Patent Grant
9625217
This application claims the benefit of Korean Application No. 10-2012-0006965, filed on Jan. 20, 2012 in the Korean Intellectual Property Office, the disclosure of which is incorporated herein by reference.
Field of the Disclosure
The present disclosure relates to an air conditioner including a heat exchanger and, more particularly, to a heat exchanger in which the passage of a refrigerant is alternated in a heat exchange unit.
Discussion of the Related Art
In general, an air conditioner is an apparatus configured to include a compressor, an outdoor heat exchanger, an expansion valve, and an indoor heat exchanger, to cool or heat the interior of a room using a refrigerating cycle. That is, the air conditioner may include a cooler for cooling the interior of a room and a heater for heating the interior of a room. The air conditioner may also be formed of a combination cooling and heating air conditioner for cooling or heating the interior of a room.
If the air conditioner is formed of the combination cooling and heating air conditioner, the air conditioner further includes a 4-way valve for changing the passage of a refrigerant, compressed by the compressor, depending on an air cooling operation or a heating operation. That is, in the air cooling operation, the refrigerant compressed by the compressor flows into the outdoor heat exchanger through the 4-way valve, and the outdoor heat exchanger functions as a condenser. Next, the refrigerant condensed by the outdoor heat exchanger is expanded by the expansion valve, and the expanded refrigerant flows into the indoor heat exchanger. In this case, the indoor heat exchanger functions as an evaporator. Next, the refrigerant evaporated by the indoor heat exchanger flows into the compressor through the 4-way valve.
Meanwhile, in the heating operation, the refrigerant compressed by the compressor flows in the indoor heat exchanger through the 4-way valve, and the indoor heat exchanger functions as a condenser. Next, the refrigerant condensed by the indoor heat exchanger is expanded by the expansion valve, and the expanded refrigerant flows into the outdoor heat exchanger. In this case, the outdoor heat exchanger functions as an evaporator. Next, the refrigerant evaporated by the outdoor heat exchanger flows into the compressor through the 4-way valve.
One object is to provide a heat exchanger in which the passage of a refrigerant is alternated in a heat exchange unit.
Objects of the present invention are not limited to the above-mentioned objects, and other objects that have not been described above will be evident to those skilled in the art from the following description.
An air conditioner according to an embodiment of the present invention includes a compressor; and a heat exchanger, including a first header pipe to flow therein a refrigerant compressed by the compressor, a heat exchange unit coupled to the first header pipe and to thermally exchange the refrigerant with air, a bypass pipe to have the refrigerant, thermally exchanged in the heat exchange unit, to pass therethrough in an air cooling operation, a second header pipe coupled to the heat exchange unit and to have the refrigerant passing through the bypass pipe, to flow therein in the air cooling operation, a plurality of first header branch pipes to couple the first header pipe and the heat exchange unit, and a plurality of second header branch pipes to couple the second header pipe and the heat exchange unit, wherein at least one of second header branch pipe crosses at least one of the first header branch pipe.
Details of other embodiments are included in the detailed description and drawings.
The above and other objects and features of the present disclosure will become apparent from the following description of some embodiments given in conjunction with the accompanying drawings, in which:
Merits and characteristics of the present disclosure and methods for achieving them will become more apparent from the following embodiments taken in conjunction with the accompanying drawings. However, the present invention is not limited to the disclosed embodiments, but may be implemented in various ways. The embodiments are provided to complete the disclosure and to allow those having ordinary skill in the art to fully understand the principles of the present invention. The same reference numbers may be used throughout the drawings to refer to the same or like parts.
Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings for describing an outdoor heat exchanger.
The air conditioner according to the embodiment of the present invention includes an outdoor unit OU and an indoor unit IU.
The outdoor unit OU includes a compressor 110, an outdoor heat exchanger 140, and a supercooler 180. The air conditioner may include one or a plurality of the outdoor units OU.
