U.S. patent application number 13/418700 was filed with the patent office on 2012-10-11 for air conditioner.
Invention is credited to Samchul Ha, Hongseong Kim, Juhyok KIM, Hanchoon Lee, Sangyeul Lee.
Application Number | 20120255323 13/418700 |
Document ID | / |
Family ID | 45894117 |
Filed Date | 2012-10-11 |
United States Patent
Application |
20120255323 |
Kind Code |
A1 |
KIM; Juhyok ; et
al. |
October 11, 2012 |
AIR CONDITIONER
Abstract
An air conditioner is provided. The air conditioner may include
a compressor that compresses a refrigerant, an outdoor
heat-exchanger that heat-exchanges with the refrigerant discharged
from the compressor according to a first operation mode, an indoor
heat-exchanger that heat-exchanges with the refrigerant discharged
from the compressor according to a second operation mode, and an
expander that decompresses the refrigerant passing through the
outdoor heat-exchanger or the indoor heat-exchanger. The expander
may include a first decompression portion disposed at an outlet
side or an inlet side of the outdoor heat-exchanger, the first
decompression portion having a first inner diameter, and a second
decompression portion connected to the first decompression portion
in series, the second decompression portion having a second inner
diameter greater than the first inner diameter.
Inventors: |
KIM; Juhyok; (Seoul, KR)
; Lee; Hanchoon; (Seoul, KR) ; Kim; Hongseong;
(Seoul, KR) ; Ha; Samchul; (Seoul, KR) ;
Lee; Sangyeul; (Seoul, KR) |
Family ID: |
45894117 |
Appl. No.: |
13/418700 |
Filed: |
March 13, 2012 |
Current U.S.
Class: |
62/498 ;
62/524 |
Current CPC
Class: |
F25B 2341/0662 20130101;
F25B 41/067 20130101; F25B 13/00 20130101; F25B 2400/16
20130101 |
Class at
Publication: |
62/498 ;
62/524 |
International
Class: |
F25B 39/02 20060101
F25B039/02; F25B 1/00 20060101 F25B001/00 |
Foreign Application Data
Date |
Code |
Application Number |
Apr 7, 2011 |
KR |
10-2011-0032179 |
Claims
1. An air conditioner, comprising: a compressor that compresses a
refrigerant; an outdoor heat-exchanger that heat-exchanges with the
refrigerant discharged from the compressor according to a first
operation mode; an indoor heat-exchanger that heat-exchanges with
the refrigerant discharged from the compressor according to a
second operation mode; and an expander that decompresses the
refrigerant having passed through the outdoor heat-exchanger or the
indoor heat-exchanger, wherein the expander comprises: a first
decompression portion disposed at an outlet side or an inlet side
of the outdoor heat-exchanger, the first decompression portion
having a first inner diameter; and a second decompression portion
connected to the first decompression portion in series, the second
decompression portion having a second inner diameter greater than
the first inner diameter.
2. The air conditioner according to claim 1, wherein, in the first
operation mode, the refrigerant is introduced into the second
decompression portion through the first decompression portion.
3. The air conditioner according to claim 1, wherein, in the second
operation mode, the refrigerant is introduced into the first
decompression portion through the second decompression portion.
4. The air conditioner according to claim 1, wherein, in the first
operation mode, the first decompression portion is disposed at the
outlet side of the outdoor heat-exchanger, and the second
decompression portion is disposed at an inlet side of the indoor
heat-exchanger.
5. The air conditioner according to claim 1, wherein, in the second
operation mode, the first decompression portion is disposed at the
inlet side of the outdoor heat-exchanger, and the second
decompression portion is disposed at an outlet side of the indoor
heat-exchanger.
6. The air conditioner according to claim 1, wherein the first
decompression portion comprises: a cooling refrigerant inflow
portion, through which the refrigerant discharged from the outdoor
heat-exchanger is introduced, or refrigerant having passed through
the second decompression portion is discharged; and a first
coupling portion coupled to the second decompression portion.
7. The air conditioner according to claim 1, wherein the second
decompression portion comprises: a heating refrigerant inflow
portion, through which the refrigerant discharged from the indoor
heat-exchanger is introduced, or refrigerant having passed through
the first decompression portion is discharged; and a second
coupling portion coupled to the first decompression portion.
8. The air conditioner according to claim 1, wherein an end of the
first decompression portion is coupled to an end of the second
decompression portion.
9. The air conditioner according to claim 1, further comprising a
connection member disposed between the first decompression portion
and the second decompression portion that connects the first
decompression portion to the second decompression portion.
10. The air conditioner according to claim 9, wherein the
connection member comprises a tank that connects the first
decompression portion to the second decompression portion.
