U.S. patent application number 13/258514 was filed with the patent office on 2012-01-19 for dehumidification system.
Invention is credited to Koichi Ishida, Yasunori Okamoto, Hideki Uchida.
Application Number | 20120012285 13/258514 |
Document ID | / |
Family ID | 42827736 |
Filed Date | 2012-01-19 |
United States Patent
Application |
20120012285 |
Kind Code |
A1 |
Okamoto; Yasunori ; et
al. |
January 19, 2012 |
DEHUMIDIFICATION SYSTEM
Abstract
A dehumidification system includes: an auxiliary heat exchanger
connected to the heating medium circuit in series with the cooling
heat exchanger, and provided downstream of a cooling heat exchanger
in an air passage; a first air heat exchanger connected to a
circulation circuit, and provided upstream of the cooling heat
exchanger in the air passage; and a second air heat exchanger
connected to the circulation circuit in series with the first air
heat exchanger, and provided downstream of the auxiliary heat
exchanger in the air passage, wherein the heating medium circuit
performs a first action of sending a heating medium which is cooled
in a cooling section, and sequentially flowed through the cooling
heat exchanger and the auxiliary heat exchanger to the cooling
section.
Inventors: |
Okamoto; Yasunori; (Osaka,
JP) ; Ishida; Koichi; (Osaka, JP) ; Uchida;
Hideki; (Osaka, JP) |
Family ID: |
42827736 |
Appl. No.: |
13/258514 |
Filed: |
March 23, 2010 |
PCT Filed: |
March 23, 2010 |
PCT NO: |
PCT/JP2010/002037 |
371 Date: |
September 22, 2011 |
Current U.S.
Class: |
165/110 |
Current CPC
Class: |
H01L 21/67017 20130101;
F24F 3/153 20130101; H01L 21/67109 20130101 |
Class at
Publication: |
165/110 |
International
Class: |
F28D 21/00 20060101
F28D021/00 |
Foreign Application Data
Date |
Code |
Application Number |
Apr 2, 2009 |
JP |
2009-090049 |
Claims
1. A dehumidification system comprising: a casing which forms an
air passage through which air flows; a heating medium circuit which
includes a cooling section for cooling a predetermined heating
medium, and in which the heating medium circulates; a cooling heat
exchanger which is connected to the heating medium circuit, and is
provided in the air passage to cool and dehumidify the air by the
heating medium flowing through the cooling heat exchanger to supply
the dehumidified air to the inside of a room; an auxiliary heat
exchanger which is connected to the heating medium circuit in
series with the cooling heat exchanger, and is arranged downstream
of the cooling heat exchanger in the air passage; a first air heat
exchanger which is connected to a circulation circuit in which the
predetermined heating medium circulates, and is arranged upstream
of the cooling heat exchanger in the air passage; and a second air
heat exchanger which is connected to the circulation circuit in
series with the first air heat exchanger, and is arranged
downstream of the auxiliary heat exchanger in the air passage,
wherein the heating medium circuit performs a first action of
sending the heating medium which is cooled in the cooling section,
and sequentially flowed through the cooling heat exchanger and the
auxiliary heat exchanger to the cooling section.
2. The dehumidification system of claim 1, further comprising: a
heating section which is arranged downstream of the second air heat
exchanger in the air passage to heat the air.
3. The dehumidification system of claim 1, wherein the cooling heat
exchanger includes an inlet which is positioned in a downstream
part of the air passage, and through which the heating medium flows
into the cooling heat exchanger, an outlet which is positioned in
an upstream part of the air passage, and through which the heating
medium flows out of the cooling heat exchanger, and an intermediate
passage formed between the inlet and the outlet.
4. The dehumidification system of claim 3, wherein the auxiliary
heat exchanger includes an inlet which is positioned in the
downstream part of the air passage, and through which the heating
medium flows into the auxiliary heat exchanger, an outlet which is
positioned in the upstream part of the air passage, and through
which the heating medium flows out of the auxiliary heat exchanger,
and an intermediate passage formed between the inlet and the
outlet.
5. The dehumidification system of claim 4, wherein the first air
heat exchanger includes an inlet which is positioned in the
downstream part of the air passage, and through which the heating
medium flows into the first air heat exchanger, an outlet which is
positioned in the upstream part of the air passage, and through
which the heating medium flows out of the first air heat exchanger,
and an intermediate passage formed between the inlet and the
outlet.
6. The dehumidification system of claim 5, wherein the second air
heat exchanger includes an inlet which is positioned in the
downstream part of the air passage, and through which the heating
medium flows into the second air heat exchanger, an outlet which is
positioned in the upstream part of the air passage, and through
which the heating medium flows out of the second air heat
exchanger, and an intermediate passage formed between the inlet and
the outlet.
7. The dehumidification system of claim 1, wherein the heating
medium circuit is configured to perform the first action, and a
second action of sending the heating medium which is cooled in the
cooling section, and sequentially flowed through the auxiliary heat
exchanger and the cooling heat exchanger to the cooling section in
a switchable manner.
8. The dehumidification system of claim 1, further comprising: a
branch passage which diverts the heating medium circulating in the
circulation circuit, and introduces the diverted heating medium
into the circulation circuit; an auxiliary cooling section which
cools the heating medium flowing through the branch passage; and a
diverted flow control mechanism which regulates a flow rate of the
heating medium flowing through the branch passage.
9. The dehumidification system of claim 1, further comprising: a
flow rate control mechanism which separately regulates a flow rate
of the heating medium flowing through the first air heat exchanger,
and a flow rate of the heating medium flowing through the second
air heat exchanger.
10. The dehumidification system of claim 1, further comprising: an
exhaust passage through which the air in the room is discharged
outside; and a sensible heat exchanger in which the heating medium
flowing through the circulation circuit and the air flowing through
the exhaust passage exchange heat.
11. The dehumidification system of claim 1, further comprising: a
bypass passage which transfers the air in the air passage upstream
of the first air heat exchanger to the downstream of the cooling
heat exchanger; and a bypass flow control mechanism which regulates
a flow rate of the air flowing through the bypass passage.
Description
TECHNICAL FIELD
[0001] The present invention relates to a dehumidification system
which cools and dehumidifies air, and supplies the dehumidified air
to the inside of a room.
BACKGROUND ART
[0002] Dehumidification systems for supplying dehumidified air to
the inside of the room have been known.
[0003] For example, Patent Document 1 discloses a dehumidification
system of this type. The dehumidification system includes a cooling
heat exchanger in an air passage in a casing. The cooling heat
exchanger is connected to a circulation circuit in which a heating
medium such as water etc. circulates. The circulation circuit
includes a pump for circulating the heating medium, and a cooling
section for cooling the circulating heating medium.
[0004] When the dehumidification system is operated, the pump is
operated to circulate water in the circulation circuit. The water
is cooled in the cooling section, and then flows through the
cooling heat exchanger. The air flows through the air passage while
a fan is operated. Thus, in the cooling heat exchanger, the water
and the air exchange heat to cool the air to a dew point
temperature or lower. As a result, moisture in the air is condensed
to dehumidify the air. The air cooled and dehumidified in this
manner is supplied to the inside of the room.
CITATION LIST
[0005] Patent Document
[0006] [Patent Document 1] Japanese Patent Publication No.
2006-112780
SUMMARY OF THE INVENTION
Technical Problem
[0007] In the dehumidification system of this type described above,
the air needs to be cooled to the dew point temperature or lower in
the cooling heat exchanger to dehumidify the air. Thus, the cooling
section of the circulation circuit needs to cool the heating medium
to a relatively low temperature. Therefore, relatively high cooling
capacity is required in the cooling section, which reduces
energy-saving effect.
[0008] In view of the foregoing, the present invention has been
achieved. The invention is concerned with providing an
energy-saving dehumidification system.
Solution to the Problem
[0009] According to a first aspect of the invention, a
dehumidification system includes: a casing (51) which forms an air
passage (52) through which air flows; a heating medium circuit (41)
which includes a cooling section (25) for cooling a predetermined
heating medium, and in which the heating medium circulates; a
cooling heat exchanger (61) which is connected to the heating
medium circuit (41), and is provided in the air passage (52) to
cool and dehumidify the air by the heating medium flowing through
the cooling heat exchanger (61) to supply the dehumidified air to
the inside of a room. The dehumidification system includes: an
auxiliary heat exchanger (62) which is connected to the heating
medium circuit (41) in series with the cooling heat exchanger (61),
and is arranged downstream of the cooling heat exchanger (61) in
the air passage (52); a first air heat exchanger (63) which is
connected to a circulation circuit (60, 130) in which the
predetermined heating medium circulates, and is arranged upstream
of the cooling heat exchanger (61) in the air passage (52); and a
second air heat exchanger (64) which is connected to the
circulation circuit (60, 130) in series with the first air heat
exchanger (63), and is arranged downstream of the auxiliary heat
exchanger (62) in the air passage (52), wherein the heating medium
circuit (41) performs a first action of sending the heating medium
which is cooled in the cooling section (25), and sequentially
flowed through the cooling heat exchanger (61) and the auxiliary
heat exchanger (62) to the cooling section (25).
[0010] According to the first aspect of the invention, the
auxiliary heat exchanger (62) is provided downstream of the cooling
heat exchanger (61) in the air passage (52) in the casing (51), the
first air heat exchanger (63) is provided upstream of the cooling
heat exchanger (61), and the second air heat exchanger (64) is
provided downstream of the auxiliary heat exchanger (62). The air
flowing in the air passage (52) first passes through the first air
heat exchanger (63). The heating medium circulating in the
circulation circuit (60, 130) flows in the first air heat exchanger
(63). Thus, the air and the heating medium exchange heat, and the
air is cooled by the heating medium in the first air heat exchanger
(63). On the other hand, the heating medium is heated by the air in
the first air heat exchanger (63).