The compressor 110 compresses a refrigerant of a low temperature and low pressure into a refrigerant of a high temperature and high pressure. The compressor 110 may have various structures, and an inverter type compressor or a constant speed compressor may be adopted as the compressor 110. A discharge temperature sensor 171 and a discharge pressure sensor 151 are installed on the discharge pipe 161 of the compressor 110. Furthermore, a suction temperature sensor 175 and a suction pressure sensor 154 are installed on the suction pipe 162 of the compressor 110.
The outdoor unit OU is illustrated as including one compressor 110, but the present invention is not limited thereto. The outdoor unit OU may include a plurality of the compressors and may include both an inverter type compressor and a constant speed compressor.
An accumulator 187 may be installed in the suction pipe 162 of the compressor 110 in order to prevent a refrigerant of a liquid state from entering the compressor 110. An oil separator 113 for collecting oil from the refrigerant discharged from the compressor 110 may be installed in the discharge pipe 161 of the compressor 110.
A 4-way valve 160 is a passage switch valve for switching cooling and heating. The 4-way valve 160 guides the refrigerant compressed by the compressor 110 to the outdoor heat exchanger 140 in an air cooling operation and guides the compressed refrigerant to an indoor heat exchanger 120 in a heating operation. The 4-way valve 160 configures to state A in the air cooling operation and configures to state B in the heating operation.
The outdoor heat exchanger 140 is disposed in an outdoor space, and the refrigerant passing through the outdoor heat exchanger 140 is thermally exchanged with outdoor air at the outdoor heat exchanger 140. The outdoor heat exchanger 140 functions as a condenser in an air cooling operation and functions as an evaporator in a heating operation.
The outdoor heat exchanger 140 is coupled to a first inflow pipe 166 and then coupled to the indoor unit IU through a liquid pipe 165. The outdoor heat exchanger 140 is coupled to a second inflow pipe 167 and then coupled to the 4-way valve 160.
The supercooler 180 includes a supercooling heat exchanger 184, a second bypass pipe 181, a supercooling expansion valve 182, and a discharge pipe 185. The supercooling heat exchanger 184 is disposed on the first inflow pipe 166. In an air cooling operation, the second bypass pipe 181 functions to bypass the refrigerant discharged from the supercooling heat exchanger 184 so that the discharged refrigerant flows in the supercooling expansion valve 182.
The supercooling expansion valve 182 is disposed on the second bypass pipe 181. The supercooling expansion valve 182 lowers the pressure and temperature of a refrigerant by constricting the refrigerant of a liquid state that flows in the second bypass pipe 181 and then forces the refrigerant to flow in the supercooling heat exchanger 184. The supercooling expansion valve 182 may be various types, and a linear expansion valve may be used as the supercooling expansion valve 182 for convenience of use. A supercooling temperature sensor 183 for detecting temperature of the refrigerant constricted by the supercooling expansion valve 182 is installed on the second bypass pipe 181.
In an air cooling operation, a condensed refrigerant passing through the outdoor heat exchanger 140 is super-cooled through a thermal exchange with a refrigerant of low temperature, introduced through the second bypass pipe 181, in the supercooling heat exchanger 184, and the super-cooled refrigerant flows in the indoor unit IU.
The refrigerant passing through the second bypass pipe 181 is thermally exchanged in the supercooling heat exchanger 184, and the thermally exchanged refrigerant flows in the accumulator 187 through the discharge pipe 185. A discharge pipe temperature sensor 178 for detecting temperature of the refrigerant entering the accumulator 187 is installed on the discharge pipe 185.
A liquid pipe temperature sensor 174 and a liquid pipe pressure sensor 156 are installed on the liquid pipe 165 which couples the supercooler 180 and the indoor unit IU.
In the air conditioner according to the embodiment of the present invention, the indoor unit IU includes the indoor heat exchanger 120, an indoor fan 125, and an indoor expansion valve 131. The air conditioner may include one or a plurality of the indoor units IU.
The indoor heat exchanger 120 is disposed in an indoor space, and a refrigerant passing through the indoor heat exchanger 120 is thermally exchanged with indoor air at the indoor heat exchanger 120. The indoor heat exchanger 120 functions as an evaporator in an air cooling operation and functions as a condenser in a heating operation. An indoor temperature sensor 176 for detecting indoor temperature is installed at the indoor heat exchanger 120.