11. The air conditioner according to claim 1, wherein the first
operation mode is a cooling operation mode, and the second
operation mode is a heating operation mode.
12. The air conditioner according to claim 1, wherein a ratio of
the second inner diameter to the first diameter is greater than
about 1 and less than about 5.
13. An air conditioner, comprising: a compressor that compresses a
refrigerant; an outdoor heat-exchanger disposed in an outdoor space
that condenses the refrigerant having passed through the compressor
in a cooling operation mode; an indoor heat-exchanger disposed in
an indoor space that condenses the refrigerant having passed
through the compressor in a heating operation mode; and a plurality
of capillary tubes that expands the refrigerant introduced through
the indoor heat-exchanger or the outdoor heat-exchanger, the
plurality of capillary tubes being connected to each other in
series, wherein, in the cooling or heating operation mode, the
refrigerant passes through the plurality of capillary tubes.
14. The air conditioner according to claim 13, wherein the
plurality of capillary tubes comprises: a first capillary tube
having a first diameter; and a second capillary tube having a
second diameter greater than the first diameter of the first
capillary tube.
15. The air conditioner according to claim 14, wherein, in the
cooling operation mode, the refrigerant passes through the first
capillary tube and then passes through the second capillary
tube.
16. The air conditioner according to claim 15, wherein the
refrigerant flows into the second capillary tube in a two-phase
state.
17. The air conditioner according to claim 14, wherein, in the
heating operation mode, the refrigerant passes through the second
capillary tube and then passes through the first capillary
tube.
18. The air conditioner according to claim 17, wherein the
refrigerant flows into the first capillary tube in a two-phase
state.
19. The air conditioner according to claim 14, wherein a ratio of
the second inner diameter to the first inner diameter is greater
than about 1 and less than about 5
20. An air conditioner having a refrigeration cycle formed by a
compressor, an outdoor heat-exchanger, an expander, and an indoor
heat-exchanger connected to each other in series, the air
conditioner comprising: a flow converter that guides a refrigerant
discharged from the compressor into the outdoor heat-exchanger or
the indoor heat-exchanger; and the expander, wherein the expander
comprises: a first capillary tube disposed between the outdoor
heat-exchanger and the indoor heat-exchanger, the first capillary
tube having a first inner diameter; and a second capillary tube
coupled the first capillary tube, the second capillary tube having
a second inner diameter greater than the first inner diameter.
21. The air conditioner according to claim 20, wherein, when the
refrigeration cycle performs a cooling operation, the refrigerant
passes through the first capillary tube and then passes through the
second capillary tube.
22. The air conditioner according to claim 20, wherein, when the
refrigeration cycle performs a heating operation, the refrigerant
passes through the second capillary tube and then passes through
the first capillary tube.
23. The air conditioner according to claim 20, wherein one end of
the second capillary tube is coupled to one end of the first
capillary tube.
24. The air conditioner according to claim 23, further comprising a
connection member that connects the one end of the second capillary
tube to the one end of the first capillary tube.
25. The air conditioner according to claim 24, wherein the
connection member comprises a tank that connects the first
capillary tube to the second capillary tube.
26. The air conditioner according to claim 17, wherein a ratio of
the second inner diameter to the first inner diameter is greater
than about 1 and less than about 5.
27. An expander for an air conditioner, the expander comprising: a
first decompression portion having a first inner diameter; and a
second decompression portion connected to the first decompression
portion and having a second inner diameter greater than the first
inner diameter, wherein a flow rate of refrigerant through the
expander increases or decreases based on a direction of refrigerant
flow.
28. The expander according to claim 27, wherein a ratio of the
second inner diameter to the first inner diameter is greater than
about 1 and less than about 5.
29. The expander according to claim 27, wherein the first
decompression portion comprises a first capillary tube and the
second decompression portion comprises a second capillary tube
connected to the first capillary tube.
30. An air conditioner comprising the expander of claim 27.
Description
CROSS-REFERENCE TO RELATED APPLICATION(S)
[0001] The present application claims priority under 35 U.S.C. 119
and 35 U.S.C. 365 to Korean Patent Application No. 10-2011-0032179,
filed in Korea on Apr. 7, 2011, which is hereby incorporated by
reference in its entirety.
BACKGROUND
[0002] 1. Field
[0003] An air conditioner is disclosed herein.
[0004] 2. Background
[0005] Air conditioners are known. However, they suffer from
various disadvantages.
BRIEF DESCRIPTION OF THE DRAWINGS
[0006] Embodiments will be described in detail with reference to
the following drawings in which like reference numerals refer to
like elements, and wherein:
[0007] FIG. 1 is a schematic diagram of an air conditioner
according to an embodiment;
[0008] FIG. 2 is a perspective view of the expander of FIG. 1;
[0009] FIG. 3 is a side view of a portion of the expander of FIG.