[0011] The air cooled in the first air heat exchanger (63) passes
through the cooling heat exchanger (61). In the heating medium
circuit (41) performing the first action, the heating medium cooled
in the cooling section (25) sequentially flows through the cooling
heat exchanger (61) and the auxiliary heat exchanger (62). Thus,
the air is cooled to a dew point temperature or lower by the
heating medium of relatively low temperature, and is dehumidified
in the cooling heat exchanger (61). On the other hand, the heating
medium is heated by the air in the cooling heat exchanger (61).
[0012] The air cooled in the cooling heat exchanger (61) passes
through the auxiliary heat exchanger (62). The heating medium
heated in the cooling heat exchanger (61) flows in the in the
auxiliary heat exchanger (62). Thus, the air is heated by the
heating medium of relatively high temperature in the auxiliary heat
exchanger (62). Thus, relative humidity of the air is reduced. On
the other hand, the heating medium is cooled by the air in the
auxiliary heat exchanger (62). Thus, the temperature of the heating
medium sent to the cooling section (25) of the heating medium
circuit (41) is reduced, thereby reducing cooling capacity required
to cool the heating medium in the cooling section (25).
[0013] The air heated in the auxiliary heat exchanger (62) passes
through the second air heat exchanger (64). The heating medium
heated in the first air heat exchanger (63) flows in the second air
heat exchanger (64). Thus, the air is further heated by the heating
medium of relatively high temperature in the second air heat
exchanger (64). This further reduces the relative humidity of the
air.
[0014] According to a second aspect related to the first aspect of
the invention, the dehumidification system further includes: a
heating section (55) which is arranged downstream of the second air
heat exchanger (64) in the air passage (52) to heat the air.
[0015] According to the second aspect of the invention, the heating
section (55) is provided downstream of the second air heat
exchanger (64). Thus, the air which passed through the second air
heat exchanger (64) can be heated by the heating section (55). This
can further reduce the relative humidity of the air which passed
through the heating section (55). The air before flowing into the
heating section (55) has already been heated by the auxiliary heat
exchanger (62) and the second air heat exchanger (64) as described
above. Therefore, heating capacity required to heat the air in the
heating section (55) can be reduced.
[0016] According to a third aspect related to the first or second
aspect of the invention, the cooling heat exchanger (61) includes
an inlet (71a) which is positioned in a downstream part of the air
passage (52), and through which the heating medium flows into the
cooling heat exchanger (61), an outlet (71b) which is positioned in
an upstream part of the air passage (52), and through which the
heating medium flows out of the cooling heat exchanger (61), and an
intermediate passage (61c) formed between the inlet (71a) and the
outlet (71b).
[0017] In the cooling heat exchanger (61) according to the third
aspect of the invention, the inlet (71a) through which the heating
medium flows into the cooling heat exchanger (61) is provided in
the downstream part of the air passage (52), the outlet (71b)
through which the heating medium flows out of the cooling heat
exchanger (61) is provided in the upstream part of the air passage
(52), and the intermediate passage (61c) through which the heating
medium flows is formed between the inlet (71a) and the outlet
(71b). Thus, in the cooling heat exchanger (61) during the first
action, the air and the heating medium flow substantially in
opposite directions to exchange heat therebetween. Specifically, in
the present invention, the cooling heat exchanger (61) during the
first action can function as a so-called convection heat exchanger.
With this configuration, the temperature of the air flowing out of
the cooling heat exchanger (61) approaches the temperature of the
heating medium flowing through the inlet (71a). Thus, for example,
as compared with a so-called parallel heat exchanger, the cooling
heat exchanger (61) can cool/dehumidify the air more effectively.
On the other hand, the temperature of the heating medium flowing
through the outlet (71b) of the cooling heat exchanger (61)
approaches the temperature of the air flowing into the cooling heat
exchanger (61). Thus, for example, as compared with the parallel
heat exchanger, the cooling heat exchanger (61) can increase the
temperature of the heating medium sent from the cooling heat
exchanger (61) to the auxiliary heat exchanger (62).
[0018] With this configuration, the heating medium which is cooled
to a relatively low temperature in the cooling heat exchanger (61)
and the air which is heated to a relatively high temperature in the
cooling heat exchanger (61) exchange heat in the auxiliary heat
exchanger (62). Thus, a difference in temperature between the
heating medium and the air in the auxiliary heat exchanger (62)
increases, thereby effectively cooling the heating medium by the
air (i.e., effectively heating the air by the heating medium). This
can further reduce the relative humidity of the air, thereby
improving the dehumidification of the air. Since the temperature of
the heating medium sent to the cooling section (25) of the heating
medium circuit (41) can further be reduced, the cooling capacity
required to cool the heating medium in the cooling section (25) can
further be reduced.
[0019] According to a fourth aspect of the invention related to any
one of the first to third aspects of the invention, the auxiliary
heat exchanger (62) includes an inlet (72a) which is positioned in
the downstream part of the air passage (52), and through which the
heating medium flows into the auxiliary heat exchanger (62), an
outlet (72b) which is positioned in the upstream part of the air
passage (52), and through which the heating medium flows out of the
auxiliary heat exchanger (62), and an intermediate passage (62c)
formed between the inlet (72a) and the outlet (72b).
[0020] In the auxiliary heat exchanger (62) according to the fourth
aspect of the invention, the inlet (72a) through which the heating
medium flows into the auxiliary heat exchanger (62) is provided in
the downstream part of the air passage (52), the outlet (72b)
through which the heating medium flows out of the auxiliary heat
exchanger (62) is provided in the upstream part of the air passage
(52), and the intermediate passage (62c) through which the heating
medium flows is formed between the inlet (72a) and the outlet
(72b). Thus, in the auxiliary heat exchanger (62) during the first
action, the air and the heating medium flow substantially in the
opposite directions to exchange heat therebetween. With this
configuration, the temperature of the air flowing out of the
auxiliary heat exchanger (62) approaches the temperature of the
heating medium flowing through the inlet (72a). Thus, for example,
as compared with the so-called parallel heat exchanger, the
auxiliary heat exchanger (62) can heat the air more effectively.
The temperature of the heating medium flowing through the outlet
(72b) of the auxiliary heat exchanger (62) approaches the
temperature of the air flowing into the auxiliary heat exchanger
(62). Thus, for example, as compared with the parallel heat
exchanger, the temperature of the heating medium sent to the
cooling section (25) of the heating medium circuit (41) can further
be reduced. This can further reduce the cooling capacity required
to cool the heating medium in the cooling section (25).
[0021] According to a fifth aspect of the invention related to any
one of the first to fourth aspects of the invention, the first air
heat exchanger (63) includes an inlet (73a) which is positioned in
the downstream part of the air passage (52), and through which the
heating medium flows into the first air heat exchanger (63), an
outlet (73b) which is positioned in the upstream part of the air
passage (52), and through which the heating medium flows out of the
first air heat exchanger (63), and an intermediate passage (63c)
formed between the inlet (73a) and the outlet (73b).
[0022] In the first air heat exchanger (63) according to the fifth
aspect of the invention, the inlet (73a) through which the heating
medium flows into the first air heat exchanger (63) is provided in
the downstream part of the air passage (52), the outlet (73b)
through which the heating medium flows out of the first air heat
exchanger (63) is provided in the upstream part of the air passage
(52), and the intermediate passage (63c, 63c, . . . ) through which
the heating medium flows is formed between the inlet (73a) and the
outlet (73b). Thus, in the first air heat exchanger (63), the air
and the heating medium flow substantially in the opposite
directions to exchange heat therebetween. In the present invention,
the first air heat exchanger (63) can function as the so-called
convection heat exchanger. With this configuration, the temperature
of the air flowing out of the first air heat exchanger (63)
approaches the temperature of the heating medium flowing through
the inlet (73a). Thus, for example, as compared with the parallel
heat exchanger, the first air heat exchanger (63) can cool the air
more effectively.
[0023] On the other hand, the temperature of the heating medium
flowing through the outlet (73b) of the first air heat exchanger
(63) approaches the temperature of the air flowing into the first
air heat exchanger (63). Thus, for example, as compared with the
parallel heat exchanger, the first air heat exchanger (63) can
increase the temperature of the heating medium sent from the first
air heat exchanger (63) to the second air heat exchanger (64).
Thus, a difference in temperature between the air and the heating
medium in the second air heat exchanger (64) increases, thereby
improving the heating of the air in the second air heat exchanger
(64). This can further reduce the relative humidity of the air in
the second air heat exchanger (64).
[0024] According to a sixth aspect of the invention related to any
one of the first to fifth aspects of the invention, the second air
heat exchanger (64) includes an inlet (74a) which is positioned in
the downstream part of the air passage (52), and through which the
heating medium flows into the second air heat exchanger (64), an
outlet (74b) which is positioned in the upstream part of the air
passage (52), and through which the heating medium flows out of the
second air heat exchanger (64), and an intermediate passage (64c)
formed between the inlet (74a) and the outlet (74b).
[0025] In the second air heat exchanger (64) according to the sixth
aspect of the invention, the inlet (74a) through which the heating
medium flows into the second air heat exchanger (64) is provided in
the downstream part of the air passage (52), the outlet (74b)
through which the heating medium flows out of the second air heat
exchanger (64) is provided in the upstream part of the air passage
(52), and the intermediate passage (64c) through which the heating
medium flows is formed between the inlet (74a) and the outlet
(74b). Thus, in the second air heat exchanger (64), the air and the
heating medium can flow substantially in the opposite directions to
exchange heat therebetween. Specifically, in the present invention,
the second air heat exchanger (64) can function as the so-called
convection heat exchanger.
[0026] With this configuration, the temperature of the air flowing
out of the second air heat exchanger (64) approaches the
temperature of the heating medium flowing through the inlet (74a).
Thus, for example, as compared with the parallel heat exchanger,
the first air heat exchanger (63) can heat the a it more
effectively. This can further reduce the relative humidity of the
air in the second air heat exchanger (64).