The indoor expansion valve 131 is an apparatus for constricting an inflow refrigerant in an air cooling operation. The indoor expansion valve 131 is installed in the indoor inlet pipe 163 of the indoor unit IU. The indoor expansion valve 131 may be various types, and a linear expansion valve may be used as the indoor expansion valve 131, for convenience of use. It is preferred that the indoor expansion valve 131 be opened in a set opening degree in an air cooling operation and be fully opened in a heating operation.
An indoor inlet pipe temperature sensor 173 is installed on the indoor inlet pipe 163. The indoor inlet pipe temperature sensor 173 may be installed between the indoor heat exchanger 120 and the indoor expansion valve 131. Furthermore, an indoor outlet pipe temperature sensor 172 is installed on the indoor outlet pipe 164.
In the air cooling operation of the above-described air conditioner, the flow of a refrigerant is described below.
A refrigerant of a high temperature and high pressure and a gaseous state, discharged from the compressor 110, flows into the outdoor heat exchanger 140 through the 4-way valve 160 and the second inflow pipe 167. The refrigerant is thermally exchanged with outdoor air at the outdoor heat exchanger 140, and thus condensed. The refrigerant discharged from the outdoor heat exchanger 140 flows into the supercooler 180 through the first inflow pipe 166. Next, the refrigerant is super-cooled by the supercooling heat exchanger 184, and the super-cooled refrigerant flows into the indoor unit IU.
A part of the refrigerant super-cooled by the supercooling heat exchanger 184 is constricted by the supercooling expansion valve 182, so that the refrigerant passing through the supercooling heat exchanger 184 is super-cooled. The refrigerant super-cooled by the supercooling heat exchanger 184 flows into the accumulator 187.
The refrigerant flowing into the indoor unit IU is constricted by the indoor expansion valve 131 opened in a set opening degree and is then thermally exchanged with indoor air at the indoor heat exchanger 120, thus being evaporated. The evaporated refrigerant flows into the compressor 110 through the 4-way valve 160 and the accumulator 187.
In the heating operation of the above-described air conditioner, the flow of a refrigerant is described below.
A refrigerant of a high temperature and high pressure and a gaseous state, discharged from the compressor 110, flows into the indoor unit IU through the 4-way valve 160. Here, the indoor expansion valves 131 of the indoor units IU are fully opened. The refrigerant discharged from the indoor unit IU flows into the outdoor heat exchanger 140 through the first inflow pipe 166. Next, the refrigerant is thermally exchanged with outdoor air at the outdoor heat exchanger 140, thus being evaporated. The evaporated refrigerant flows into the suction pipe 162 of the compressor 110 through the second inflow pipe 167, the 4-way valve 160, and the accumulator 187.
The outdoor heat exchanger 140 according to an embodiment of the present invention includes a first header pipe 141a configured to have a refrigerant, compressed by the compressor in an air cooling operation, to flow therein. A heat exchange unit 143 is coupled to the first header pipe 141a and is configured to thermally exchange a refrigerant with air. A bypass pipe 144 is configured to have the refrigerant, thermally exchanged in the heat exchange unit 143 in an air cooling operation, to pass therethrough. A second header pipe 141b is configured to have the refrigerant, passing through the bypass pipe 144, to flow therein in the air cooling operation and is coupled to the heat exchange unit 143. A plurality of first header branch pipes 142a is configured to couple the first header pipe 141a and the heat exchange unit 143, and a plurality of second header branch pipes 142b is configured to couple the second header pipe 141b and the heat exchange unit 143, and cross the plurality of first header branch pipes 142a.
The first header pipe 141a has one end coupled to the second inflow pipe 167, and thus is coupled to the compressor 110. The first header pipe 141a has the other end coupled to the bypass pipe 144 and the second header pipe 141b. A check valve 149 is disposed at the other end of the first header pipe 141a. The check valve 149 prevents a refrigerant from flowing from the first header pipe 141a to the second header pipe 141b, but allows a refrigerant to flow from the second header pipe 141b to the first header pipe 141a.