2;
[0010] FIG. 4 is a graph illustrating a difference in flow rate of
a refrigerant in cooling and heating operations according to an
embodiment; and
[0011] FIG. 5 is a view illustrating a portion of an expander
according to another embodiment.
DETAILED DESCRIPTION
[0012] Hereinafter, embodiments will be described with reference to
the accompanying drawings. The concepts may, however, be embodied
in many different forms and should not be construed as being
limited to the embodiments set forth herein; rather, alternate
embodiments included in other retrogressive inventions or falling
within the spirit and scope of the present disclosure may fully
convey the concepts to those skilled in the art.
[0013] Generally, air conditioners are home appliances that
maintain indoor air at a proper state according to a use and
purpose thereof. For example, such an air conditioner may cool
indoor air in summer and warm the indoor air in winter. Further,
the air conditioner may control a humidity of the indoor air and
purify the indoor air by removing impurities therefrom. As products
for life's convenience, such as air conditioners, are gradually
expanded in use, consumers require products having high energy
efficiency, superior performance, and greater convenience in
use.
[0014] The air conditioner may perform a cooling or heating
operation for an indoor space according to an operation direction
of a refrigeration cycle. That is, a flow direction of a
refrigerant flowing in the refrigeration cycle may vary according
to a specific operation condition (cooling or heating requirement).
Further, the cooling or heating operation may be selectively
performed using one system device.
[0015] In more detail, the refrigeration cycle may be formed by
sequentially connecting to each other a compressor, an outdoor
heat-exchanger, an expander, and an indoor heat-exchanger. When a
cooling operation is performed, the refrigerant passing through the
compressor may be condensed in the outdoor heat-exchanger and
expanded (decompressed) while passing through the expander. Then,
the refrigerant may be evaporated in the indoor heat-exchanger and
introduced again into the compressor. On the other hand, when a
heating operation is performed, the refrigerant passing through the
compressor may be condensed in the indoor heat-exchanger and passes
through the expander. Then, the refrigerant may be evaporated in
the outdoor heat-exchanger and introduced again into the
compressor.
[0016] The refrigerant passing through the outdoor heat-exchanger
or the indoor heat-exchanger may be additionally condensed in a
liquid state to reach an overcooled state. As the overcooled degree
of the refrigerant increases, a flow rate of the refrigerant
passing through the expander may increase. Thus, the flow rate of
the refrigerant may increase to improve the cooling or heating
performance.
[0017] An expander is a device that controls the flow rate of the
refrigerant and a pressure of the system. Thus, the expander may
act as an important element for determining the cooling or heating
performance. Typically, the expander may have a constant sectional
area (constant inner diameter).
[0018] According to pressure and temperature (outdoor temperature
and indoor temperature) of the refrigeration cycle, an overcooled
degree of the refrigerant during the heating operation may be
higher than that of the refrigerant during the cooling operation.
Thus, a flow rate of the refrigerant during the heating operation
may be greater than that of the refrigerant during the cooling
operation.
[0019] However, when a flow rate of the refrigerant during the
heating operation is less than that of the refrigerant during the
cooling operation, it may be difficult to obtain a flow rate of the
refrigerant for the cooling or heating operation required in the
refrigeration system. For example, the refrigerant may have a flow
rate greater than that required during the heating operation, and
also, the refrigerant may have a flow rate less than that required
during the cooling operation.
[0020] As a result, refrigeration performance during the cooling
operation may be insufficient, and the refrigerant performance
during the heating operation may be excessive.
[0021] FIG. 1 is a schematic diagram of an air conditioner
according to an embodiment. Referring to FIG. 1, the air
conditioner 1 may include a compressor 10 that compresses a
refrigerant to a high-temperature and high-pressure, an outdoor
heat-exchanger 30 disposed in an outdoor space that heat-exchanges
the refrigerant with outdoor air, an indoor heat-exchanger 40
disposed in an indoor space that heat-exchanges the refrigerant
with indoor air, and an expander 100 that decompresses the
refrigerant condensed in the outdoor heat-exchanger 30 or the
indoor heat-exchanger 40 to a predetermined pressure.
[0022] The air conditioner 1 may further include a flow converter
20 that guides the refrigerant discharged from the compressor 10
toward the outdoor heat-exchanger 30 or the indoor heat-exchanger
40. The flow converter 20 may include a four-way valve that
controls a flow direction of the refrigerant.
