Patent Application
20240271839
The present disclosure relates to a refrigerator for defrosting an evaporator using a refrigerant or a heating source.
In general, a refrigerator is a home appliance provided to store various foods for a long period of time using cold air generated by circulating refrigerant through a refrigeration cycle.
The refrigerator may be provided with one or more storage compartments partitioned from each other to store a storage (e.g. food, beverage, etc.). The storage compartment is supplied with cold air generated by a refrigeration system consisting of a compressor, condenser, expansion valve, and evaporator, and is maintained within a set temperature range.
As the refrigerator operates, the cold air circulating in each storage compartment passes through the evaporator, and in this process, the moisture contained in the cold air is condensed on the surface of the evaporator, thereby creating frost.
The frost formed on the surface of the evaporator gradually accumulates and affects the flow of cold air passing through the evaporator. This means that the heat exchange efficiency is degraded as the flow of cold air passing through the evaporator is reduced in proportion to the amount of frost.
In the related art, when a predetermined time elapses after operation of the refrigerator or a condition for the defrosting operation is satisfied, an operation (defrosting operation) for defrosting the evaporator is performed.
The defrosting operation is performed by using one or more heating sources installed in the corresponding evaporator.
When the defrosting operation is performed by the heating source, a cooling operation for each storage compartment is stopped.
However, using only the heating source to defrost, it takes a lot of time and energy to cool down with each storage compartment to a set temperature after the defrosting operation is complete.
In particular, the defrosting method using the heating source does not deforest evenly and therefore requires more heating than necessary, resulting in an increase in a storage compartment temperature that affects the food stored in the compartment.
Accordingly, in the related art, a hot gas defrosting method using a high-temperature refrigerant (hot gas) passing through a compressor is additionally provided, thereby reducing defrosting time and minimizing an increase in a storage compartment temperature during the defrosting operation. This is described in Korean Patent Publication No. 10-2010-0034442 (related art 1).
However, in the above-described related art 1, as the hot gas defrosting and the heater defrosting are selectively performed according to a room temperature outside of a refrigerator, there is still a problem in the defrosting operation using only the heating source.
In particular, in the related art 1, the hot gas discharged from a compressor flows directly to an evaporator without passing through an expansion valve, then defrosts the evaporator and then returns to the compressor. As a result, the refrigerant does not sufficiently expand, so there is s a problem in that the liquefied refrigerant (hot gas) does not circulate sufficiently inside the evaporator and remains in the tube.
In addition, the technology of related art 1 is applied only to refrigerators that perform cooling operations for one evaporator with one compressor, and could not be applied to refrigerators that perform cooling operations for two or more evaporators with one compressor.
Meanwhile, recently, a defrosting technology using hot gas has been provided in a refrigerator that performs a cooling operation for the two evaporators with one compressor. This is as presented in Korean Patent Publication No. 10-2017-0013766 (Related art 2) and Korean Patent Publication No. 10-2017-0013767 (Related art 3).
However, as the technologies of Related art 2 and Related art 3 described above used only hot gas to defrost the evaporator, power consumption is reduced, but the defrosting time is not significantly reduced compared to the method using a heating source.
In addition, in the related art 2 and related art 3, when the hot gas that has passed through one evaporator is introduced into the other evaporator of the other storage compartment, it passes through the other evaporator expansion valve of the other storage compartment. Accordingly, there is a problem in that it is difficult to control the amount of refrigerant introduced into the evaporator of the other storage compartment.
In other words, the refrigerant that flows directly through the condenser into the evaporator of the other storage compartment and the refrigerant that flows into the evaporator of the other storage compartment after passing through the condenser and one evaporator are at different pressures and temperatures. For this reason, there is inevitably a difference in heat exchange performance due to a difference in decompression when passing through the same expansion valve.
Meanwhile, the heating source may include a sheath heater using radiant heat or a cord heater in contact with the outer surface of a heat exchange fin.
