 31 through
the four-way selector 32 of the outdoor machine 30. Thereafter, the refrigerant circulates
repeatedly above-described refrigerating cycle. It should be noted that, the refrigerating
cycle in dehumidification operation is the same as the refrigerating cycle of the
above described cooling operation.
[0077] Next, in the heating operation, the four-way selector 32 can switch so that the refrigerant
from the compressor 31 is sent out to the indoor heat exchanger 21. Then, the refrigerant
flows as indicated by the dotted arrow in FIG. 1. In such a case, the outdoor heat
exchanger 33 functions as an evaporator, whereas the indoor heat exchanger 21 functions
as a condenser.
[0078] The vapor refrigerant sent out from the compressor 31 passes through the four-way
selector 32, and flows out from the outdoor machine 30. Then, the vapor refrigerant
passes through the gas communication piping 11a, and flows in the refrigerant flow
channel of the indoor machine 20. Then, the vapor refrigerant flows in the indoor
heat exchanger 21 via the inlet piping 12. In particular, the refrigerant flows in
the paths P1, P2 of the indoor heat exchanger 21 through the flow divider tube as
shown in FIG. 5.
[0079] As R32 is used as refrigerant in the present embodiment, as can be seen from FIG.
15, the temperature of the inlet heat transfer tube T1 of the indoor heat exchanger
21 becomes around 110°C.
[0080] As shown in FIG. 5, the relay heat transfer tubes T2a arranged near the seal material
S1 correspond to the twelfth and thirteenth heat transfer tubes T that the refrigerant
flows through if the inlet heat transfer tube T1 is counted as the first heat transfer
tube T. Therefore, referring to FIG. 15, it can be seen that the surface temperature
of the relay heat transfer tubes T2a is around 70°C. Further, the relay heat transfer
tubes T2b arranged near the seal material S2 correspond to the fourth and fifth heat
transfer tubes T. Therefore, referring to FIG. 15, it can be seen that the surface
temperature of the relay heat transfer tubes T2b is around 70°C. Further, the relay
heat transfer tube T2c arranged near the seal material S3 corresponds to the eighth
heat transfer tube T. Therefore, referring to FIG. 15, it can be seen that the temperature
of the relay heat transfer tube T2c is around 70°C.
[0081] Returning to FIG. 1, when the vapor refrigerant flows in the indoor heat exchanger
21, the refrigerant is condensed by heat-exchanging with the air, supplied by the
indoor blower 22, of the room R as the object of air conditioning. Then, the specific
enthalpy of the refrigerant falls while maintaining certain pressure. As such, the
vapor refrigerant is converted to low temperature and high pressure supercooled liquid
refrigerant. Also, the above heat exchange heats the air of the room R. As the result,
the room temperature of the room R as the object of air conditioning rised.
[0082] The supercooled liquid refrigerant sent out from the indoor heat exchanger 21passes
through the liquid communication piping 11b, flows in the refrigerant flow channel
of the outdoor machine 30, then, flows in the expansion valve 34 of the outdoor machine
30.
[0083] When the liquid refrigerant flows in the expansion valve 34, the liquid refrigerant
is inflated by the expansion valve 34. Then, the liquid refrigerant is decompressed
while maintaining certain specific enthalpy to be converted to low temperature and
low pressure state, where the refrigerant becomes vapor refrigerant. Then, this vapor
refrigerant is sent out from the expansion valve 34, and flows in the outdoor heat
exchanger 33 of the outdoor machine 30.
[0084] When the vapor refrigerant flows in the outdoor heat exchanger 33, the vapor refrigerant
is condensed by heat-exchanging with the outside air (outdoor air) supplied by the
outdoor blower 35. Then, the specific enthalpy of the refrigerant rised while maintaining
certain pressure. As such, the vapor refrigerant is converted to high temperature
and low pressure heated vapor refrigerant. Then, the vapor refrigerant is sent out
from the outdoor heat exchanger 33.
[0085] The heated vapor refrigerant sent out from the outdoor heat exchanger 33 flows again
in the compressor 31 through the four-way selector 32. Thereafter, the refrigerant
circulates repeatedly above-described refrigerating cycle.