[0023] When a cooling operation is performed, the refrigerant
discharged from the compressor 10 may pass through the flow
converter 20 to flow toward the outdoor heat-exchanger 30. On the
other hand, when a heating operation is performed, the refrigerant
discharged from the compressor 10 may pass through the flow
converter 20 to flow toward the indoor heat-exchanger 40.
[0024] A gas/liquid separator 50 that filters a liquid refrigerant
from an evaporated refrigerant may be disposed at an inlet side of
the compressor 10. A gaseous refrigerant passing through the
gas/liquid separator 50 may be introduced into the compressor
10.
[0025] The expander 100 may include a first capillary tube 110
disposed at an outlet or inlet side of the outdoor heat-exchanger
30 and a second capillary tube 150 disposed at an outlet or inlet
side of the indoor heat-exchanger 40. The first capillary tube 110
may be referred to as a "first decompression portion", and the
second capillary tube 150 may be referred to as a "second
decompression portion". The term "outlet side" and "inlet side" may
be understood as terms defined on the basis of the flow direction
of the refrigerant.
[0026] The first and second capillary tubes 110 and 150 may be
connected to each other in series. Also, the first and second
capillary tubes 110 and 150 may have diameters different from each
other. The refrigerant may be phase-converted from an overcooled
liquid state into a two-phase state (i.e., a mixed state of liquid
and gaseous refrigerants) while passing through the expander
100.
[0027] A flow direction of the refrigerant according to an
operation mode will be described hereinbelow.
[0028] When the air conditioner 1 is operated in a cooling
operation mode (a first operation mode), the refrigerant may flow
in a direction (A), shown in FIG. 1 as a solid arrow. In more
detail, the refrigerant passing through the compressor 10 may pass
through the flow converter 20 and be introduced into the outdoor
heat-exchanger 30. Then, the refrigerant may be condensed while
passing through the outdoor heat-exchanger 30. When the
condensation of the refrigerant is completed, the refrigerant may
be converted into an overcooled liquid state.
[0029] The refrigerant in the overcooled liquid state may be
decompressed to a predetermined pressure while passing through the
expander 100, and thus, a flow rate of the refrigerant may be
controlled. That is, the flow rate of the refrigerant may be
controlled according to structural characteristics of the expander
100, for example, an inner diameter or length of the expander
100.
[0030] The refrigerant passing through the expander 100 may be
evaporated while passing through the indoor heat-exchanger 40.
Then, the evaporated refrigerant may pass through the gas/liquid
separator 50 via the flow converter 20, and the gaseous liquid,
from which the liquid refrigerant is separated, may be introduced
into the compressor 10. The refrigerant circulation process may be
repeatedly performed.
[0031] On the other hand, when the air conditioner 1 is operated in
a heating mode (a second operation mode), the refrigerant may flow
in a direction (B), shown in FIG. 1 as a dotted arrow. In more
detail, the refrigerant passing through the compressor 10 may pass
through the flow converter 20 and be introduced into the indoor
heat-exchanger 40. Then, the refrigerant may be condensed while
passing through the indoor heat-exchanger 40. When the condensation
of the refrigerant is completed, the refrigerant may be converted
into an overcooled liquid state.
[0032] The refrigerant in the overcooled liquid state may be
decompressed to a predetermined pressure while passing through the
expander 100, and thus, a flow rate of the refrigerant may be
controlled. Also, the refrigerant passing through the expander 100
may be evaporated while passing through the outdoor heat-exchanger
30, and the evaporated refrigerant may be introduced into the
compressor 10 through the flow converter 20 and the gas/liquid
separator 50. The refrigerant circulation process may be repeatedly
performed.
[0033] As described above, when the cooling or heating operation is
performed, the refrigerant circulating through the refrigeration
cycle may be changed in flow direction. In more detail, when the
cooling operation is performed, the refrigerant condensed in the
outdoor heat-exchanger 30 may successively pass through the first
capillary tube 110 and the second capillary tube 150 and may be
introduced into the indoor heat exchanger 40. That is, the first
capillary tube 110 may be disposed at an outlet side of the outdoor
heat-exchanger 30, and the second capillary tube 150 may be
disposed at an inlet side of the indoor heat-exchanger 40.
[0034] On the other hand, when the heating operation is performed,
the refrigerant condensed in the indoor heat-exchanger 40 may
successively pass through the second capillary tube 150 and the
first capillary tube 110 and be introduced into the outdoor
heat-exchanger 30. That is, the second capillary tube may be
disposed at an outlet side of the indoor heat-exchanger 40, and the
first capillary tube 110 may be disposed at the inlet side of the
outdoor heat-exchanger 30.