[0027] On the other hand, the temperature of the heating medium
flowing through the outlet (74b) of the second air heat exchanger
(64) approaches the temperature of the air flowing into the second
air heat exchanger (64). Thus, for example, as compared with the
parallel heat exchanger, the second air heat exchanger (64) can
cool the heating medium more effectively. Thus, the temperature of
the heating medium sent from the second air heat exchanger (64) to
the first air heat exchanger (63) can further be reduced, thereby
cooling the air more effectively in the first air heat exchanger
(63).
[0028] According to a seventh aspect of the invention related to
any one of the first to sixth aspects of the invention, the heating
medium circuit (41) is configured to perform the first action, and
a second action of sending the heating medium which is cooled in
the cooling section (25), and sequentially flowed through the
auxiliary heat exchanger (62) and the cooling heat exchanger (61)
to the cooling section (25) in a switchable manner.
[0029] In the heating medium circuit (41) according to the seventh
aspect of the invention, the second action is performed in addition
to the above-described first action. In the heating medium circuit
(41) performing the second action, the heating medium cooled in the
cooling section (25) sequentially flows through the auxiliary heat
exchanger (62) and the cooling heat exchanger (61). Specifically,
in the air passage (52), the air sequentially flows through the
cooling heat exchanger (61) and the auxiliary heat exchanger (62),
while the heating medium flows in the opposite way. Thus, different
from the first action, the heating medium cooled in the cooling
section (25) first flows through the auxiliary heat exchanger (62),
and the air is cooled by the heating medium. As a result, the air
is cooled in both of the cooling heat exchanger (61) and the
auxiliary heat exchanger (62) in the second action, thereby
improving the dehumidification of the air.
[0030] According to an eighth aspect of the invention related to
any one of the first to seventh aspects of the invention, the
dehumidification system further includes: a branch passage (66)
which diverts the heating medium circulating in the circulation
circuit (60, 130), and introduces the diverted heating medium into
the circulation circuit (60, 130); an auxiliary cooling section
(95) which cools the heating medium flowing through the branch
passage (66); and a diverted flow control mechanism (97) which
regulates a flow rate of the heating medium flowing through the
branch passage (66).
[0031] In the eighth aspect of the invention, the diverted flow
control mechanism (97) regulates the flow rate of the heating
medium flowing through the branch passage (66), thereby changing
the cooling capacity required to cool the air in the first air heat
exchanger (63). Specifically, for example, when the diverted flow
control mechanism (97) increases the flow rate of the heating
medium flowing through the branch passage (66), an amount of the
heating medium cooled in the an auxiliary cooling unit (95) is
increased. Thus, the temperature of the heating medium returned to
the circulation circuit (60, 130) is reduced, and the cooling
capacity of the first air heat exchanger (63) is reduced.
[0032] For example, when the diverted flow control mechanism (97)
reduces the flow rate of the heating medium flowing through the
branch passage (66), the amount of the heating medium cooled in the
an auxiliary cooling unit (95) is reduced. Thus, the temperature of
the heating medium returned to the circulation circuit (60, 130) is
increased, and the cooling capacity of the first air heat exchanger
(63) is increased.
[0033] According to a ninth aspect of the invention related to any
one of the first to eighth aspects of the invention, the
dehumidification system further includes: a flow rate control
mechanism (35-37, 65) which separately regulates a flow rate of the
heating medium flowing through the first air heat exchanger (63),
and a flow rate of the heating medium flowing through the second
air heat exchanger (64).
[0034] In the ninth aspect of the invention, the flow rate control
mechanism (35-37, 65) can separately regulate the flow rates of the
heating medium flowing through the first air heat exchanger (63)
and the second air heat exchanger (64). Thus, for example,
cooling/dehumidifying capacity required to cool/dehumidify the air
in the first air heat exchanger (63) can be changed by changing the
flow rate of the heating medium flowing through the first air heat
exchanger (63). Further, air heating capacity required to heat the
air in the second air heat exchanger (64) can be changed by
changing the flow rate of the heating medium flowing through the
second air heat exchanger (64).
[0035] According to a tenth aspect of the invention related to any
one of the first to ninth aspects of the invention, the
dehumidification system further includes: an exhaust passage (59)
through which the air in the room is discharged outside; and a
sensible heat exchanger (68) in which the heating medium flowing
through the circulation circuit (60, 130) and the air flowing
through the exhaust passage (59) exchange heat.
[0036] In the tenth aspect of the invention, the room air is
discharged outside through the exhaust passage (59). In this case,
the heating medium used to cool the air in the first air heat
exchanger (63) exchanges heat with the room air in the sensible
heat exchanger (68) provided in the exhaust passage (59). Thus, for
example, when the temperature of the room air flowing through the
exhaust passage (59) is relatively low, cold of the room air can be
added to the heating medium. This can improve the cooling of the
air in the first air heat exchanger (63).
[0037] For example, when the temperature of the room air flowing
through the exhaust passage (59) is relatively high, the heat of
the room air can be added to the heating medium. This can improve
the heating of the air in the second air heat exchanger (64).
[0038] According to an eleventh aspect of the invention related to
any one of the first to tenth aspects of the invention, the
dehumidification system further includes: a bypass passage (140)
which transfers the air in the air passage (52) upstream of the
first air heat exchanger (63) to the downstream of the cooling heat
exchanger (61); and a bypass flow control mechanism (141) which
regulates a flow rate of the air flowing through the bypass passage
(140).
[0039] In the eleventh aspect of the invention, the bypass passage
(140) is provided in the air passage (52), and the flow rate of the
air flowing through the bypass passage (140) can be regulated by
the bypass flow control mechanism (141). For example, when the flow
rate of the air flowing through the bypass passage (140) is
increased, the flow rate of the air which is cooled/dehumidified in
the first air heat exchanger (63) and the cooling heat exchanger
(61) is reduced. Thus, an amount of latent heat handled by the
dehumidification system is reduced. For example, when the flow rate
of the air flowing through the bypass passage (140) is reduced, the
flow rate of the air which is cooled/dehumidified in the first air
heat exchanger (63) and the cooling heat exchanger (61) is
increased. Thus, in the present invention, changing the flow rate
of the air flowing through the bypass passage (140) allows
operation corresponding to a latent heat load.
ADVANTAGES OF THE INVENTION
[0040] In the present invention, the air is cooled in advance by
the heating medium flowing through the first air heat exchanger
(63), and then the air is cooled/dehumidified in the cooling heat
exchanger (61). This can reduce the cooling capacity required to
cool the air in the cooling heat exchanger (61), and can reduce the
cooling capacity required to cool the air in the cooling section
(25) of the heating medium circuit (41). In the auxiliary heat
exchanger (62), the air is heated by heat collected from the air in
the cooling heat exchanger (61). This can improve the dehumidifying
capacity, and the temperature of the heating medium sent to the
cooling section (25) can be reduced. Thus, the cooling capacity
required in the cooling section (25), and an amount of the heating
medium circulating in the heating medium circuit (41) can be both
reduced. In the second air heat exchanger (64), the air is heated
by heat collected from the air in the first air heat exchanger
(63). This can further improve the dehumidifying capacity, and cold
collected from the air can be used again to cool the air in the
first air heat exchanger (63). Thus, the present invention can
improve the dehumidifying capacity, while significantly reducing
energy consumption of the dehumidification system.
[0041] In the second aspect of the invention, the air can be heated
in the auxiliary heat exchanger (62) and the second air heat
exchanger (64), thereby reducing the heating capacity required to
heat the air in the heating section (55). This can further reduce
the energy consumption of the dehumidification system.
[0042] In the third aspect of the invention, the air and the
heating medium flow in the opposite directions in the cooling heat
exchanger (61) to exchange heat therebetween. Thus, in the cooling
heat exchanger (61) during the first action, the air can be cooled
to a lower temperature, and the heating medium can be heated to a
higher temperature. This can reduce the cooling capacity required
in the cooling section (25), and the heating capacity required in
the heating section (55) etc., thereby further reducing energy
consumption of the dehumidification system. In the fourth aspect of
the invention, the heating medium and the air flow in the opposite
directions in the auxiliary heat exchanger (62) during the first
action to exchange heat therebetween. Thus, the temperature of the
heating medium flowing out of the auxiliary heat exchanger (62) is
further reduced, and the temperature of the air passing through the
auxiliary heat exchanger (62) is further increased. This can
further reduce the cooling capacity required in the cooling section
(25), and the heating capacity required in the heating section (55)
etc.
[0043] In the fifth aspect of the invention, the air and the
heating medium flow in the opposite directions in the first air
heat exchanger (63) to exchange heat therebetween. Thus, the air
can be cooled to a lower temperature, and the heating medium can be
heated to a higher temperature in the first air heat exchanger
(63). This can further reduce the cooling capacity required in the
cooling heat exchanger (61), and the heating capacity required in
the heating section (55), and can further reduce the energy
consumption of the dehumidification system.
[0044] In the sixth aspect of the invention, the air and the
heating medium flow in the opposite directions in the second air
heat exchanger (64) to exchange heat therebetween.
[0045] Thus, the air can be heated more effectively in the second
air heat exchanger (64), and an amount of the cold collected from
the air in the second air heat exchanger (64) is increased.
Therefore, the air is cooled more effectively in the first air heat
exchanger (63).
[0046] In the seventh aspect of the invention, the second action of
feeding the air to sequentially flow through the cooling heat
exchanger (61) and the auxiliary heat exchanger (62), and
simultaneously feeding the heating medium to sequentially flow
through the auxiliary heat exchanger (62) and the cooling heat
exchanger (61) is performed. Thus, different from the first action,
the air can be cooled in both of the cooling heat exchanger (61)
and the auxiliary heat exchanger (62). Therefore, the air can be
dehumidified more effectively in the second action than in the
first action. Even when the temperature and humidity of the target
air are high, the air can reliably be dehumidified by performing
the second action.