[0086] As described above, in the indoor heat exchanger 21 according to the present embodiment,
as shown in FIG. 5, the inlet piping 12 is connected, instead of to the relay heat
transfer tubes T2a, T2b, T2c arranged near the seal materials S 1-S3, to the inlet
heat transfer tube T1 arranged farther than the relay heat transfer tubes T2a, T2b,
T2c are. As such, in the heating operation, the high heat of the inlet piping 12 cannot
be transferred as easily to the seal materials S1-S3, which suppresses lowering of
the sealing property of the seal materials S1-S3.
[0087] For example, if the inlet piping 12 is connected to the relay heat transfer tubes
T2a, T2b, T2c arranged near the seal materials S 1-S3, the high heat of the inlet
piping 12 is easily transferred to the seal materials S1-S3 through the relay heat
transfer tubes T2a, T2b, and T2c. As the result, the seal materials S1-S3 are likely
to be high temperature. In particular, as R32 is used as refrigerant in the present
embodiment, the temperature of the inlet piping 12 rises, and the surface temperature
of the first heat transfer tube T that the refrigerant flows through reaches around
110°C (refer to FIG. 15). As such, the high heat of the first heat transfer tube T1
that the refrigerant flows through is transferred to the seal materials S1-S3, which
might possibly cause the temperature of the seal materials S 1-S3 to exceed the heat
resistant temperature of 100°C. As the result, the sealing property of the seal materials
S1-S3 is deteriorated, possibly causing the deterioration of reliability of the seal
materials S1-S3.
[0088] However, in the present embodiment, the inlet piping 12 of the refrigerant is connected,
instead of to the relay heat transfer tubes T2a, T2b, T2c arranged near the seal materials
S 1-S3, to the inlet heat transfer tube T1 that is arranged farther than the relay
heat transfer tubes T2a, T2b, T2c are. As such, the high heat of the inlet piping
12 cannot be transferred as easily to the seal materials S1-S3, which suppresses lowering
of the sealing property of the seal materials S 1-S3.
[0089] Further, in the present embodiment, there is no need to reduce to the less amount
of refrigerant circulating through the refrigerating cycle 100 than the standard amount
of refrigerant nor to widen the opening degree of the expansion valve 34, that is,
to increase Cv value of the expansion valve 34 in order to prevent rising of the surface
temperature of the inlet piping 12 of the refrigerant in the heating operation. Therefore,
lowering of the heating operation performance of the air conditioner 10 and the operating
efficiency can be prevented.
[0090] In addition, in the present embodiment, there is no need to use high-priced heat
resistant material for the seal materials S1-S3. As the result, an increase in the
product costs can be suppressed. Further, even when R32 is used as refrigerant, the
seal materials S1-S3 according to the present disclosure can show equivalent sealing
performance to the cases in which R22, R410A, R407C, or the like is used as refrigerant.
[0091] Further, in the outdoor heat exchanger 33 according to the present embodiment, as
shown in FIG. 11, the inlet piping 14 is connected, instead of to the relay heat transfer
tube T2d arranged near the cushioning member 60, to the inlet heat transfer tube T1
that is arranged farther than the relay heat transfer tube T2d is. As such, in the
cooling operation, the high heat of the inlet piping 14 cannot be transferred as easily
to the cushioning member 60, which can suppress degradation of the shock mitigation
performance of the cushioning member 60.
[0092] For example, if the inlet piping 14 is connected to the relay heat transfer tube
T2d that is arranged near the cushioning member 60, the high heat of the inlet piping
14 is easily transferred to the cushioning member 60 through the relay heat transfer
tube T2d. As the result, the cushioning member 60 is prone to be heated to high temperature.
Particularly, as R32 is used as refrigerant in the present embodiment, the high heat
of the inlet piping 14 is transferred, causing the surface temperature of the first
heat transfer tube T that the refrigerant flows through to reach around 110°C (refer
to FIG. 15). As such, the high heat of the first heat transfer tube T that the refrigerant
flows through is transferred to the cushioning member 60, possibly causing the temperature
of the cushioning member 60 to exceed the heat resistant temperature of 80°C. As the
result, the cushioning member 60 is easily degraded, lowering the shock mitigation
performance.
[0093] However, in the present embodiment, the inlet piping 14 of the refrigerant is connected,
instead of to the relay heat transfer tube T2d arranged near the cushioning member
60, to the inlet heat transfer tube T1 that is arranged farther than the relay heat
transfer tube T2d is. As such, the high heat of the inlet piping 14 cannot be transferred
as easily to the cushioning member 60, suppressing deterioration of the cushioning
member 60.