In particular, the sheath heater and the cord heater are provided together to improve defrost efficiency and shorten the defrost operation time. This is as described in Korean Patent Publication No. 10-2001-0047410 (Related art 4), Korean Patent Publication No. 10-2018-0011691 (Related art 5).
However, the defrosting method using only a heating source using electricity as in Related art 4 and Related art 5, requires a significant time to lower each storage compartment to a set temperature after the completion of the defrosting operation, and has a disadvantage in that power consumption is severe.
One object of the present disclosure is to simultaneously apply a heat conduction method using a high-temperature refrigerant and a radiant heat method using a heating source to defrost an evaporator, thereby reducing the defrost operation time.
Another object of the present disclosure is to improve power efficiency by allowing heat generated from a heating source to be conducted through a flow path through which a high-temperature refrigerant flows.
Another object of the present disclosure is to enable the entire portion of the evaporator to be evenly defrosted by being re-heated by the heating source even when the temperature of the refrigerant decreases during defrosting of the evaporator by the high-temperature refrigerant.
Another object of the present disclosure is to shorten an operation time for providing heat to a first evaporator, thereby reducing an increase in the internal temperature of a storage compartment due to the provision of heat.
Another object of the present disclosure is to minimize power consumption for a heat supply operation, so that power consumption may be improved.
Another object of the present disclosure is to enable the internal temperature of the storage compartment, which has been raised due to the defrosting of the evaporator, to be rapidly cooled to a set temperature range.
According to a refrigerator of the present disclosure, a hot gas flow path and a heating source may be provided together to selectively supply heat to a portion requiring heat.
According to the refrigerator of the present disclosure, the hot gas flow path may receive heat from the heating source by a heat transfer member. Accordingly, even if the temperature of the hot gas flow path decreases while passing through an evaporator during a defrost operation, the defrost effect may be further improved by reheating.
According to the refrigerator of the present disclosure, the hot gas flow path may be provided separately from a refrigerant flow path passing through an expansion valve and the evaporator from a condenser.
According to the refrigerator of the present disclosure, the hot gas flow path may be formed to guide a flow of the refrigerant returned to a compressor through the evaporator without passing through the expansion valve from the condenser.
According to the refrigerator of the present disclosure, the heat transfer member may be in contact with the heating source.
According to the refrigerator of the present disclosure, the heat transfer member may be in contact with the hot gas flow path.
According to the refrigerator of the present disclosure, the heating source may be configured as a sheath heater.
According to the refrigerator of the present disclosure, the heat transfer member may be formed of a metal plate.
According to the refrigerator of the present disclosure, one end of the heat transfer member may be formed to be in surface contact with the heating source while surrounding at least a portion of the heating source.
According to the refrigerator of the present disclosure, the other end of the heat transfer member may be formed to be in surface contact with the hot gas flow path while surrounding at least a portion of the hot gas flow path.
According to the refrigerator of the present disclosure, the heat transfer member may be formed to be rounded or bent from a contact portion with the heating source to a contact portion with the hot gas flow path.
According to the refrigerator of the present disclosure, a plurality of heat transfer members may be provided.
According to the refrigerator of the present disclosure, a hot gas inlet side of the hot gas flow path may be connected to a side of the evaporator farthest from the heating source.
According to the refrigerator of the present disclosure, a hot gas outlet side of the hot gas flow path may be connected to a side of the evaporator farthest from the heating source.
According to the refrigerator of the present disclosure, the hot gas inlet side and the hot gas outlet side of the hot gas flow path may be located at a portion opposite to the portion where the heating source is located in the evaporator.
According to the refrigerator of the present disclosure, at least a portion of the hot gas flow path may be configured to pass through an adjacent portion of the heating source.
According to the refrigerator of the present disclosure, the hot gas flow path may be formed to sequentially penetrate from heat exchange fins in the uppermost row to the heat exchange fins in the lowest row, which form the evaporator.