[0047] In the eighth aspect of the invention, the flow rate of the
heating medium sent to the branch passage (66) is regulated to
suitably regulate the cooling capacity required in the first air
heat exchanger (63). Thus, the dehumidification system can be
operated in accordance with the humidity and temperature of the
target air. Since the auxiliary cooling unit (95) reduces the
temperature of the heating medium, the air can be
cooled/dehumidified also in the second air heat exchanger (64).
[0048] In the ninth aspect of the invention, the flow rate of the
heating medium flowing through the first air heat exchanger (63),
and the flow rate of the heating medium flowing through the second
air heat exchanger (64) can separately be regulated. Thus, the
cooling capacity required to cool the air in the first air heat
exchanger (63), and the heating capacity required to heat the air
in the second air heat exchanger (64) can separately be changed.
Therefore, the operation can be optimized in accordance with
operating conditions.
[0049] In the tenth aspect of the invention, the air discharged
from the inside of the room and the heating medium flowing through
the heating medium circuit (41) exchange heat in the sensible heat
exchanger (68). When the room is cooled, the cold of the air is
added to the heating medium flowing through the heating medium
circuit (41), thereby cooling the air more effectively in the first
air heat exchanger (63). For example, when the room is heated, the
heat of the air is added to the heating medium flowing through the
heating medium circuit (41), thereby heating the air more
effectively in the second air heat exchanger (64).
[0050] In the eleventh aspect of the invention, the flow rate of
the air flowing through the bypass passage (140) is regulated to
regulate the flow rate of the air flowing through the first air
heat exchanger (63) and the cooling heat exchanger (61). Thus, the
dehumidifying capacity required to dehumidify the air, and the
cooling capacity required to cool the air in the dehumidification
system can separately be regulated. This allows
cooling/dehumidifying operation optimized in accordance with the
operating conditions and needs associated with the operation.
BRIEF DESCRIPTION OF THE DRAWINGS
[0051] FIG. 1 is a schematic view illustrating a general structure
of a dehumidification system according to a first embodiment.
[0052] FIG. 2 is a schematic view illustrating heat exchangers in
an air conditioning unit.
[0053] FIG. 3 is a schematic view illustrating the heat exchangers
in the air conditioning unit together with a flow of a heating
medium during heat recovery operation.
[0054] FIG. 4 is a schematic view illustrating the heat exchangers
in the air conditioning unit together with a flow of the heating
medium during dehumidification-dominant operation.
[0055] FIG. 5 is a schematic view illustrating a general structure
of a dehumidification system according to a first alternative.
[0056] FIG. 6 is a schematic view illustrating heat exchangers in
an air conditioning unit according to the first alternative
together with a flow of a heating medium when a three-way valve is
set to a first state.
[0057] FIG. 7 is a schematic view illustrating the heat exchangers
in the air conditioning unit according to the first alternative
together with a flow of the heating medium when the three-way valve
is set to a second state.
[0058] FIG. 8 is a schematic view illustrating a general structure
of a dehumidification system according to a second alternative.
[0059] FIG. 9 is a schematic view illustrating a general structure
of a dehumidification system according to a third alternative.
[0060] FIG. 10 is a schematic view illustrating a general structure
of a dehumidification system according to a fourth alternative.
[0061] FIG. 11 is a schematic view illustrating a general structure
of a dehumidification system according to a fifth alternative.
[0062] FIG. 12 is a schematic view illustrating a general structure
of a dehumidification system according to a sixth alternative.
[0063] FIG. 13 is a schematic view illustrating a general structure
of a dehumidification system according to a seventh
alternative.
[0064] FIG. 14 is a schematic view illustrating a general structure
of an air conditioning unit of another dehumidification system
according to the seventh alternative.
DESCRIPTION OF EMBODIMENTS
[0065] Embodiments of the present invention will be described in
detail below with reference to the drawings.
[0066] [First Embodiment]
[0067] A dehumidification system according to a first embodiment
regulates room humidity and room temperature, and constitutes, for
example, an air conditioning system (10) applied to semiconductor
factories etc. As shown in FIG. 1, the air conditioning system (10)
according to the first embodiment is configured to take outside air
(OA), conditions humidity and temperature of the air, and supplies
the conditioned air as supply air (SA) to the inside of a room. The
air conditioning system (10) includes a chiller unit (20), and an
air conditioning unit (50). The air conditioning system (10)
further includes a refrigerant circuit (21), a radiation circuit
(31), and a heating medium circuit (41).
[0068] <Structure of Refrigerant Circuit>
[0069] The refrigerant circuit (21) is included in the chiller unit
(20). The refrigerant circuit (21) constitutes a closed circuit
filled with a refrigerant. A compressor (22), a radiator (23), an
expansion valve (24), and an evaporator (25) are connected to the
refrigerant circuit (21). The refrigerant circuit (21) performs a
vapor compression refrigeration cycle by circulating the
refrigerant.
[0070] The radiator (23) includes a first heat transfer pipe (23a)
connected to the refrigerant circuit (21), and a second heat
transfer pipe (23b) connected to the radiation circuit (31). Thus,
the refrigerant circuit (21) is connected to the radiation circuit
(31) through the radiator (23). In the radiator (23), the
refrigerant flowing through the first heat transfer pipe (23a) and
a heating medium flowing through the second heat transfer pipe
(23b) exchange heat. The evaporator (25) includes a first heat
transfer pipe (25a) connected to the refrigerant circuit (21), and
a second heat transfer pipe (25b) connected to the heating medium
circuit (41). Thus, the refrigerant circuit (21) is connected to
the heating medium circuit (41) through the evaporator (25). In the
evaporator (25), the refrigerant flowing through the first heat
transfer pipe (25a) and the heating medium flowing through the
second heat transfer pipe (25b) exchange heat.
[0071] <Structure of Radiation Circuit>
[0072] The radiation circuit (31) constitutes a closed circuit
filled with water as the heating medium. The radiator (23), a water
pump (32), and a cooling tower (33) are connected to the radiation
circuit (31). The water pump (32) transfers and circulates the
water in the radiation circuit (31). The cooling tower (33)
constitutes a cooling member for cooling the water circulating in
the radiation circuit (31). An arrow shown near the water pump (32)
in the drawings indicates a direction of the water circulated in
the radiation circuit (31).
[0073] <Structure of Circulation Circuit>
[0074] The heating medium circuit (41) constitutes a closed circuit
filled with water as the heating medium. The evaporator (25), a
chiller pump (42), and a cooling heat exchanger (61) are connected
to the heating medium circuit (41). The evaporator (25) constitutes
a heating medium cooling section for cooling the heating medium
circulating in the heating medium circuit (41). The chiller pump
(42) constitutes a heating medium transfer mechanism for
transferring and circulating the water in the heating medium
circuit (41). Details of the cooling heat exchanger (61) will be
described later. An arrow shown near the chiller pump (42) in the
drawings indicates a direction of the water flowing in the heating
medium circuit (41).
[0075] A water bypass pipe (43) is connected to the heating medium
circuit (41). An end of the water bypass pipe (43) is connected
between the chiller pump (42) and the cooling heat exchanger (61).
The other end of the water bypass pipe (43) is connected between
the cooling heat exchanger (61) and the evaporator (25). A
motor-operated bypass valve (44) is provided in the water bypass
pipe (43). The motor-operated bypass valve (44) constitutes a flow
rate control valve which can regulate the degree of opening of the
water bypass pipe (43). In FIG. 1 (and FIGS. 5, and 8-14), pipes
are partially omitted to schematically show how the pipes are
communicated with each other during a first action described in
detail later.
[0076] <Structure of Air Conditioning Unit>
[0077] The air conditioning unit (50) includes a casing (51) which
is in the shape of a horizontally oriented flat rectangular
parallelepiped. An air passage (52) through which air flows is
formed in the casing (51). An inlet end of the air passage (52) is
connected to an end of an inlet duct (53). The other end of the
inlet duct (53) is opened outside the room. An outlet end of the
air passage (52) is connected to an end of a supply duct (54). The
other end of the supply duct (54) is opened in a room (5).
[0078] The air passage (52) includes a first air heat exchanger
(63), the cooling heat exchanger (61), an auxiliary heat exchanger
(62), a second air heat exchanger (64), an electric heater (55), a
sprinkler (56), and a blower (57) sequentially arranged from
upstream to downstream in the air passage. The electric heater (55)
is provided downstream of the second air heat exchanger (64) to
constitute an air heating section for heating the air. The
sprinkler (56) constitutes a humidifying section which sprinkles
water in a tank (not shown) in the air through a nozzle. The blower
(57) constitutes an air transfer mechanism which transfers the air
in the air passage (52).
[0079] The cooling heat exchanger (61) described above constitutes
an air cooling section for cooling the air to a dew point
temperature or lower. As shown in FIGS. 2-4, the cooling heat
exchanger (61) includes a plurality of fins (61a), and a heat
transfer tube (61b) penetrating the fins (61a) to constitute a
so-called fin-and-tube heat exchanger. The cooling heat exchanger
(61) includes fin sets each containing five fins arranged in a
direction of air flow.
[0080] The cooling heat exchanger (61) includes an inlet (71a)
which is positioned in a downstream part of the air passage (52),
and through which water flows into the cooling heat exchanger (61),
and an outlet (71b) which is positioned in an upstream part of the
air passage (52), and through which water flows out of the cooling
heat exchanger (61). A first inlet pipe (71) and a first outlet
pipe (72) are connected to the inlet (71a) and the outlet (71b) of
the cooling heat exchanger (61), respectively.
[0081] Each of the inlet (71a) and the outlet (71b) of the cooling
heat exchanger (61) is divided into two or more branches by a flow
divider. The branches of the inlet (71a) are connected to inlet
ends of a plurality of paths (61c, 61c, . . . ) in the cooling heat
exchanger (61), and the branches of the outlet (71b) are connected
to outlet ends of a plurality of paths (61c, 61c, . . . ) in the
cooling heat exchanger (61). The paths (61c, 61c, . . . ) are
aligned in the vertical direction to be parallel with each other,
and extend between the inlet (71a) and the outlet (71b). The paths
(61c, 61c, . . . ) constitute an intermediate passage formed
between the inlet (71a) and the outlet (71b).