[0094] Further, in the present embodiment, as shown in FIGS. 11 and 13, the inlet piping
14 is connected, instead of to the relay heat transfer tubes T2e, T2f arranged near
the band members 71, 72, to the inlet heat transfer tube T1 that is arranged farther
than the relay heat transfer tubes T2e, T2f are. As such, the high heat of the inlet
piping 14 cannot be transferred as easily to the band members 71, 72 in the cooling
operation, suppressing the degradation of the band members 71, 72.
[0095] For example, if the inlet piping 14 is connected to the relay heat transfer tubes
T2e, T2f that are arranged near the band members 71, 72, the high heat of the inlet
piping 14 is easily transferred to the band members 71, 72 through the relay heat
transfer tubes T2e, T2f. As the result, the band members 71, 72 are prone to be heated
to high temperature. Particularly, as R32 is used as the refrigerant in the present
embodiment, the high heat of the inlet piping 14 is transferred, causing the surface
temperature of the first heat transfer tube T that the refrigerant flows through to
reach around 110°C (refer to FIG. 15). As such, the high heat of the first heat transfer
tube T that the refrigerant flows through is transferred to the band members 71, 72,
possibly causing the temperature of the band members 71, 72 to exceed the heat resistant
temperature of 85°C. As the result, the band members 71, 72 are easily degraded.
[0096] However, in the present embodiment, the inlet piping 14 of the refrigerant is connected,
instead of to the relay heat transfer tubes T2e, T2f arranged near the band members
71, 72, to the inlet heat transfer tube T1 that is arranged farther than the relay
heat transfer tubes T2e, T2f are. As such, the high heat of the inlet piping 14 cannot
be transferred as easily to the band members 71, 72, suppressing deterioration of
the band members 71, 72.
[0097] Further, in the present embodiment, there is no need to reduce to the less amount
of the refrigerant circulating through the refrigerating cycle 100 than the standard
amount of the refrigerant nor to increase Cv value of the expansion valve 34 by widening
the opening of the expansion valve 34 in order to prevent rising of the surface temperature
of the inlet piping 14 of the refrigerant in the cooling operation. Therefore, lowering
of the heating operation performance and operating efficiency of the air conditioner
10 can be prevented.
[0098] In addition, there is no need to use high priced, heat resistant material for the
cushioning member 60 and the band members 71, 72. As the result, an increase in the
product costs can be suppressed. Further, even when R32 is used as refrigerant, the
cushioning member 60, band members 71, 72 according to the present embodiment can
show equivalent performance to the cases in which R22, R410A, R407C, or the like is
used as refrigerant.
[0099] So far, the embodiment of the present disclosure has been described without limiting
the present disclosure to the above embodiment.
[0100] For example, in the present embodiment, as shown in FIG. 5, five relay heat transfer
tubes T2 including the relay heat transfer tube T2a arranged nearest the seal material
S 1 are arranged between the seal material S1 and the inlet heat transfer tube T1.
However, without limitation, at least one relay heat transfer tube T2 may be arranged
between the seal material S1 and the inlet heat transfer tube T1. In other words,
so as not to make the heat transfer tube T nearest the seal material S1 become 100°C
or more, in the heating operation, the inlet piping 12 of the refrigerant should not
be connected to the heat transfer tube T nearest the seal material S1. This is because,
as shown in FIG. 15, when R32 is the refrigerant, the surface temperature of the second
heat transfer tube T decreases to around 92°C which is lower than 100°C.
[0101] Further, in the present embodiment, as shown in FIG. 5, a plurality of relay heat
transfer tubes T2, including the relay heat transfer tube T2b arranged nearest the
seal material S2, are arranged between the seal material S2 and the inlet heat transfer
tube T1. However, without limitation, at least one relay heat transfer tube T2 may
be arranged between the seal material S2 and the inlet heat transfer tube T1. In other
words, so as not to make the heat transfer tube T nearest the seal material S1 become
100°C or more, in the heating operation, the inlet piping 12 of the refrigerant should
not be connected to the heat transfer tube T nearest the seal material S2. This is
because, as shown in FIG. 15, when R32 is the refrigerant, the surface temperature
of the second heat transfer tube T decreases to around 92°C which is lower than 100°C.