The first header pipe 141a is coupled to the plurality of first header branch pipes 142a. The first header pipe 141a is branched into the plurality of first header branch pipes 142a and is coupled to one end of the heat exchange unit 143.
The plurality of first header branch pipes 142a couples the first header pipe 141a and the heat exchange unit 143. The plurality of first header branch pipes 142a is branched from the first header pipe 141a and is coupled to the one end of the heat exchange unit 143. The plurality of first header branch pipes 142a is configured to cross the plurality of second header branch pipes 142b and is coupled to the one end of the heat exchange unit 143. In other words, the plurality of first header branch pipes 142a and the plurality of second header branch pipes 142b are alternately coupled to the heat exchange unit 143. The plurality of first header branch pipes 142a and the plurality of second header branch pipes 142b may be alternately coupled to the heat exchange unit 143 one by one or may be classified in groups of one or two or more and then alternately coupled to the heat exchange unit 143.
The plurality of first header branch pipes 142a and the plurality of second header branch pipes 142b are alternately coupled to one end of the heat exchange unit 143, and a plurality of first distribution branch pipes 146a and a plurality of second distribution branch pipes 146b are alternately coupled to the other end of the heat exchange unit 143. In this embodiment, the heat exchange unit 143 includes a plurality of refrigerant tubes 143a and 143b positioned parallel to each other through which a refrigerant flows and a plurality of electric heat pins. and thermally exchanges the refrigerant with air.
The plurality of first header branch pipes 142a and the plurality of second header branch pipes 142b are alternately coupled to respective refrigerant tubes such that at least two refrigerant tubes 143a coupled to the first header branch pipes 142a have at least one refrigerant tube 143b coupled to the second header branch pipe 142b therebetween. Or, the plurality of first header branch pipes 142a and the plurality of second header branch pipes 142b are alternately coupled to respective refrigerant tubes such that at least two refrigerant tubes 143b coupled to the second header branch pipes 142b have at least one refrigerant tube 143a coupled to the first header branch pipe 142a therebetween. Therebetween includes refrigerant tubes being immediately next to each other or there can be intervening refrigerant tubes.
Similarly, the plurality of first distribution branch pipes 146a and the plurality of second distribution branch pipes 146b are alternately coupled to respective refrigerant tubes such that at least two refrigerant tubes coupled to the first distribution branch pipes 146a have at least one refrigerant tube coupled to the second distribution branch pipe 146b therebetween. Or, the plurality of first distribution branch pipes 146a and the plurality of second distribution branch pipes 146b are alternately coupled to respective refrigerant tubes such that at least two refrigerant tubes coupled to the second distribution branch pipe 146b have at least one refrigerant tube coupled to the first distribution branch pipe 146a therebetween. Therebetween includes refrigerant tubes being immediately next to each other or there can be intervening refrigerant tubes.
The plurality of first header branch pipes 142a and the plurality of second header branch pipes 142b are alternately coupled to one ends of the plurality of refrigerant tubes of the heat exchange unit 143, and the plurality of first distribution branch pipes 146a and the plurality of second distribution branch pipes 146b are alternately coupled to the other end of the plurality of refrigerant tubes of the heat exchange unit 143. The refrigerant tube coupled to the first header branch pipe 142a is coupled to the first distribution branch pipe 146a, and the refrigerant tube coupled to the second header branch pipe 142b is coupled to the second distribution branch pipe 146b.
The plurality of first distribution branch pipes 146a couples a first distributor 147a and the heat exchange unit 143. The plurality of first distribution branch pipes 146a is merged into the first distributor 147a. The plurality of first distribution branch pipes 146a is coupled to the other end of the heat exchange unit 143 and is configured to cross the plurality of second distribution branch pipes 146b. In other words, the plurality of first distribution branch pipes 146a and the plurality of second distribution branch pipes 146b are alternately coupled to the heat exchange unit 143. The plurality of first distribution branch pipes 146a and the plurality of second distribution branch pipes 146b may be alternately coupled to the heat exchange unit 143 one by one or may be classified in groups of one or two or more and then alternately coupled to the heat exchange unit 143.