According to the refrigerator of the present disclosure, the hot gas flow path may include a first path for guiding the introduced refrigerant (hot gas) to flow through a portion of the evaporator.
According to the refrigerator of the present disclosure, the hot gas flow path may include a third path for guiding the outflow of the refrigerant flowing through the other part of the evaporator.
According to the refrigerator of the present disclosure, the hot gas flow path may include a third path, which is connected to the first path and the second path.
According to the refrigerator of the present disclosure, the second path of the hot gas flow path may be formed to sequentially pass through the heat exchange fins in the lowest row.
According to the refrigerator of the present disclosure, the heating source may be located at the bottom of the second path forming the hot gas flow path.
According to the refrigerator of the present disclosure, the heat transfer member may be configured to connect the second path forming the hot gas flow path and the heating source.
According to the refrigerator of the present disclosure, a physical property adjustment part may be provided on a flow path of the refrigerant flowing to a second evaporator through the first evaporator. Accordingly, a physical property of the refrigerant flowing into the second evaporator may be maintained constant.
According to the refrigerator of the present disclosure, resistance of a second expansion valve for decompressing the refrigerant flowing into the second evaporator and resistance of the physical property adjustment part may be different from each other. Accordingly, it is possible to reduce the difference in physical properties between the refrigerant flowing into the second evaporator through the first evaporator and the refrigerant flowing directly to the second evaporator without passing through the first evaporator.
According to the refrigerator of the present disclosure, a flow path switching valve may be included to switch a flow path such that the refrigerant flows from a discharge flow path to at least one of a first refrigerant flow path, a second refrigerant flow path, or the hot gas flow path.
According to the refrigerator of the present disclosure, the hot gas flow path may include a first path from the flow path switching valve to the first evaporator.
According to the refrigerator of the present disclosure, the hot gas flow path may include a second path from the first path to the physical property adjustment part via the first evaporator.
According to the refrigerator of the present disclosure, the first path of the hot gas flow path may be formed to have the same diameter as the flow path from a condenser to the flow path switching valve.
According to the refrigerator of the present disclosure, the second path of the hot gas flow path may be formed to have a larger diameter than the first path.
According to the refrigerator of the present disclosure, the second path of the hot gas flow path may be formed to have a smaller diameter than that of the flow path passing through the first evaporator of the first refrigerant flow path.
According to the refrigerator of the present disclosure, the physical property adjustment part may have a different resistance from the second expansion valve by having a different length.
According to the refrigerator of the present disclosure, the length of the physical property adjustment part may be shorter than that of the second expansion valve, such that the resistance of the physical property adjustment part may be smaller than the resistance of the second expansion valve.
According to the refrigerator of the present disclosure, the physical property adjustment part may be formed to have different resistance by varying the tube diameter from the second expansion valve.
According to the refrigerator of the present disclosure, the tube diameter of the physical property adjustment part may be formed to be larger than the diameter of the second expansion valve, such that the resistance of the property value adjustment part may be smaller than the resistance of the second expansion valve.
According to the refrigerator of the present disclosure, the second path of the hot gas flow path may be formed to pass through the heating source.
According to the refrigerator of the present disclosure, the second path of the hot gas flow path may be connected to heat with hot gas a side of the first evaporator away from the heating source.
According to the refrigerator of the present disclosure, the heating source may be located at any one side of the first evaporator.
According to the refrigerator of the present disclosure, the second path of the hot gas flow path may be formed such that a hot gas inlet side is positioned on the opposite side to where the heating source is located in the first evaporator.
According to the refrigerator of the present disclosure, at least a portion of the second path of the hot gas flow path may be formed to be heated while passing through an adjacent portion of the heating source.
According to the refrigerator of the present disclosure, the second path of the hot gas flow path may be formed such that a hot gas outlet side is positioned on the opposite side to where the heating source is located.