[0102] Likewise, as long as the inlet piping 12 of the refrigerant in the heating operation
is not connected to the heat transfer tube T nearest the seal material S3, the positions
of the other heat transfer tubes T are arbitrary. That is, so as not to make the heat
transfer tube T nearest the seal material S3 become 100°C or more, the inlet piping
12 should be connected to the heat transfer tube T.
[0103] Further, in the present embodiment, as shown in FIG. 11, five relay heat transfer
tubes T2 including the relay heat transfer tube T2d arranged nearest the cushioning
member 60 are arranged between the cushioning member 60 and the inlet heat transfer
tube T1 of path P3. However, without limitation, four or less relay heat transfer
tubes T2 may be arranged or six or more relay heat transfer tubes T2 may be arranged
between the cushioning member 60 and the inlet heat transfer tube T1. However, taking
into account that the heat resistant temperature of the cushioning member 60 is 80°C;
the surface temperature of the second heat transfer tube T is around 92°C; and the
surface temperature of the third heat transfer tube T is around 75°C, as shown in
FIG. 15, the relay heat transfer tube T2d shown in FIG. 11 is preferably not the first
or second heat transfer tube T that the refrigerant passes through. That is, the relay
heat transfer tube T2d arranged nearest the cushioning member 60 is preferably the
third heat transfer tube T or later that the refrigerant passes through when the inlet
heat transfer tube T1 is the first heat transfer tube T that the refrigerant passes
through.
[0104] Further, in the present embodiment, as shown in FIG. 11, four relay heat transfer
tubes T2 including the relay heat transfer tube T2e arranged nearest the band member
71 are arranged between the band member 71 and the inlet heat transfer tube T1 of
path P5. However, without limitation, three or less relay heat transfer tubes T2 may
be arranged or five or more relay heat transfer tubes T2 may be arranged between the
band member 71 and the inlet heat transfer tube T1. However, taking into account that
the heat resistant temperature of the band member 71 is 85°C; the surface temperature
of the second heat transfer tube T is around 92°C; and the surface temperature of
the third heat transfer tube T is around 75°C, as shown in FIG. 15, the relay heat
transfer tube T2e shown in FIG. 11 is preferably not the first or second heat transfer
tube T that the refrigerant passes through. That is, the relay heat transfer tube
T2e arranged nearest the band member 71 is preferably the third heat transfer tube
T or later that the refrigerant passes through when the inlet heat transfer tube T1
is the first heat transfer tube T that the refrigerant passes through.
[0105] Further, in the present embodiment, as shown in FIG. 13, three relay heat transfer
tubes T2 including the relay heat transfer tube T2f arranged nearest the band member
72 are arranged between the band member 72 and the inlet heat transfer tube T1 of
path P5. However, without limitation, two or less relay heat transfer tubes T2 may
be arranged or four or more relay heat transfer tubes T2 may be arranged between the
band member 72 and the inlet heat transfer tube T1. However, taking into account that
the heat resistant temperature of the band member 72 is 85°C; the surface temperature
of the second heat transfer tube T is around 92°C; and the surface temperature of
the third heat transfer tube T is around 75°C, as shown in FIG. 15, the relay heat
transfer tube T2f shown in FIG. 13 is preferably not the first or second heat transfer
tube T that the refrigerant passes through. That is, the relay heat transfer tube
T2f arranged nearest the band member 72 is preferably the third heat transfer tube
T or later that the refrigerant passes through when the inlet heat transfer tube T1
is the first heat transfer tube T that the refrigerant passes through.
[0106] Further, the indoor heat exchanger 21 according to the present embodiment has two
fin units (front-side fin unit 41, back-side fin unit 42). However, without limitation,
the indoor heat exchanger 21 may have three or more fin units. Likewise, the outdoor
heat exchanger 33 according to the present embodiment has two fin units (front-side
fin unit 43, back-side fin unit 44). However, without limitation, the outdoor heat
exchanger 33 may have three or more fin units.
[0107] Further, the indoor heat exchanger 21 according to the present embodiment has two
paths P1, P2 formed therein. However, without limitation, for example, one path or
three or more paths may be formed in the indoor heat exchanger 21.
[0108] Further, the outdoor heat exchanger 33 according to the present embodiment has four
paths P3-P6 formed therein. However, without limitation, for example, three or less
paths, or five or more paths may be formed in the outdoor heat exchanger 33.