[0082] The auxiliary heat exchanger (62) is provided downstream of
the cooling heat exchanger (61). The auxiliary heat exchanger (62)
includes a plurality of fins (62a), and a heat transfer tube (62b)
penetrating the fins (62a) to constitute the so-called fin-and-tube
heat exchanger. The auxiliary heat exchanger (62) includes fin sets
each containing three fins arranged in the direction of air flow.
Specifically, the number of the fins in each fin set of the
auxiliary heat exchanger (62) is smaller than the number of the
fins in each fin set of the cooling heat exchanger (61).
[0083] The auxiliary heat exchanger (62) includes an inlet (72a)
which is positioned in the downstream part of the air passage (52),
and through which water flows into the auxiliary heat exchanger
(62), and an outlet (72b) which is positioned in the upstream part
of the air passage (52), and through which water flows out of the
auxiliary heat exchanger (62). A second inlet pipe (73) and a
second outlet pipe (74) are connected to the inlet (72a) and the
outlet (72b) of the auxiliary heat exchanger (62),
respectively.
[0084] Like in the cooling heat exchanger (61) described above, the
inlet (72a) and the outlet (72b) of the auxiliary heat exchanger
(62) are branched, and a plurality of paths (62c, 62c, . . . ) are
formed as an intermediate passage between the inlet (72a) and the
outlet (72b).
[0085] The cooling heat exchanger (61) and the auxiliary heat
exchanger (62) are coupled through a first coupling pipe (75) and a
second coupling pipe (76). The inlet (71a) of the cooling heat
exchanger (61) and the outlet (72b) of the auxiliary heat exchanger
(62) communicate with each other through the first coupling pipe
(75). The outlet (71b) of the cooling heat exchanger (61) and the
inlet (72a) of the auxiliary heat exchanger (62) communicate with
each other through the second coupling pipe (76).
[0086] The first inlet pipe (71) has a first valve (81), the first
outlet pipe (72) has a second valve (82), the second inlet pipe
(73) has a third valve (83), the second outlet pipe (74) has a
fourth valve (84), the first coupling pipe (75) has a fifth valve
(85), and the second coupling pipe (76) has a sixth valve (86). The
valves (81-86) are configured to open or close the corresponding
passages. Each of the valves (81-86) of the present embodiment
constitutes a flow rate control valve which can regulate the degree
of opening of the corresponding passage.
[0087] The air conditioning system (10) includes a circulation
circuit (60) in which water as the heating medium circulates. The
first air heat exchanger (63) and the second air heat exchanger
(64) are connected in series to the circulation circuit (60).
[0088] The first air heat exchanger (63) is provided upstream of
the cooling heat exchanger (61) in the air passage (52). The first
air heat exchanger (63) includes a plurality of fins (63a), and a
heat transfer tube (63b) penetrating the fins (63a) to constitute
the so-called fin-and-tube heat exchanger. The first air heat
exchanger (63) includes fin sets each containing two fins arranged
in the direction of the air flow.
[0089] The first air heat exchanger (63) includes an inlet (73a)
which is positioned in the downstream part of the air passage (52),
and through which water flows into the first air heat exchanger
(63), and an outlet (73b) which is positioned in the upstream part
of the air passage (52), and through which water flows out of the
first air heat exchanger (63). An end of a third coupling pipe
(77), and an end of a fourth coupling pipe (78) are connected to
the outlet (73b) and the inlet (73a) of the first air heat
exchanger (63), respectively.
[0090] Like in the cooling heat exchanger (61) described above, the
inlet (73a) and the outlet (73b) of the first air heat exchanger
(63) are branched, and a plurality of paths (63c, 63c, . . . ) are
formed as an intermediate passage between the inlet (73a) and the
outlet (73b).
[0091] The second air heat exchanger (64) is provided downstream of
the auxiliary heat exchanger (62) in the air passage (52). The
second air heat exchanger (64) includes a plurality of fins (64a),
and a heat transfer tube (64b) penetrating the fins (64a) to
constitute the so-called fin-and-tube heat exchanger. The second
air heat exchanger (64) includes fin sets each containing three
fins arranged in the direction of the air flow.
[0092] The second air heat exchanger (64) includes an inlet (74a)
which is positioned in the downstream part of the air passage (52),
and through which water flows into the second air heat exchanger
(64), and an outlet (74b) which is positioned in the upstream part
of the air passage (52), and through which water flows out of the
second air heat exchanger (64). The other end of the third coupling
pipe (77) and the other end of the fourth coupling pipe (78) are
connected to the inlet (74a) and the outlet (74b) of the second air
heat exchanger (64), respectively.
[0093] Like in the cooling heat exchanger (61) described above, the
inlet (74a) and the outlet (74b) of the second air heat exchanger
(64) are branched, and a plurality of paths (64c, 64c, . . . ) are
formed as an intermediate passage between the inlet (74a) and the
outlet (74b).
[0094] As described above, the first air heat exchanger (63), the
third coupling pipe (77), the second air heat exchanger (64), and
the fourth coupling pipe (78) are sequentially connected to
constitute the closed circulation circuit (60). The third coupling
pipe (77) includes a circulating pump (65) for transferring water
in the circulation circuit (60).
[0095] <Structure of Controller>
[0096] The air conditioning system (10) includes a controller (100)
as a control section. A signal related to an operating state of the
air conditioning system (10) is input to the controller (100).
Based on the input signal, the controller (100) controls cooling
capacity of the chiller unit (20), an amount of water circulating
in the water pump (32), the chiller pump (42), and the circulating
pump (65), heating capacity of the electric heater (55), an amount
of water sprinkled by the sprinkler (56), the degree of opening of
the motor-operated bypass valve (44), etc. The controller (100)
controls the degree of opening of the first to six valves (81-86)
in response to switching between "heat recovery operation" and
"dehumidification-dominant operation" described in detail
later.
Working Mechanism
[0097] [Heat Recovery Operation]
[0098] Heat recovery operation is dehumidifying operation which
places importance on energy conservation than dehumidifying
capacity. The heat recovery operation is carried out, for example,
when temperature and humidity in the room are relatively low, i.e.,
in winter etc. A dehumidification load in the room (e.g., a
difference between target room humidity and current room humidity)
may be detected to automatically perform the heat recovery
operation when the dehumidification load is relatively low.
[0099] In the heat recovery operation, the compressor (22), the
water pump (32), the chiller pump (42), and the blower (57) of the
chiller unit (20) are driven. Basically, the electric heater (55)
is turned on, and the sprinkling of the sprinkler (56) is stopped
during the heat recovery operation. The controller (100) opens the
first valve (81), the fourth valve (84), and the sixth valve (86),
and closes the second valve (82), the third valve (83), and the
fifth valve (85) (see FIG. 3).
[0100] In the heat recovery operation, the refrigerant circuit (21)
performs a refrigeration cycle. Specifically, the refrigerant
compressed in the compressor (22) flows through the radiator (23).
In the radiator (23), the refrigerant flowing through the first
heat transfer pipe (23a) dissipates heat to water flowing through
the second heat transfer pipe (23b), and is condensed. The water
heated by the second heat transfer pipe (23b) of the radiator (23)
dissipates heat to the outside air in the cooling tower (33). The
refrigerant condensed in the radiator (23) is decompressed by the
expansion valve (24) as a pressure reducing mechanism, and then
flows through the evaporator (25). In the evaporator (25), the
refrigerant flowing through the first heat transfer pipe (25a)
absorbs heat from water flowing through the second heat transfer
pipe (25b), and is evaporated. The refrigerant evaporated in the
evaporator (25) is sucked into the compressor (22), and is
compressed.
[0101] The water cooled in the second heat transfer pipe (25b) of
the evaporator (25) passes through the chiller pump (42), and is
transferred to the casing (51) of the air conditioning unit (50).
In the heat recovery operation, water passing through the inlet of
the heating medium circuit (41) flows through the first inlet pipe
(71) to enter the cooling heat exchanger (61). The water is
diverted into the plurality of paths (61c, 61c, . . . ), and flows
through the paths (61c, 61c, . . . ) to the upstream of the air
flow. The water that passed through the paths (61c, 61c, . . . ) of
the cooling heat exchanger (61) flows into the auxiliary heat
exchanger (62) through the second coupling pipe (76). The water is
diverted into the plurality of paths (62c, 62c, . . . ), and flows
through the paths (62c, 62c, . . . ) to the upstream of the air
flow. The water that passed through the paths (62c, 62c, . . . ) of
the auxiliary heat exchanger (62) is returned to the evaporator
(25) of the heating medium circuit (41) through the second outlet
pipe (74), and is cooled in the evaporator (25).
[0102] In the heat recovery operation described above, a first
action of sending the water which is cooled in the evaporator (25)
of the heating medium circuit (41), and sequentially flowed through
the cooling heat exchanger (61) and the auxiliary heat exchanger
(62) to the evaporator (25) is performed.
[0103] In the circulation circuit (60), water transferred by the
circulating pump (65) flows into the second air heat exchanger (64)
through the third coupling valve (77). The water is diverted into
the plurality of paths (64c, 64c, . . . ), and flows through the
paths (64c, 64c, . . . ) to the upstream of the air flow. The water
that passed through the paths (64c, 64 , . . . ) of the second air
heat exchanger (64) is sent to the fourth coupling valve (78), and
flows into the first air heat exchanger (63). The water is diverted
into the plurality of paths (63c, 63c, . . . ), and flows through
the paths (63c, 63c, . . . ) to the upstream of the air flow. The
water that passed through the paths (63c, 63c, . . . ) of the first
air heat exchanger (63) is sent to the third coupling valve
(77).