According to the refrigerator of the present disclosure, the second path of the hot gas flow path may be formed such that hot gas flows out of the first evaporator through the heating source to a side away from the heating source in the first evaporator.
According to the refrigerator of the present disclosure, the first evaporator may be configured such that a portion through which the hot gas flows into the second path of the hot gas flow path is heated faster than a portion adjacent to the heating source during the defrosting operation.
According to the refrigerator of the present disclosure, the heating source may be provided at a lower portion of the first evaporator.
According to the refrigerator of the present disclosure, the second path may be connected to be in contact while passing through each heat exchange fin of the first evaporator.
According to the refrigerator of the present disclosure, when the first evaporator is defrosted, the flow path switching valve may be operated such that the refrigerant passing through the condenser may pass through the hot gas flow path.
In the refrigerator of the present disclosure, heat of a heating source and heat from a hot gas flow path through which a high-temperature refrigerant (hot gas) flows may be provided together. Thus, heat may be sufficiently supplied to a place where heat is required.
In the refrigerator of the present disclosure, since a defrosting operation is performed while the heating source and the hot gas are used together, the time for the defrosting operation is shortened, and the power consumption for the defrosting operation is reduced.
According to the refrigerator of the present disclosure, since the hot gas flow path is reheated with the heat generated by the heating source by using a heat transfer member, heat for defrosting may be sufficiently provided until the hot gas passes completely through an evaporator.
In the refrigerator of the present disclosure, since the heat transfer member is bendable, the heat transfer member may be stably coupled even if a gap between the hot gas flow path and the heating source is different from a designed interval.
In the refrigerator of the present disclosure, since the heat transfer member is in surface contact with the heating source, the heat transfer member may receive sufficient heat from the heating source.
In the refrigerator of the present disclosure, since the heat transfer member is in surface contact with the hot gas flow path, the heat transfer member may conduct sufficient heat to the hot gas flow path.
In the refrigerator of the present disclosure, since the heat transfer member is connected to a connecting side path of the hot gas flow path, the refrigerant of which the temperature is lowered while passing through the evaporator may be re-heated.
In the refrigerator of the present disclosure, since the hot gas used for defrosting a first evaporator is configured to pass through a second evaporator, it is possible to perform a cooling operation of a second storage compartment in spite of the defrosting operation of the first evaporator. In addition, after the defrosting operation, only the cooling operation of the first storage compartment needs to be performed, thereby reducing power consumption.
In the refrigerator of the present disclosure, after the hot gas used for defrosting the first evaporator passes through the first evaporator, the physical property of the refrigerant is adjusted in a physical property adjustment part. Accordingly, heat exchange defects in the second evaporator due to the refrigerant provided to the second evaporator during the defrosting operation of the first evaporator are prevented.
In the refrigerator of the present disclosure, since a second path of the hot gas flow path for defrosting the first evaporator heats the first evaporator from a place far from the heating source, defrosting is performed evenly over all parts of the first evaporator.
In the refrigerator of the present disclosure, since the second path of the hot gas flow path is formed to be heated while passing through an adjacent portion of the heating source, heat for defrosting is sufficiently provided to a refrigerant outlet side of the second path.
In the refrigerator of the present disclosure, since the second path of the hot gas flow path is configured to heat from the upper end of the first evaporator where frost is most likely to occur, defrost defects in which frost remains after the defrosting operation are prevented.
Hereinafter, a preferred embodiment of a refrigerator of the present disclosure will be described with reference to
Before describing the embodiment, each direction referred to in the description of the installation position of each component will be, for example, an installation state during actual use (the same state as in the illustrated embodiment).
The accompanying
As shown in these drawings, the refrigerator according to the embodiment of the present disclosure provides a heating source 310 and a hot gas to selectively supply heat to a portion where heat is required.