The first distributor 147a couples the plurality of first distribution branch pipes 146a and a first distribution pipe 148a. The plurality of first distribution branch pipes 146a is merged and coupled to the first distributor 147a. The first distributor 147a is coupled to the heat exchange unit 143 through the plurality of first distribution branch pipes 146a.
The first distribution pipe 148a is coupled to the first distributor 147a. The first distribution pipe 148a is coupled to the other end of the heat exchange unit 143 through the first distributor 147a and the plurality of first distribution branch pipes 146a.
The first distribution pipe 148a is coupled to the first inflow pipe 166. The first distribution pipe 148a and a second distribution pipe 148b are merged into the first inflow pipe 166.
A first expansion valve 132a for controlling the degree of opening of the first distribution pipe 148a is disposed in the first distribution pipe 148a. The first expansion valve 132a may constrict, bypass, or block a refrigerant passing through the first distribution pipe 148a.
The bypass pipe 144 has one end coupled to the first distribution pipe 148a and the other end coupled to the second header pipe 141b. An intermittent valve 145 is disposed in the bypass pipe 144 and is opened or closed in order to control the flow of a refrigerant. The intermittent valve 145 may be opened so that a refrigerant flows from the first distributor 147a to the second header pipe 141b and may be closed so that a refrigerant does not flow from the second header pipe 141b to the first distributor 147a.
In accordance with an embodiment, the bypass pipe 144 may be coupled to the first distributor 147a or may be coupled to the plurality of first header branch pipes 142a.
The second header pipe 141b is coupled to the bypass pipe 144 and the first header pipe 141a. The second header pipe 141b is coupled to the plurality of second header branch pipes 142b. The second header pipe 141b is branched into the plurality of second header branch pipes 142b and then coupled to one end of the heat exchange unit 143.
The plurality of second header branch pipes 142b couples the second header pipe 141b and the heat exchange unit 143. The plurality of second header branch pipes 142b is branched from the second header pipe 141b and then coupled to the one end of the heat exchange unit 143. The plurality of second header branch pipes 142b is coupled to the one end of the heat exchange unit 143 and is configured to cross the plurality of first header branch pipes 142a. That is, the plurality of second header branch pipes 142b and the plurality of first header branch pipes 142a are alternately coupled to the heat exchange unit 143. The plurality of second header branch pipes 142b and the plurality of first header branch pipes 142a may be alternately coupled to the heat exchange unit 143 one by one or may be classified in groups of one or two or more and then alternately coupled to the heat exchange unit 143.
The plurality of second distribution branch pipes 146b couples a second distributor 147b and the heat exchange unit 143. The plurality of second distribution branch pipes 146b is merged into the second distributor 147b. The plurality of second distribution branch pipes 146b is coupled to the other end of the heat exchange unit 143 and is configured to cross the plurality of first distribution branch pipes 146a. That is, the plurality of second distribution branch pipes 146b and the plurality of first distribution branch pipes 146a are alternately coupled to the heat exchange unit 143. The plurality of second distribution branch pipes 146b and the plurality of first distribution branch pipes 146a may be alternately coupled to the heat exchange unit 143 one by one or may be classified in groups of one or two or more and then alternately coupled to the heat exchange unit 143.
The second distributor 147b couples the plurality of second distribution branch pipes 146b and the second distribution pipe 148b. The plurality of second distribution branch pipes 146b is merged and coupled to the second distributor 147b. The second distributor 147b is coupled to the heat exchange unit 143 through the plurality of second distribution branch pipes 146b.
The second distribution pipe 148b is coupled to the second distributor 147b. The second distribution pipe 148b is coupled to the other end of the heat exchange unit 143 through the second distributor 147b and the plurality of second distribution branch pipes 146b.