[0104] In the air conditioning unit (50), the outside air (OA)
taken into the inlet duct (53) from the outside of the room flows
through the air passage (52) in the casing (51). The air first
passes through the first air heat exchanger (63). In the first air
heat exchanger (63), the water and the air flowing in substantially
opposite directions exchange heat therebetween. Specifically, in
the first air heat exchanger (63), for example, the air of about
30.degree. C. and the water of about 17.degree. C. exchange heat,
thereby cooling the air of 30.degree. C. to about 25.degree. C. The
water flowing out of the first air heat exchanger (63) is heated
to, e.g., about 20.degree. C.
[0105] The air cooled in the first air heat exchanger (63) passes
through the cooling heat exchanger (61). In the cooling heat
exchanger (61), the water and the air flowing in substantially
opposite directions exchange heat therebetween. As a result, the
air is cooled to a dew point temperature or lower (e.g., about
10.degree. C.), and is dehumidified. The water flowing out of the
cooling heat exchanger (61) is heated to, e.g., about 15.degree.
C.
[0106] The air cooled/dehumidified in the cooling heat exchanger
(61) passes through the auxiliary heat exchanger (62). In the
auxiliary heat exchanger (62), for example, the air of about
10.degree. C. and the water of about 15.degree. C. exchange heat,
thereby heating the air of about 10.degree. C. to about 12.degree.
C.
[0107] The air heated in the auxiliary heat exchanger (62) flows
through the second air heat exchanger (64). In the second air heat
exchanger (64), for example, the air of about 12.degree. C. and the
water of about 20.degree. C. exchange heat, thereby heating the air
to about 15.degree. C., and cooling the water to about 17.degree.
C.
[0108] The air heated in the second air heat exchanger (64) is
further heated by the electric heater (55). When the temperature of
the air heated in the second air heat exchanger (64) exceeds a
target room temperature, the electric heater (55) may be turned
off
[0109] The air dehumidified in this way is supplied to the room (5)
as supply air (SA) through the supply duct (54).
[0110] [Dehumidification-dominant Operation]
[0111] Dehumidification-dominant operation is dehumidifying
operation which places importance on dehumidifying capacity than
energy conservation. The dehumidification-dominant operation is
carried out, for example, when temperature and humidity in the room
are relatively high, i.e., in summer etc. A dehumidification load
in the room may be detected to automatically perform the
dehumidification-dominant operation when the dehumidification load
is relatively high.
[0112] In the dehumidification-dominant operation, the compressor
(22), the water pump (32), the chiller pump (42), and the blower
(57) of the chiller unit (20) are driven. Basically, the electric
heater (55) is turned on, and the sprinkling of the sprinkler (56)
is stopped during the dehumidification-dominant operation. The
controller (100) opens the second valve (82), the third valve (83),
and the fifth valve (85), and closes the first valve (81), the
fourth valve (84), and the sixth valve (86) (see FIG. 4).
[0113] In the dehumidification-dominant operation, the refrigerant
circuit (21) performs the refrigeration cycle in the same manner as
in the heat recovery operation. Water cooled in the second heat
transfer pipe (25b) of the evaporator (25) passes through the
chiller pump (42), and is transferred to the casing (51) of the air
conditioning unit (50).
[0114] In the dehumidification-dominant operation, water passing
through the inlet of the heating medium circuit (41) flows through
the second inlet pipe (73) to enter the auxiliary heat exchanger
(62). The water is diverted into the plurality of paths (62c, 62c,
. . . ), and flows through the paths (62c, 62c, . . . ) to the
upstream of the air flow. The water that passed through the paths
(62c, 62c, . . . ) of the auxiliary heat exchanger (62) flows into
the cooling heat exchanger (61) through the first coupling pipe
(75). The water is diverted into the plurality of paths (61c, 61c,
. . . ), and flows through the paths (61c, 61c, . . . ) to the
upstream of the air flow. The water that passed through the paths
(61c, 61c, . . . ) of the cooling heat exchanger (61) is returned
to the evaporator (25) of the heating medium circuit (41) through
the first outlet pipe (72), and is cooled in the evaporator
(25).
[0115] In the dehumidification-dominant operation described above,
a second action of sending the water which is cooled in the
evaporator (25) of the heating medium circuit (41), and
sequentially flowed through the auxiliary heat exchanger (62) and
the cooling heat exchanger (61) to the evaporator (25) is
performed.
[0116] In the air conditioning unit (50), the outside air (OA)
taken into the inlet duct (53) from the outside of the room flows
through the air passage (52) in the casing (51). The air passes
through the cooling heat exchanger (61), and then passes through
the auxiliary heat exchanger (62). The water in the heating medium
circuit (41) flows through the paths (62c, 62c, . . . ) of the
auxiliary heat exchanger (62), and then flows through the paths
(61c, 61c, . . . ) of the cooling heat exchanger (61) as described
above. Thus, in the air passage (52), the air and the heating
medium (water) flow substantially in the opposite directions in the
two air heat exchangers (61, 62) to exchange heat therebetween.
Specifically, the two air heat exchangers (61, 62) substantially
function as a single convection heat exchanger in the
dehumidification-dominant operation.
[0117] Thus, when the air cooled in the first air heat exchanger
(63) passes through the cooling heat exchanger (61) and the
auxiliary heat exchanger (62), the air is cooled in both of the
heat exchangers (61, 62). As a result, the air which passed through
the auxiliary heat exchanger (62) is more cooled in the
dehumidification-dominant operation than in the heat recovery
operation described above. This improves the dehumidifying
capacity.
[0118] The air cooled/dehumidified in the two heat exchangers (61,
62) is heated by the second air heat exchanger (64) and the
electric heater (55). The air dehumidified as described above is
supplied to the room (5) as the supply air (SA) through the supply
duct (54).
Advantages of First Embodiment
[0119] In the above embodiment, the air which is not
cooled/dehumidified yet in the cooling heat exchanger (61) is
cooled in advance in the first air heat exchanger (63). This can
reduce the cooling capacity required in the cooling heat exchanger
(61), and can reduce, for example, the amount of water flowing in
the heating medium circuit (41), or the cooling capacity required
in the evaporator (25) (i.e., power of the compressor). This can
reduce energy consumption of the air conditioning system (10).
[0120] In the second air heat exchanger (64), heat collected from
the air in the first air heat exchanger (63) is used to heat the
air. Thus, the dehumidifying capacity can be improved, and cold
collected from the air can be used to cool the air again in the
first air heat exchanger (63). Further, input to the electric
heater (55) can be reduced.
[0121] In the auxiliary heat exchanger (62) during the heat
recovery operation, heat collected from the air in the cooling heat
exchanger (61) is used to heat the air. This can further improve
the dehumidifying capacity, and can reduce the temperature of water
sent to the evaporator (25) of the heating medium circuit (41).
Thus, the cooling capacity required in the evaporator (25) can
further be reduced, and energy consumption can further be reduced.
In addition, the input to the electric heater (55) can be
reduced.
[0122] In the cooling heat exchanger (61) during the heat recovery
operation, the air and the water flowing in the opposite directions
exchange heat therebetween. Thus, the air flowing out of the
cooling heat exchanger (61) can be cooled to a temperature close to
the temperature of the water introduced in the cooling heat
exchanger (61), thereby cooling/dehumidifying the air more
effectively in the cooling heat exchanger (61). On the other hand,
the water flowing out of the cooling heat exchanger (61) can be
heated to a temperature close to the temperature of the air flowing
into the cooling heat exchanger (61). Thus, the air can be heated
more effectively in the auxiliary heat exchanger (62), thereby
further reducing the heating capacity required in the electric
heater (55).
[0123] In the auxiliary heat exchanger (62) during the heat
recovery operation, the air and water flowing in the opposite
directions exchange heat therebetween. This can significantly heat
the air, and significantly cool the water. Therefore, the cooling
capacity required in the evaporator (25) can further be reduced,
and the heating capacity required in the electric heater (55) can
further be reduced.
[0124] The first air heat exchanger (63) which functions as the
so-called convection heat exchanger can effectively cool the air.
Since the temperature of the water flowing out of the first air
heat exchanger (63) is relatively high, the second air heat
exchanger (64) can effectively heat the air. Further, the second
air heat exchanger (64) which also functions as the so-called
convection heat exchanger can effectively heat the air. Since the
temperature of the water flowing out of the second air heat
exchanger (64) is relatively low, the first air heat exchanger (63)
can effectively cool the air.
[0125] In the above embodiment, the air sequentially flows through
the cooling heat exchanger (61) and the auxiliary heat exchanger
(62), and the water sequentially flows through the auxiliary heat
exchanger (62) and the cooling heat exchanger (61) in the
dehumidification-dominant operation. Thus, the air can be cooled in
both of the cooling heat exchanger (61) and the auxiliary heat
exchanger (62), and the operation can be performed with priority
given to the dehumidification of the air. Even when the outside
humidity or temperature is significantly high, latent heat of the
air can reliably be handled to supply the air to the inside of the
room.
[0126] In the above embodiment, the passages in the heating medium
circuit (41) through which the water flows are changed in the
dehumidification-dominant operation in such a manner that both of
the cooling heat exchanger (61) and the auxiliary heat exchanger
(62) function as the so-called convection heat exchangers. Thus, in
the dehumidification-dominant operation, the two heat exchangers
(61, 62) substantially function as a single convection air heat
exchanger. Therefore, the air can be cooled and dehumidified more
effectively.
[0127] [Alternative of First Embodiment]
[0128] The first embodiment described above may be modified in the
following manner. In the following description, the same components
as those of the first embodiment will not be described in
detail.
[0129] <First Alternative>
[0130] An air conditioning system (10) of a first alternative shown
in FIGS. 5-7 includes a branch passage (66) into which part of the
water circulating in the circulation circuit (60) is diverted, and
an auxiliary cooling unit (90) for cooling the water flowing
through the branch passage (66).