In the refrigerator according to the embodiment of the present disclosure, a hot gas flow path 320 through which a high-temperature refrigerant (hot gas) flows may be heated by the heating source 310. Accordingly, it is possible to provide sufficient heat until the high-temperature refrigerant flowing along the hot gas flow path 320 completely passes through a first evaporator 240.
The refrigerator according to the embodiment of the present disclosure will be described in more detail according to each configuration.
First, the refrigerator according to the embodiment of the present disclosure may include a refrigerator main body 100 providing at least one storage compartment.
The storage compartment may include a first storage compartment 101 and a second storage compartment 102 as a storage space for storing stored objects. Each of the first storage compartment 101 and the second storage compartment 102 may be provided one by one, or at least one of the first storage compartment 101 and the second storage compartment 102 may be provided in plural.
The first storage compartment 101 and the second storage compartment 102 may be opened and closed by a first door 110 and a second door 120, respectively. Each of the first door 110 and the second door 120 may be provided one by one, or two or more of the first door 110 and the second door 120 may be provided.
The first storage compartment 101 may be maintained at a first set reference temperature (NT1). The first set reference temperature (NT1) may be a temperature at which a stored object may be frozen. For example, the first set reference temperature (NT1) may be set to a temperature equal to or less than 0° C. and equal to or higher than −24° C.
The first set reference temperature (NT1) may be set by a user. When the user does not set the first set reference temperature (NT1), a predetermined temperature may be used as the first set reference temperature (NT1).
The second storage compartment 102 may be maintained at a second set reference temperature (NT2). The second set reference temperature (NT2) may be a temperature different from the first set reference temperature (NT1). Thus, the second storage compartment 102 is maintained at a different temperature range from that of the first storage compartment 101.
The second set reference temperature (NT2) may be in a higher temperature range than the first set reference temperature (NT1). The second set reference temperature (NT2) may be a temperature at which the stored object is not frozen. For example, the second set reference temperature (NT2) may be a temperature of 32° C. or less and above 0° C. The second set reference temperature NT2 may be set higher than 32° C., 0° C., or lower than 0° C., as necessary (e.g., depending on a room temperature outside the refrigerator or the type of stored object, etc.).
Each of the storage compartments 101 and 102 continues to supply cold air according to an upper limit temperature or a lower limit temperature of each of the set reference temperatures (NT1, NT2). For example, when the temperature of the storage compartment 101, 102 exceeds the upper limit reference temperature (NT1+Diff, NT2+Diff), cold air is controlled to be supplied to the storage compartments 101 and 102. When the temperature of the storage compartments 101, 102 is lower than the lower limit reference temperature (NT1-Diff, NT2-Diff), the supply of cold air is controlled to stop. Accordingly, each of the storage compartments 101 and 102 may be maintained at each set reference temperature (NT1, NT2).
The refrigerator of the present disclosure includes a refrigeration system.
The first storage compartment 101 may be maintained at the first set reference temperature (NT1) by the refrigeration system.
Hereinafter, the refrigeration system of the first embodiment will be described.
The refrigeration system of the first embodiment may include a compressor 210 that compresses a refrigerant. The compressor 210 may be disposed in a machine room 103 in the refrigerator main body 100.
The refrigeration system of the first embodiment may include a condenser 220 in which the refrigerant is condensed. The condenser 220 may be disposed in the machine room 103 in the refrigerator main body 100.
A cooling fan 221 may be disposed adjacent to the condenser 220. For example, the cooling fan 221 may be provided in the machine room 103. The refrigerant passing through the inside of the condenser 220 by the cooling fan 221 may exchange heat with air passing through the outside of the condenser 220. When the cooling fan 221 is not operated, the refrigerant passing through the condenser 220 is maintained at a high temperature and is discharged to a discharge flow path 222.
The discharge flow path 222 is provided to guide the flow of the refrigerant passing through the condenser 220.
The refrigeration system of the first embodiment may include a first expansion valve 231 that decompresses and expands the refrigerant flowing to a first evaporator 240 through the condenser 220.