[0035] When the first and the second capillary tubes 110 and 150
have inner diameters different from each other, a flow resistance
of the refrigerant flowing into the first or second capillary tube
110 or 150 may be different. Thus, pressure drop or refrigerant
flow rate may be different. More specifically, when an inner
diameter of the capillary tube decreases, the pressure drop may
increase and the refrigerant flow rate may decrease. Hereinafter,
expander 100 will be described in detail with reference to the
accompanying drawings.
[0036] FIG. 2 is a perspective view of the expander FIG. 1. FIG. 3
is a side view of a portion of the expander of FIG. 2. Referring to
FIGS. 2 and 3, the expander 100 may include the plurality of
capillary tubes 110 and 150, which may be connected to each other
in series.
[0037] The plurality of capillary tubes 110 and 150 may include the
first capillary tube 110, which may be connected to an outlet side
of the outdoor heat-exchanger 30 during the cooling operation, and
the second capillary tube 150, which may be connected to an outlet
side of the indoor heat-exchanger 40 during the heating operation.
Each of the first and second capillary tubes 110 and 150 may be
wound in a coil shape, and may be coupled to each other.
[0038] The first capillary tube 110 may include a cooling
refrigerant inflow portion 111, through which the refrigerant
discharged from the outdoor heat-exchanger 30 may be introduced,
and a first coupling portion 112 coupled to the second capillary
tube 150. The cooling refrigerant inflow part 111 may be disposed
on an end of one side of the first capillary tube 110, and the
first coupling part 112 may be disposed on an end of the other side
of the first capillary tube 110.
[0039] In the cooling operation mode, the refrigerant passing
through the outdoor heat-exchanger 30 may be introduced into the
expander 100 through the cooling refrigerant inflow portion 111. On
the other hand, in the heating operation mode, the refrigerant
passing through the second capillary tube 150 and the first
capillary tube 110 may be discharged from the expander 100 through
the cooling refrigerant inflow portion 111.
[0040] The second capillary tube 150 may include a heating
refrigerant inflow portion 151, through which the refrigerant
discharged from the indoor heat-exchanger 40 may be introduced, and
a second coupling portion 152 coupled to the first capillary tube
150. The heating refrigerant inflow portion 151 may be disposed on
an end of one side of the second capillary tube 150, and the second
coupling part 152 may be disposed on an end of the other side of
the second capillary tube 150.
[0041] In the heating operation mode, the refrigerant passing
through the indoor heat-exchanger 40 may be introduced into the
expander 100 through the heating refrigerant inflow portion 151. On
the other hand, in the cooling operation mode, the refrigerant
passing through the first and second capillary tubes 110 and 150
may be discharged from the expander through the heating refrigerant
inflow portion 151.
[0042] The first coupling portion 112 may be connected to the
second coupling portion 152. For example, an end of the first
capillary tube 110 may be coupled to an end of the second capillary
tube 150.
[0043] The expander 100 may include a connection portion 130
coupled to the first and second coupling portions 112 and 152. The
first and second capillary tubes 110 and 150 may communicate with
each other through the connection portion 130. That is, the
refrigerant flowing into the first capillary tube 110 may be
introduced into the second capillary tube 150 through the
connection portion 130, and the refrigerant flowing into the second
capillary tube 150 may be introduced into the first capillary tube
110 through the connection portion 130.
[0044] The first and second coupling portions 112 and 152 may be,
for example, welded to each other or coupled to each other through
a separate coupling member to manufacture the connection portion
130. Alternatively, the first coupling portion 112 may be inserted
into the second coupling portion 152 to manufacture the connection
portion 130. However, embodiments are not limited to such methods
of manufacturing the connection portion 130.
[0045] The cooling refrigerant inflow portion 111 may be an inlet
port, through which the refrigerant may be introduced into the
expander 100 when the cooling operation is performed, and the
heating refrigerant inflow portion 115 may be an inlet port,
through which the refrigerant is introduced into the expander 100
when the heating operation is performed. On the other hand, the
heating refrigerant inflow portion 115 may be an outlet port,
through which the refrigerant may be discharged from the expander
110 when the cooling operation is performed, and the cooling
refrigerant inflow part 111 may be an outlet port, through which
the refrigerant may be discharged from the expander 110 when the
heating operation is performed.
[0046] An inner diameter of the first capillary tube 110 may be
referred to using reference symbol D1 (a first inner diameter), and
an inner diameter of the second capillary tube 150 may be referred
to using reference symbol D2 (a second inner diameter). The second
inner diameter D2 may be greater than the first inner diameter
D1.