[0131] The auxiliary cooling unit (90) includes a refrigerant
circuit (91) which is filled with a refrigerant, and performs a
vapor compression refrigeration cycle. A compressor (92), a
radiator (93), an expansion valve (94), and an evaporator (95) are
sequentially connected to the refrigerant circuit (91) of the
auxiliary cooling unit (90). The refrigerant circuit (91) is
connected to the branch passage (66) through the evaporator (95).
The evaporator (95) constitutes an auxiliary cooling section which
cools the heating medium flowing through the branch passage (66) by
the refrigerant.
[0132] The branch passage (66) includes a first branch pipe (66a)
closer to an inlet of the evaporator (95), and a second branch pipe
(66b) closer to an outlet of the evaporator (95). An inlet end of
the first branch pipe (66a) is connected to an upstream end of the
third coupling valve (77). A three-way valve (97) is provided at a
junction between the first branch pipe (66a) and the third coupling
valve (77). The three-way valve (97) is configured to regulate the
amounts of the heating medium sent to the third coupling valve (77)
and the first branch pipe (66a) from the outlet (73b) of the first
air heat exchanger (63). Specifically, the three-way valve (97) can
be switched between a state where the entire heating medium flowing
out of the outlet (73b) of the first air heat exchanger (63) is
sent to the third coupling valve (77) (a state shown in FIG. 6),
and a state where the heating medium flowing out of the outlet
(73b) of the first air heat exchanger (63) is diverted to the third
coupling valve (77) and the first branch pipe (66a) (a state shown
in FIG. 7). The three-way valve (97) can be switched to a state
where the entire heating medium flowing out of the outlet (73b) of
the first air heat exchanger (63) is sent to the first branch pipe
(66a). In this way, the three-way valve (97) constitutes a diverted
flow control mechanism which regulates a flow rate of the heating
medium flowing through the branch passage (66).
[0133] In the dehumidifying operation performed by the air
conditioning system (10) of the first alternative, the controller
(100) controls the degree of opening of the three-way valve (97)
based on temperature and humidity of the target air, set room
temperature (target temperature) and set room humidity (target
humidity).
[0134] Specifically, for example, in the normal dehumidifying
operation, the controller (100) controls the three-way valve (97)
in the state shown in FIG. 6. Thus, the entire heating medium
flowing out of the outlet (73b) of the first air heat exchanger
(63) is not sent to the branch passage (66), but flows through the
third coupling valve (77). Thus, in this case, the dehumidifying
operation is performed in the same manner as described in the first
embodiment.
[0135] For example, when the dehumidifying operation is performed
when the humidity or temperature of the target air is excessively
high, or the set room temperature or humidity is excessively low,
the controller (100) controls the three-way valve (97) in the state
shown in FIG. 7. Thus, part of the heating medium flowing out of
the outlet (73b) of the first air heat exchanger (63) is sent to
the branch passage (66). The heating medium flowing through the
branch passage (66) is cooled in the evaporator (95) of the
auxiliary cooling unit (90), and is then sent to the second air
heat exchanger (64). Thus, in this operation, the air can be
cooled/dehumidified also in the second air heat exchanger (64).
Therefore, even when the latent heat load is high, the
dehumidification can be performed to a preferred degree.
[0136] <Second Alternative>
[0137] In an air conditioning system (10) of a second alternative
shown in FIG. 8, a refrigerant circuit (130) is used as a
circulation circuit in place of the circulation circuit (60) of the
first embodiment. The refrigerant circuit (130) is configured to
perform a vapor compression refrigeration cycle by circulating a
refrigerant as a heating medium.
[0138] A compressor (131), a second air heat exchanger (64), an
expansion valve (132), and a first air heat exchanger (63) are
sequentially connected to the refrigerant circuit (130). In the
second alternative, the second air heat exchanger (64) functions as
a radiator (a condenser), and the first air heat exchanger (63)
functions as an evaporator.
[0139] Specifically, when the air flowing through the air passage
(52) passes through the first air heat exchanger (63), the
refrigerant absorbs heat from the air to evaporate, thereby
precooling the air. When the air cooled/dehumidified in the cooling
heat exchanger (61) passes through the second air heat exchanger
(64), the refrigerant dissipates heat to the air to heat the air.
In the second alternative, the heat collected from the air to the
refrigerant in the first air heat exchanger (63) is used to heat
the air in the second air heat exchanger (64). This can reduce
energy consumption of the air conditioning system (10).
[0140] <Third Alternative>
[0141] A circulation circuit (41) of a third alternative shown in
FIG. 9 includes a first water tank (35), a second water tank (36),
and an auxiliary pump (37).
[0142] The first water tank (35) and the second water tank (36)
constitute a heating medium container for temporarily containing
water as a heating medium. The first water tank (35) is provided in
the third coupling valve (77) near an inlet end of the circulating
pump (65). The auxiliary pump (37) is provided in the fourth
coupling valve (78). The second water tank (36) is provided in the
fourth coupling valve (78) near an inlet end of the auxiliary pump
(37). The circulating pump (65) and the auxiliary pump (37) are
centrifugal pumps, for example, and an amount of the heating medium
transferred by each pump is variable by changing the number or
revolutions of a motor.
[0143] The first water tank (35), the second water tank (36), the
auxiliary pump (37), and the circulating pump (65) constitute a
flow rate control mechanism which separately regulates the flow
rate of the water flowing through the first air heat exchanger
(63), and the flow rate of the water flowing through the second air
heat exchanger (64).
[0144] The controller (100) of the third alternative includes a
pump control section. The pump control section is configured to
control the numbers of revolutions of motors of the circulating
pump (65) and the auxiliary pump (37) (i.e., the flow rate of the
heating medium).
[0145] Specifically, the pump control section regulates the flow
rates of the heating medium transferred by the circulating pump
(65) and the auxiliary pump (37) differently between daytime and
nighttime.
[0146] In the daytime, the flow rate of water transferred by the
auxiliary pump (37) is controlled to be higher than the flow rate
of water transferred by the circulating pump (65) (first pump
control operation). Specifically, in the first pump control
operation, the flow rate of water flowing through the first air
heat exchanger (63) is higher than the flow rate of water flowing
through the second air heat exchanger (64). In the daytime, the
temperature of the outside air (OA) is higher than that in the
nighttime. With the flow rate of the water flowing through the
first air heat exchanger (63) controlled to be relatively high, the
outside air can sufficiently be cooled and dehumidified. When the
flow rate of the water flowing through the second air heat
exchanger (64) is lower than the flow rate of the water flowing
through the first air heat exchanger (63), the amount of water
which is heated in the first air heat exchanger (63), and is
contained in the first water tank (35) increases.
[0147] In the nighttime, the flow rate of the water transferred by
the circulating pump (65) is controlled to be higher than the flow
rate of the water transferred by the auxiliary pump (37) (second
pump control operation). Specifically, in the second pump control
operation, the flow rate of the water flowing through the second
air heat exchanger (64) is higher than the flow rate of the water
flowing through the first air heat exchanger (63). In the
nighttime, the temperature of the outside air (OA) is lower than
that in the daytime. With the flow rate of the water flowing
through the second air heat exchanger (64) controlled to be
relatively low, excessive cooling of the outside air can be
avoided. In the nighttime, a large amount of water of relatively
high temperature accumulated in the first water tank (35) in the
daytime flows through the second air heat exchanger (64). Thus,
heat exchange between the water and the air is accelerated in the
second air heat exchanger (64), i.e., heating of the air and
cooling of the water are accelerated.
[0148] When the flow rate of the water flowing through the first
air heat exchanger (63) is lower than the flow rate of the water
flowing through the second air heat exchanger (64), the amount of
water which is cooled in the second air heat exchanger (64), and is
contained in the second water tank (36) increases.
[0149] Then, when the first pump control operation is performed
again in the daytime, the flow rate of the water transferred by the
auxiliary pump (37) is higher than the flow rate of the water
transferred by the circulating pump (65) as described above. Thus,
a large amount of water of relatively low temperature accumulated
in the second water tank (36) in the nighttime flows through the
first air heat exchanger (63). Therefore, heat exchange between the
water and the air is accelerated in the first air heat exchanger
(63), i.e., cooling of the air and heating of the water are
accelerated.
[0150] In the third alternative described above, the flow rates of
water transferred by the circulating pump (65) and the auxiliary
pump (37) are changed between the daytime and nighttime, and the
water is accumulated in the water tanks (35, 36). Thus, the cold
collected in the nighttime can be used to cool the air in the
daytime, and the heat collected in the daytime can be used to heat
the air in the nighttime. This can further reduce energy
consumption of the air conditioning system (10) in the heat
recovery operation.
[0151] In the third alternative, the daytime operation and the
nighttime operation may be switched, for example, using a timer
etc., or based on the outside temperature (for example, the first
pump control operation is performed when the outside temperature
detected by a sensor is higher than a predetermined value, and the
second pump control operation is performed when the outside
temperature detected by the sensor is lower than the predetermined
value), etc.
[0152] <Fourth Alternative>
[0153] An air conditioning system (10) of a fourth alternative
shown in FIG. 10 includes an internal heat exchanger (28) in which
water in the radiation circuit (31) and water in the circulation
circuit (60) exchange heat therebetween. Specifically, a diverting
pipe (26) for diverting part of the water in the radiation circuit
(31) is connected to the radiation circuit (31). A flow rate
control valve (27) capable of regulating its degree of opening is
provided in the diverting pipe (26). The internal heat exchanger
(28) is configured to allow heat exchange between water circulating
in the circulation circuit (60) and water diverted to the diverting
pipe (26) to cool the water in the diverting pipe (26) by the water
in the circulation circuit (60).
[0154] Specifically, in the above-described dehumidifying
operation, when the flow rate control valve (27) opens the
diverting pipe (26) at a predetermined degree of opening, the water
in the radiation circuit (31) is diverted to the diverting pipe
(26). The diverted water exchanges heat with the water of
relatively low temperature flowing through the circulation circuit
(60), and is cooled in the internal heat exchanger (28). Thus, in
the fourth alternative, for example, when the outside temperature
is low, cold of the water in the circulation circuit (60) can be
used to cool the water in the radiation circuit (31).