The refrigeration system of the first embodiment may include a first evaporator 240 that exchanges heat between a refrigerant and air in the refrigerator.
The refrigerant decompressed in the first expansion valve 231 and the air (cold air) flowing in the first storage compartment 101 are heat-exchanged with each other in the first evaporator 240.
The first evaporator 240 may be located in the first storage compartment 101. Although not shown, the first evaporator 240 may be located at a portion other than the first storage compartment 101.
The first evaporator 240 may exchange heat between the air flowing by the driving of a first storage compartment blowing fan 281.
The first evaporator 240 includes a heat exchange fin 241 and refrigerant tubes 242a and 242b through which the refrigerant flow is guided while passing through the heat exchange fin 241.
The heat exchange fin 241 may comprise a plurality of rows vertically spaced apart from each other. For example, as shown in the drawings, the heat exchange fins 241 may be arranged in six rows. That is, the uppermost first row of heat exchange fins 241 and the lowest sixth row of the heat exchange fins 241 may be sequentially arranged for each column.
The refrigerant tubes 242a and 242b may be formed to sequentially pass through the heat exchange fins 241 of each row and then be discharged.
The refrigerant tubes 242a, 242b include an inlet-side refrigerant tube 242a located on one side and an outlet-side refrigerant tube 242b located on the other side when viewed from the heat exchange fins 241 in each row.
The inlet-side refrigerant tube 242a may be formed to sequentially pass through in a zigzag pattern from heat exchange fins 241 in one row (e.g., uppermost row) to heat exchange fins 241 in another row (e.g., lowest row). The outlet-side refrigerant tube 242b may be formed to sequentially pass through the heat exchange fins 241 in any one row in a zigzag pattern while being bent in reverse after passing through the heat exchange fins 241 in the other row. The inlet-side refrigerant tube 242a and the outlet-side refrigerant tube 242b are connected to each other at the heat exchange fins 241 in the other row.
That is, the refrigerant may sequentially exchange heat from the heat exchange fins 241 of the uppermost row to the heat exchange fins 241 of the lowest row, and may continue to be heat-exchanged until reaching the heat exchange fins 241 in the uppermost row, and then be discharged.
The refrigeration system of the first embodiment may include a first refrigerant flow path 201.
The first refrigerant flow path 201 is connected to the discharge flow path 222 to guide the flow of the refrigerant provided to the first evaporator 240 through the first expansion valve 231.
The first refrigerant flow path 201 is connected to the inlet side refrigerant tube 242a and the outlet side refrigerant tube 242b of the first evaporator 240. Accordingly, the flow of the refrigerant flowing into the first evaporator 240 is guided by the first refrigerant flow path 201, and the flow of the refrigerant discharged from the first evaporator 240 is guided by the first refrigerant flow path 201. A portion of the first refrigerant flow path 201 may be formed as the inlet-side refrigerant tube 242a of the first evaporator 240 or the outlet-side refrigerant tube 242b.
The refrigerator according to the embodiment of the present disclosure may include a heating source 310.
The heating source 310 may be a heat source that provides high-temperature heat.
The heating source 310 may be used to supply heat for defrosting the first evaporator 240. That is, the heating source 310 may be provided as a defrosting heater that generates heat so as to defrost frost formed on the surface of the first evaporator 240 (the surface of each heat exchange fin and the surface of the refrigerant tube).
The heating source 310 may be provided as a heater other than the defrosting heater. For example, the heating source 310 may be provided as a heater used to supply heat to prevent a gasket provided to the doors 110 and 120 from freezing or may be provided as a heater used to remove ice.
The heating source 310 may be disposed adjacent to any one side of the first evaporator 240.
For example, the heating source 310 may be disposed at the bottom of the heat exchange fin 241 in the lowest row forming the first evaporator 240. The heating source 310 may be spaced apart from the heat exchange fin 241 in the lowest row of the first evaporator 240. Accordingly, the heat generated by the heating of the heating source 310 may flow upward to heat the first evaporator 240.