[0047] When the air conditioner 1 performs the cooling operation,
the first capillary tube 110 may be referred to as an "expander"
that provides a flow resistance, so that the refrigerant in the
overcooled liquid state is phase-changed into refrigerant having a
liquid state. The second capillary tube 150 may be referred to as
an "expander" that provides a flow resistance, so that the
refrigerant in the liquid state is phase-changed into refrigerant
having a two-phase state (i.e., a mixed state of liquid and gaseous
refrigerants). In this case, the first capillary tube 110 may be
the expander in which a single phase flow is performed, and the
second capillary tube 150 may be the expander in which a two-phase
flow (liquid phase and gaseous phase flow) is performed.
[0048] On the other hand, when the air conditioner 1 performs the
heating operation, the second capillary tube 150 may be referred to
as an "expander" that provides a flow resistance, so that the
refrigerant in the overcooled liquid state is phase-changed into
refrigerant in a liquid state. Also, the first capillary tube 110
may be referred to as an "expander" that provides a flow
resistance, so that the refrigerant in the liquid state is
phase-changed into refrigerant in the two-phase state (the mixed
state of the liquid and gaseous refrigerants). In this case, the
second capillary tube 150 may be the expander in which a single
phase flow is performed, and the first capillary tube 110 may be
the expander in which a two-phase flow (liquid phase and gaseous
phase flow) is performed.
[0049] When the cooling operation is performed, the refrigerant may
successively pass through the first and second capillary tubes 110
and 150 to form the single phase flow and the two-phase flow.
During the single phase flow and the two-phase flow, a pressure
drop due to friction may occur within the first and second
capillary tube 110 and 150.
[0050] Further, when the refrigerant flows in the two-phase state,
a pressure drop due to acceleration of the refrigerant, in addition
to the pressure drop due to the friction within the capillary tube,
may occur. Thus, when the refrigerant flows in the two-phase state,
the pressure drop (flow resistance) effect may be significant when
compared to that of the single phase flow. Also, when the pressure
drop effect is significant, a mass flow rate within the capillary
tube may be relatively low.
[0051] The more the inner diameter of each of the first and second
capillary tubes 110 and 150 decreases, the more the flow resistance
increases. Thus, a flow rate of the refrigerant may decrease.
[0052] When the inner diameter of the capillary tube in which the
two-phase flow is performed decreases, the pressure drop effect of
the refrigerant flowing into the expander 100 may increase. Thus,
the flow rate of the refrigerant may decrease.
[0053] Referring to FIGS. 2 and 3, in the cooling operation mode
(see arrow (A)), the refrigerant may flow into the first capillary
tube 110 in the single phase state and flow into the second
capillary tube 150 having an inner diameter greater than that of
the first capillary tube 110 in the two-phase state. In the heating
operation mode (see arrow (B)), the refrigerant may flow into the
second capillary tube 150 in the single phase state and flow into
the first capillary tube 110 having an inner diameter less than
that of the second capillary tube 150 in the two-phase state.
[0054] Thus, since a refrigerant decompression effect in the
heating operation mode is greater than that in the cooling
operation mode, the flow rate of the refrigerant flowing into the
expander 100 during the heating operation may be less than the
refrigerant flowing into the expander 100 during the cooling
operation.
[0055] In summary, the plurality of capillary tubes 110 and 150 may
be connected to each other in series, and the refrigerant may pass
through the plurality of capillary tubes 110 and 150 during the
cooling or heating operation. However, because the plurality of
capillary tubes 110 and 150 have inner diameters different from
each other, the cooling flow rate may be greater than the heating
flow rate. In general, considering that the refrigerant flow rate
required for the heating operation may be less than that required
for the cooling operation, the refrigerant flow rate required for
the system during the cooling and heating operation may be
satisfied by the above-described configuration.
[0056] Hereinafter, a refrigerant decompression effect due to a
length of the first or second capillary tube 110 or 150 will be
described with reference to Table. 1.
TABLE-US-00001 TABLE 1 First capillary Second capillary
Classification tube (110) tube (150) Length L of L1 L2 capillary
tube
[0057] In general, when the capillary tube increases in length, a
decompression effect of the refrigerant passing through the inside
of the capillary tube may increase. Thus, the more the length L1 of
the first capillary tube 110 or the length L2 of the second
capillary tube 150 increases, the more the refrigerant
decompression performance may increase and the refrigerant flow
rate may relatively decrease. The lengths L1 and L2 may be set to
specific values according to the phase-change process of the
refrigerant during the cooling or heating operation.
[0058] That is, the length L1 may be set so that the refrigerant
flows into the first capillary tube 110 in the single phase state
and then flows into the second capillary tube 150 in the two-phase
state during the cooling operation. On the other hand, the length
L2 may be set so that the refrigerant flows into the second
capillary tube 150 in the single phase state and then flows into
the first capillary tube 110 in the two-phase state during the
heating operation.