The second distribution pipe 148b is coupled to the first inflow pipe 166. The second distribution pipe 148b and the first distribution pipe 148a are merged into the first inflow pipe 166.
A second expansion valve 132b for controlling the degree of opening of the second distribution pipe 148b is disposed in the second distribution pipe 148b. The second expansion valve 132b may constrict, bypass, or block a refrigerant passing through the second distribution pipe 148b.
The flow of a refrigerant in the air cooling operation of the above-described outdoor heat exchanger is described below with reference to
A refrigerant compressed by the compressor 110 flows into the first header pipe 141a through the second inflow pipe 167. The check valve 149 prevents the refrigerant, flowing into the first header pipe 141a, from flowing into the second header pipe 141b. The refrigerant flowing into the first header pipe 141a flows into the heat exchange unit 143 through the plurality of first header branch pipes 142a.
The refrigerant flowing into the heat exchange unit 143 is thermally exchanged with air, thus being condensed. The refrigerant condensed by the heat exchange unit 143 flows into the plurality of first distribution branch pipes 146a and then flows into the first distribution pipe 148a via the first distributor 147a. In the air cooling operation, the first expansion valve 132a is closed. Thus, the refrigerant flowing into the first distribution pipe 148a does not flow into the first inflow pipe 166, but flows into the bypass pipe 144.
The refrigerant passing through the bypass pipe 144 flows into the second header pipe 141b. The refrigerant flowing into the second header pipe 141b flows into the heat exchange unit 143 through the plurality of second header branch pipes 142b.
The refrigerant flowing into the heat exchange unit 143 is condensed again through a thermal exchange with air. Here, since the plurality of second header branch pipes 142b and the plurality of first header branch pipes 142a are alternately coupled to the heat exchange unit 143, the refrigerants flowing from the plurality of second header branch pipes 142b to the heat exchange unit 143 flow between the refrigerants flowing from the plurality of first header branch pipes 142a to the heat exchange unit 143.
The refrigerant condensed by the heat exchange unit 143 flows into the plurality of second distribution branch pipes 146b and then flows into the second distribution pipe 148b via the second distributor 147b. In the air cooling operation, the second expansion valve 132b is fully opened. Thus, the refrigerant flowing into the second distribution pipe 148b flows into the first inflow pipe 166 and then flows into the indoor unit IU through the liquid pipe 165.
The flow of the refrigerant in the heating operation of the above-described outdoor heat exchanger is described below with reference to
A refrigerant condensed by the indoor heat exchanger 120 of the indoor unit IU flows into the first inflow pipe 166 through the liquid pipe 165. The refrigerant flowing into the first inflow pipe 166 flows into the first distribution pipe 148a and the second distribution pipe 148b.
The refrigerant flowing into the second distribution pipe 148b is expanded by the second expansion valve 132b whose degree of opening is controlled. The refrigerant expanded by the second expansion valve 132b flows into the heat exchange unit 143 through the second distributor 147b and the plurality of second distribution branch pipes 146b.
The refrigerant flowed into the heat exchange unit 143 is thermally exchanged with air, thus being evaporated. The refrigerant evaporated by the heat exchange unit 143 flows into the second header pipe 141b via the second header branch pipe 142b.
In the heating operation, the intermittent valve 145 is closed, and thus the refrigerant flowing into the second header pipe 141b does not pass through the bypass pipe 144. The refrigerant flowing into the second header pipe 141b flows into the first header pipe 141a.
Meanwhile, the refrigerant flowing into the first distribution pipe 148a does not flow into the second header pipe 141b because the intermittent valve 145 is closed in the heating operation. Accordingly, the refrigerant flowing into the first distribution pipe 148a is expanded by the first expansion valve 132a whose degree of opening is controlled. The refrigerant expanded by the first expansion valve 132a flows into the plurality of first distribution branch pipes 146a via the first distributor 147a.
The refrigerant flowing into first distribution branch pipes 146a flows into the heat exchange unit 143. The refrigerant flowing into the heat exchange unit 143 is thermally exchanged with air, and thus evaporated.