[0155] <Fifth Alternative>
[0156] An air conditioning system (10) of a fifth alternative shown
in FIG. 11 includes an exhaust duct (59), and a duct heat exchanger
(68). An end of the exhaust duct (59) is connected to the room (5),
and the other end is opened to the outside air. Thus, the exhaust
duct (59) forms an exhaust passage through which the air in the
room (5), which is target air of the air conditioning system (10),
is discharged outside as exhaust air (EA). The duct heat exchanger
(68) is arranged inside of the exhaust duct (59) to occupy the
whole cross sectional area of the exhaust duct (59). The duct heat
exchanger (68) is connected to a pipe between the first air heat
exchanger (63) and the second air heat exchanger (64) (the third
coupling valve (77)). Specifically, the duct heat exchanger (68)
constitutes a sensible heat exchanger in which the water sent from
the first air heat exchanger (63) to the second air heat exchanger
(64) and the air sent from the room (5) to the outside exchange
heat.
[0157] According to the fifth alternative, for example, in summer,
cold of the room air can be added to the water in the circulation
circuit (60). Thus, in the air conditioning unit (50), the cold
collected to the circulation circuit (60) can be used to cool the
air in the first air heat exchanger (63). For example, in winter,
heat of the room air can be added to the water in the circulation
circuit (60). Thus, in the air conditioning unit (50), the heat
collected to the circulation circuit (60) can be used to heat the
air in the second air heat exchanger (64).
[0158] <Sixth Alternative>
[0159] An air conditioning unit (50) of an air conditioning system
(10) of a sixth alternative shown in FIG. 12 is configured to send
supply air (SA) to three rooms (a first room (5a), a second room
(5b), and a third room (5c)). Specifically, an outlet end of the
supply duct (54) of the air conditioning unit (50) is branched into
three air supply parts (a first air supply part (54a), a second air
supply part (54b), and a third air supply part (54c)). An outlet
end of the first air supply part (54a) is opened in the first room
(5a), an outlet end of the second air supply part (54b) is opened
in the second room (5b), and an outlet end of the third air supply
part (54c) is opened in the third room (5c). An exhaust duct (59a)
is connected to the first room (5a).
[0160] The air conditioning system (10) of the sixth alternative
includes first and second auxiliary air conditioning units (120,
130). The first auxiliary air conditioning unit (120) is concerned
with the second room (5b), and the second auxiliary air
conditioning unit (130) is concerned with the third room (5c).
[0161] Each of the auxiliary air conditioning units (120, 130)
includes a casing (121, 131) which forms an air passage (122, 132),
an inlet duct (123, 133) which connects an inlet end of the air
passage (122, 132) and a room (5b, 5c), and a supply duct (124,
134) which connects an outlet end of the air passage (122, 132) and
the room (5b, 5c).
[0162] In the air passage (122, 132) of each of the auxiliary air
conditioning units (122, 132), an air heat exchanger (125, 135), an
electric heater (126, 136), a sprinkler (127, 137), and a blower
(128, 138) are sequentially arranged in a direction from upstream
to downstream of the air passage. Heat transfer pipes of the air
heat exchangers (125, 135) are filled with a heating medium such as
water etc.
[0163] In the air conditioning system (10), the air conditioning
unit (50) is operated in association with each of the auxiliary air
conditioning units (122, 132). The air cooled/dehumidified in the
air conditioning unit (50) is divided into the three air supply
parts (54a, 54b, 54c) from the supply duct (54), and is supplied to
the rooms (54a, 54b, 54c).
[0164] In each of the auxiliary air conditioning units (120, 130),
the room air (RA) in each of the room (5b, 5c) is introduced into
the air passage (122, 132) through the inlet duct (123, 133). The
air is cooled/dehumidified by the heating medium flowing through
the air heat exchanger (125, 135), and is then heated by the
electric heater (126, 136). The air dehumidified in this manner is
supplied to the rooms (5b, 5c) as supply air (SA).
[0165] <Seventh Alternative>
[0166] An air conditioning system (10) of a seventh alternative
shown in FIG. 13 includes a branch duct (140), and an air flow
control valve (141). An inlet end of the branch duct (140) is
connected to the inlet duct (53). An outlet end of the branch duct
(140) is opened between the second air heat exchanger (64) and the
electric heater (55) in the air passage (52). Specifically, the
branch duct (140) constitutes a bypass passage which transfers the
air in the air passage (52) upstream of the first air heat
exchanger (63) to the downstream of the second air heat exchanger
(64). The air flow control valve (141) constitutes a bypass flow
control mechanism which regulates the flow rate of the air flowing
through the branch duct (140). The bypass flow control mechanism
may be other mechanisms, such as a damper etc.
[0167] In the seventh alternative, the controller (100) controls
the air flow control valve (141) based on operating conditions,
thereby allowing operation suitable for a target latent or sensible
heat load.
[0168] Specifically, for example, when the target latent heat load
is high, the degree of opening of the air flow control valve (141)
is reduced to reduce the flow rate of the air flowing through the
branch duct (140). Thus, the flow rate of the air passing through
the first air heat exchanger (63) and the cooling heat exchanger
(61) is relatively high, and the air can be cooled/dehumidified to
sufficiently handle the latent heat load.
[0169] For example, when the target latent heat load is not very
high, but the target sensible heat load is relatively high, the
degree of opening of the air flow control valve (141) is increased
to increase the flow rate of the air flowing through the branch
duct (140). Thus, the flow rate of the air passing through the
first air heat exchanger (63) and the cooling heat exchanger (61)
is relatively low. This reduces a cooling load of the evaporator
(25) of the heating medium circuit (41), thereby reducing cooling
capacity required in the evaporator (25).
[0170] In the seventh alternative described above, the operation
can be performed based on the latent or sensible heat load. Thus,
the latent and sensible heat loads can reliably be handled while
keeping the energy consumption low. The latent heat load to be
handled by the air conditioning system (10) can be calculated, for
example, from a difference between a target room humidity set in
the controller (100), and humidity of the outside air detected by a
sensor etc. The sensible heat load to be handled by the air
conditioning system (10) can be calculated, for example, from a
difference between a target room temperature set in the controller
(100), and temperature of the outside air detected by a sensor
etc.
[0171] In the seventh alternative, the air flow control valve (141)
is fully opened in winter etc., i.e., in heating operation for
heating the outside air by the electric heater (55), or
heating/humidifying operation for heating the outside air by the
electric heater (55), and humidifying the heated air by the
sprinkler (56). Specifically, the first air heat exchanger (63),
the cooling heat exchanger (61), the auxiliary heat exchanger (62),
and the second air heat exchanger (64) are stopped in the heating
operation or the heating/humidifying operation. At this time, the
flow rate of the air passing through the branch duct (140) is the
highest. Thus, the flow rate of the air passing through each of the
heat exchangers (61-64) can be reduced as much as possible, and
pressure loss in each of the heat exchangers (61-64) can be reduced
as much as possible. This can reduce power required by the blower
(57) in the heating operation and the heating/humidifying
operation.
[0172] The outlet end of the branch duct (140) of the seventh
alternative may be opened in the other part. Specifically, for
example, the outlet end of the branch duct (140) may be opened
downstream of the electric heater (55) as shown in FIG. 14.
[0173] [Other Embodiments]
[0174] The above embodiment may be modified in the following
manner.
[0175] The air conditioning system (10) according to the above
embodiment (and the alternatives) takes the outside air (OA) into
the air passage (52) to cool and dehumidify the air. However, the
air conditioning system may take the room air (RA) into the air
passage (52) to cool and dehumidify the room air.
[0176] In the above embodiment, the electric heater (55) is used as
the heating section provided in the air passage (52) to heat the
air. However, the heating section may be a condenser of a
refrigerant circuit which performs a refrigeration cycle, or other
heating members.
[0177] Two or more of the first to seventh alternatives may be
combined to constitute the air conditioning system (10). The
above-described embodiment has been set forth merely for the
purposes of preferred examples in nature, and are not intended to
limit the scope, applications, and use of the invention.
INDUSTRIAL APPLICABILITY
[0178] As described above, the present invention is useful for
dehumidification systems which cool and dehumidify air, and supply
the dehumidified air to the inside of the room.
DESCRIPTION OF REFERENCE CHARACTERS
[0179] 10 Air conditioning system (dehumidification system)
[0180] 25 Evaporator (cooling section)
[0181] 35 First water tank (flow rate control mechanism)
[0182] 36 Second water tank (flow rate control mechanism)
[0183] 37 Auxiliary pump (flow rate control mechanism)
[0184] 41 Heating medium circuit
[0185] 51 Casing
[0186] 52 Air passage
[0187] 55 Electric heater (heating section)
[0188] 59 Exhaust passage (exhaust duct)
[0189] 61 Cooling heat exchanger
[0190] 61c Paths (intermediate passage)
[0191] 62 Auxiliary heat exchanger
[0192] 62c Paths (intermediate passage)
[0193] 63 First air heat exchanger
[0194] 63c Paths (intermediate passage)
[0195] 64 Second air heat exchanger
[0196] 64c Paths (intermediate passage)
[0197] 65 Circulating pump (flow rate control mechanism)
[0198] 66 Branch passage
[0199] 68 Duct heat exchanger (latent heat exchanger)
[0200] 71a Inlet
[0201] 71b Outlet
[0202] 72a Inlet
[0203] 72b Outlet
[0204] 73a Inlet
[0205] 73b Outlet
[0206] 74a Inlet
[0207] 74b Outlet
[0208] 95 Evaporator (auxiliary cooling section)
[0209] 97 Three-way valve (diverted flow control mechanism)
[0210] 130 Circulation circuit (refrigerant circuit)
[0211] 140 Branch duct (bypass pipe)
[0212] 141 Air flow control valve (bypass flow control
mechanism)
* * * * *