[0059] The conversion between the single phase flow and the
two-phase flow may be unclear at the connection part 130 of the
first and second capillary tubes 110 and 150. However, it may be
understood that the two-phase flow of the refrigerant may be larger
within the first capillary tube 110 than the second capillary tube
150 during the cooling operation, and the two-phase flow of the
refrigerant may be larger within the first capillary tube 110 than
the second capillary tube 150 during the heating operation.
[0060] FIG. 4 is a graph illustrating a difference in a flow rate
of a refrigerant in cooling and heating operations according to an
embodiment. Hereinafter, a flow rate difference of the refrigerant
during the cooling and heating operation according to an embodiment
will be described with reference to FIG. 4.
[0061] Referring to FIG. 4, a horizontal-axis variable of the graph
represents D2/D1 (an inner diameter of the second capillary tube to
an inner diameter of the first capillary tube), and a vertical-axis
variable represents a directional refrigerant flow rate difference
(hereinafter, referred to as a "refrigerant flow rate
difference").
[0062] Since D2 may be greater that D1, a valve of D2/D1 may exceed
1. Also, the more the value of D2/D1 increases, the more the
refrigerant flow rate difference may increase. Also, the value of
D2/D1 may be less than 5.
[0063] For example, when the D2/D1 is 1.14, the refrigerant flow
rate difference may be about 3.2%. That is, the refrigerant flow
rate in the cooling operation mode may be greater by about 3.2%
than that in the heating operation mode. For example, when the
refrigerant flow rate in the heating operation mode is about 100,
the refrigerant flow rate in the cooling operation mode may be
about 103.2.
[0064] Also, when D2/D1 is about 1.32, the refrigerant flow rate
difference may be about 13%. As shown in FIG. 4, the plurality of
capillary tubes may have inner diameters different from each other
to secure a greater refrigerant flow rate in the cooling operation
mode than in the heating operation mode.
[0065] Hereinafter, another embodiment will be described with
reference to FIG. 5. In describing this embodiment, like reference
numerals have been used to indicate like elements, and repetitive
description has been omitted.
[0066] FIG. 5 is a view illustrating a portion of an expander
according to another embodiment. Referring to FIG. 5, an expander
100 according to this embodiment may include a first capillary tube
110 connected to an outlet side of an outdoor heat-exchanger 30, a
second capillary tube 150 connected to an outlet side of an indoor
heat-exchanger 40, and a connection member 140 disposed between the
first capillary tube 110 and the second capillary tube 150.
[0067] The connection member 140 may be a tank, in which
refrigerant may be temporarily received while flowing into the
expander 100. The connection member 140 may connect the first
capillary tube 110 to the second capillary tube 150.
[0068] The connection member 140 may include a first connection
portion 141 connected to the first capillary tube 110 and a second
connection portion 142 connected to the second capillary tube 150.
The first connection portion 141 may be disposed at one side of the
connection member 140, and the second connection portion 142 may be
disposed at an other side of the connection member 140. The
refrigerant within the first and second capillary tubes 110 and 150
may flow into the connection member 140 through the first and
second connection portions 141 and 142.
[0069] An inner diameter D3 of the connection member 140 may be
greater than each of an inner diameter D1 of the first capillary
tube 110 and an inner diameter D2 of the second capillary tube 150.
That is, a refrigerant flow sectional area of the connection member
140 may be greater than that of each of the first and second
capillary tubes 110 and 150.
[0070] Because the connection member 140 has an inner diameter or
sectional area greater than that of each of the first and second
capillary tubes 110 and 150, a decompression effect while the
refrigerant flows into the connection member 140 may not be large.
Thus, when the refrigerant is directly introduced from the first
capillary tube 110 into the second capillary tube 150 or from the
second capillary tube 150 into the first capillary tube 150 like
the foregoing embodiment, refrigerant decompression and refrigerant
flow rate adjustment effects when the refrigerant is introduced
through the connection member 140 may be similar to those of the
foregoing embodiment.
[0071] In the cooling operation mode, the refrigerant may flow into
the connection member 140 or the second capillary tube 150 in a
two-phase state. Also, in the heating operation mode, the
refrigerant may flow into the connection member 140 or the first
capillary tube 110 in the two-phase state.
[0072] Also, as shown in the embodiments disclosed herein, a
refrigerant flow rate in the cooling operation mode may be greater
than that in the heating operation mode. Thus, the refrigerant flow
rate required for the cooling or heating operation mode of the
system may be satisfied.
[0073] According to embodiments disclosed herein, the flow rate of
the refrigerant flowing according to the operation direction of the
air conditioner may be adequately controlled to improve the cooling
or heating performance.