[0109] Further, in the present embodiment, the material of the seal materials S 1-S3 is
EPDM rubber foam with one side being an adhesive face, while other material may also
be used without limitation. However, in view of costs and availability, EPDM rubber
foam is preferable.
[0110] Further, while the material of the cushioning member 60 is foamed styrol material
in the present embodiment, other material may also be used without limitation. However,
in view of costs and availability, foamed styrol material is preferable.
[0111] Further, while the material of the band members 71, 72 is 6,6 nylon in the present
embodiment, other material may also be used without limitation. However, in view of
costs and availability, 6,6 nylon is preferable.
[0112] Further, in the present embodiment, the outdoor heat exchanger 33 has one cushioning
member 60 as shown in FIGS. 10 and 11. However, without limitation, the outdoor heat
exchanger 33 may have two or more cushioning members 60. Further, while, in the present
embodiment, the cushioning member 60 is arranged on the -X side end plane of the front-side
fin unit 43 without limitation, the position where the cushioning member 60 is arranged
is arbitrary. For example, the cushioning member 60 may be arranged between the outdoor
machine chassis 36 and the back-side fin unit 44, or other places.
[0113] Further, in the present embodiment, the outdoor heat exchanger 33 has two band members
71, 72 as shown in FIGS. 11 to 14. However, without limitation, the outdoor heat exchanger
33 has three or more band members 71, 72. Further, the places that the band members
71, 72 tie are also arbitrary. The band members 71, 72 may fix other places than the
above-described places.
[0114] Further, in the present embodiment, refrigerant consisting only of R32 or R32-rich
refrigerant with R32 content of 50% or more is used as the refrigerant used for the
air conditioner 10. However, without limitation, other refrigerant (for example, R22,
R410A, R407C or the like) may also be used. In such cases, it should be appreciated
that the inlet piping 12 of the refrigerant in the heating operation and the inlet
piping 14 of the refrigerant in the cooling operation do not become high temperature,
thus, the seal materials S1-S3, the cushioning member 60, and the band members 71,
72 are not deteriorated.
[0115] Various embodiments and modifications of the present disclosure are possible without
departing from the wide spirit and scope of the present disclosure. The above-described
embodiment is only for explanation of the present disclosure without limiting the
scope of the present disclosure.
[0116] The air conditioner according to the present disclosure is suitable for air conditioning
the target of air conditioning. Further, the indoor heat exchanger, the indoor machine,
the outdoor heat exchanger, and the outdoor machine according to the present disclosure
are suitable to be used in air conditioners.
legend
[0117]
- 10
- air conditioner
- 11a
- gas communication piping
- 11b
- liquid communication piping
- 12
- inlet piping (for refrigerant in heating operation)
- 13
- outlet piping (for refrigerant in heating operation)
- 14
- inlet piping (for refrigerant in cooling operation)
- 15
- outlet piping (for refrigerant in cooling operation)
- 20
- indoor machine
- 21
- indoor heat exchanger
- 22
- indoor blower
- 22a
- blower fan
- 23
- indoor machine chassis
- 23a
- front panel
- 23b
- air channel
- 24, 25
- air inlet
- 26
- air outlet
- 27
- horizontal vane
- 28
- vertical flap
- 29A, 29B
- condensate receiver
- 30
- outdoor machine
- 31
- compressor
- 32
- four-way selector
- 33
- outdoor heat exchanger
- 34
- expansion valve
- 35
- outdoor blower
- 35a
- blower fan
- 35b
- fan motor
- 36
- outdoor machine chassis
- 37
- partitioning plate
- 41
- front-side fin unit (first fin unit)
- 42
- back-side fin unit (second fin unit)
- 43
- front-side fin unit (third fin unit)
- 44
- back-side fin unit (fourth fin unit)
- 45
- through hole
- 50
- hairpin (folded-back piping)
- 51
- U-shaped piping (folded-back piping)
- 60
- cushioning member
- 71, 72
- band member (fixing member)
- 100
- refrigerating cycle
- S1-S3
- seal material
- A
- air flow
- M
- machine room
- F
- blower room
- P1-P6
- path
- R
- room
- T
- heat transfer tube
- T1
- inlet heat transfer tube
- T2, T2a to T2f, T2-1 to T2-12
- relay heat transfer tube
- T3
- outlet heat transfer tube
- L1
- row pitch
- L2
- stage pitch