The plurality of second distribution branch pipes 146b and the plurality of first distribution branch pipes 146a are alternately coupled to the heat exchange unit 143. Accordingly, the refrigerants flowing from the plurality of second distribution branch pipes 146b to the heat exchange unit 143 flow between the refrigerants flowing from the plurality of first distribution branch pipes 146a to the heat exchange unit 143.
The refrigerant evaporated by the heat exchange unit 143 flows into the first header pipe 141a through the plurality of first header branch pipes 142a. The refrigerant flowing into the first header pipe 141a is merged with the refrigerant passing through the second header pipe 141b. Next, the merged refrigerant flows into the second inflow pipe 167, and then into the compressor 110.
In the heating operation, the generation of frost is not concentrated on a part of the heat exchange unit 143 because the refrigerant passing through the plurality of first distribution branch pipes 146a from the heat exchange unit 143 and the refrigerant passing through the plurality of second distribution branch pipes 146b from the heat exchange unit 143 sequentially pass within the heat exchange unit 143.
Furthermore, in a defrosting operation for operating a cooling cycle in order to remove frost when the frost is generated, frost generated in the heat exchange unit 143 may be uniformly removed because the refrigerant passing through the plurality of first header branch pipes 142a from the heat exchange unit 143 and the refrigerant passing through the plurality of second header branch pipes 142b from the heat exchange unit 143 sequentially pass within the heat exchange unit 143.
The outdoor heat exchanger according to embodiments of the present invention has one or more of the following advantages.
First, there is an advantage in that the generation of frost is not concentrated on the variable heat exchanger in which condensation is performed twice in an air cooling operation because refrigerants flowing through different paths uniformly pass through the heat exchanger in a heating operation.
Second, there is an advantage in that frost may be uniformly removed because refrigerants flowing through different paths uniformly pass through the heat exchanger in a defrosting operation.
Effects of the embodiments of the present invention are not limited to the above-mentioned effects, and other effects that have not been described above will be evident to those skilled in the art from the following description.
The heat exchanger may be used in residential air conditioners, commercial air conditioners, and vehicles, such as cars and trucks. Vehicles such as electric cars and hybrid cars may take advantage of the air conditioners using the heat exchanger.
Furthermore, although the preferred embodiments of the present invention have been illustrated and described, the present invention is not limited to the above specific embodiments, and a person having ordinary skill in the art to which the invention belongs may modify the embodiments in various ways without departing from the gist of the claims. The modified embodiments should not be interpreted individually from the technical spirit or prospect of the present invention.
| Number | Date | Country | Kind |
|---|---|---|---|
| 10-2012-0006965 | Jan 2012 | KR | national |
| Number | Name | Date | Kind |
|---|---|---|---|
| 4389851 | Chrostowski | Jun 1983 | A |
| 4535838 | Gray | Aug 1985 | A |
| 5806585 | Yoshida | Sep 1998 | A |
| 6230506 | Nishida et al. | May 2001 | B1 |
| 6257014 | Jao | Jul 2001 | B1 |
| 7353664 | Kim | Apr 2008 | B2 |
| 20090019872 | Kotani et al. | Jan 2009 | A1 |
| 20090019884 | Sekine et al. | Jan 2009 | A1 |
| 20100051229 | Choi et al. | Mar 2010 | A1 |
| 20100095701 | Strunk et al. | Apr 2010 | A1 |
| 20100293980 | Shimaoka | Nov 2010 | A1 |
| 20110138839 | Lee | Jun 2011 | A1 |
| Number | Date | Country |
|---|---|---|
| 2003 121019 | Apr 2003 | JP |
| 2003121019 | Apr 2003 | JP |
| 2010-234945 | Oct 2010 | JP |
| 2010 234945 | Oct 2010 | JP |
| 2010-0115001 | Nov 2010 | KR |
| 2010008960 | Jan 2010 | WO |
| Number | Date | Country | |
|---|---|---|---|
| 20130192809 A1 | Aug 2013 | US |