[0074] Also, the refrigerant passing through the condenser when the
cooling operation is performed may flow into the capillary tube
having a relatively small inner diameter in the single phase state
and flow into the capillary tube having a relatively large inner
diameter in the two-phase state. Thus, the flow resistance may be
reduced to secure the high refrigerant flow rate.
[0075] On the other hand, the refrigerant passing through the
condenser when the heating operation is performed may flow into the
capillary tube having a relatively large inner diameter in the
single phase state and flow into the capillary tube having a
relatively small inner diameter in the two-phase state. Thus, the
flow resistance may relatively increase to reduce the refrigerant
flow rate.
[0076] Also, since the refrigerant may adequately flow according to
the operation modes, that is, the cooling mode or the heating mode,
the refrigeration cycle may be economically performed.
[0077] Also, since the plurality of capillary tubs may be connected
to each other in series to constitute the expander, the system may
be simplified in structure and inexpensive in manufacturing
costs.
[0078] According to embodiments disclosed herein, the flow rate of
the refrigerant flowing according to the operation direction of the
air conditioner may be adequately controlled to improve the cooling
or heating performance. Thus, industrial applicability may be
significantly improved.
[0079] Embodiments disclosed herein provide an air conditioner in
which a plurality of expanders are disposed in series.
[0080] Embodiments disclosed herein provide an air conditioner that
may include a compressor that compresses a refrigerant; an outdoor
that heat-exchanges heat-exchanging with the refrigerant discharged
from the compressor according to a first operation mode; an indoor
heat-exchanger that heat-exchanges with the refrigerant discharged
from the compressor according to a second operation mode; and an
expander that decompresses the refrigerant passing through the
outdoor heat-exchanger or the indoor heat-exchanger. The expander
may include a first decompression part or portion disposed at an
outlet side or an inlet side of the outdoor heat-exchanger, the
first decompression part or portion having a first inner diameter,
and a second decompression part or portion connected to the first
decompression part in series, the second decompression part or
portion having a second inner diameter greater than the first inner
diameter.
[0081] Embodiments disclosed herein further provide an air
conditioner that may include a compressor that compresses a
refrigerant; an outdoor heat-exchanger disposed in an outdoor space
that condenses the refrigerant passing through the compressor in a
cooling operation process; an indoor heat-exchanger disposed in an
indoor space to condense the refrigerant passing through the
compressor in a heating operation process; and a plurality of
capillary tubes that expand the refrigerant introduced through the
indoor heat-exchanger or the outdoor heat-exchanger, the plurality
of capillary tubes being connected to each other in series. In the
cooling or heating operation process, the refrigerant passes
through the plurality of capillary tubes.
[0082] Embodiments disclosed herein additionally provide an air
conditioner having a refrigeration cycle constituted by
sequentially connecting a compressor, an outdoor heat-exchanger, an
expander, and an indoor heat-exchanger to each other that may
include a flow conversion part or converter that guides a
refrigerant discharged from the compressor into the outdoor
heat-exchanger or the indoor heat-exchanger. The expander may
include a first capillary tube disposed between the outdoor
heat-exchanger and the indoor heat-exchanger, the first capillary
tube having a first inner diameter, and a second capillary tube
coupled to an end of one side of the first capillary tube, the
second capillary tube having a second inner diameter greater than
the first inner diameter.
[0083] Although embodiments have been described with reference to a
number of illustrative embodiments thereof, it should be understood
that numerous other modifications and embodiments can be devised by
those skilled in the art that will fall within the spirit and scope
of the principles of this disclosure. More particularly, various
variations and modifications are possible in the component parts
and/or arrangements of the subject combination arrangement within
the scope of the disclosure, the drawings and the appended claims.
In addition to variations and modifications in the component parts
and/or arrangements, alternative uses will also be apparent to
those skilled in the art.
[0084] Any reference in this specification to "one embodiment," "an
embodiment," "example embodiment," etc., means that a particular
feature, structure, or characteristic described in connection with
the embodiment is included in at least one embodiment of the
invention. The appearances of such phrases in various places in the
specification are not necessarily all referring to the same
embodiment. Further, when a particular feature, structure, or
characteristic is described in connection with any embodiment, it
is submitted that it is within the purview of one skilled in the
art to effect such feature, structure, or characteristic in
connection with other ones of the embodiments.
[0085] Although embodiments have been described with reference to a
number of illustrative embodiments thereof, it should be understood
that numerous other modifications and embodiments can be devised by
those skilled in the art that will fall within the spirit and scope
of the principles of this disclosure. More particularly, various
variations and modifications are possible in the component parts
and/or arrangements of the subject combination arrangement within
the scope of the disclosure, the drawings and the appended claims.
In addition to variations and modifications in the component parts
and/or arrangements, alternative uses will also be apparent to
those skilled in the art.
* * * * *