The heating source 310 may be integrally formed with the first evaporator 240. That is, at least one side portion of the heating source 310 may be installed on at least one side plate 243 of two side plates 243 on both sides for supporting the refrigerant tubes 242a and 242b. Although not shown, the heating source 310 may be configured separately from the first evaporator 240.
The heating source 310 may be configured as a sheath heater which is heated by power supply. Accordingly, the first evaporator 240 may remove frost (or freezing) by the radiant heat of the heating source 310.
The refrigeration system of the first embodiment may include a hot gas flow path 320.
The hot gas flow path 320 may be provided as a heat source for supplying high-temperature heat together with the heating source 310.
The hot gas flow path 320 guides the high-temperature refrigerant (hot gas) (not heat-exchanged) that has passed through the condenser 220. That is, the hot gas (high-temperature refrigerant) guided by the hot gas flow path 320 provides high-temperature heat.
The hot gas flow path 320 is formed to guide the refrigerant flow separately from the first refrigerant flow path 201. The hot gas flow path 231 may be formed such that hot gas (high-temperature refrigerant) guided to the discharge flow path 222 through the condenser 220 is provided to the first evaporator 240 without passing through the first expansion valve 231 and then returned to the compressor 210 through the first evaporator 240.
The hot gas flow path 320 may be branched from the first refrigerant flow path 201.
The refrigeration system of the first embodiment may be provided with a flow path switching valve 330.
The flow path switching valve 330 is provided at a branch portion of the hot gas flow path 320. That is, the refrigerant passing through the discharge flow path 222 by the operation of the flow path switching valve 330 is provided to the first evaporator 240 through the first expansion valve 231 through the first refrigerant flow path 201 or is provided to the first evaporator 240 through the hot gas flow path 320 without passing through the first expansion valve 231.
Only one flow path switching valve 330 may be provided or two or more flow path switching valves 330 may be provided.
When only one flow path switching valve 330 is provided, for example, the flow path switching valve 330 may be formed as a multi-directional valve such as a four-way valve.
When two or more flow path switching valves 330 are provided, for example, the flow path switching valve 330 may be formed as a three-way valve or a check valve.
A portion of the hot gas flow path 320 passing through the first evaporator 240 may be formed in a zigzag structure from one side of the first evaporator 240 via the other side to any one side of the first evaporator 240. As a result, the hot gas (high-temperature refrigerant) flowing along the hot gas flow path 320 may affect the entire portion of the first evaporator 240.
The hot gas flow path 320 may include a first path 321 for guiding the flow of the hot gas (high-temperature refrigerant) flowing into the first evaporator 240.
The hot gas flow path 320 may include a second path 322 passing through the heat exchange fins 241 of the first evaporator 240.
The hot gas flow path 320 may include a third path 323 for guiding the flow of hot gas (high-temperature refrigerant) passing through the second path 322.
The second path 322 may include an inlet side path 322a for guiding the hot gas (high-temperature refrigerant) provided from the first path 321 to flow from any one side (e.g. the upper side in the drawing) of the first evaporator 240 to the other side (e.g. the lower side in the drawing) of the first evaporator 240. For example, the inlet side path 322a guides a hot gas (high temperature refrigerant) from an upper side to a lower side of the first evaporator 240.
The second path 322 may include an outlet side path 322b for guiding the hot gas (high-temperature refrigerant) 321 to flow from any one side (e.g. the lower side in the drawing) of the first evaporator 240 to the other side (e.g. the upper side in the drawing) of the first evaporator 240. For example, the outlet path 322b guides a hot gas (high-temperature refrigerant) from a lower side to an upper side of the first evaporator 240.
The second path 322 may include a connecting side path 322c to which the inlet side path 322a and the outlet side path 322b are connected. The connecting side path 322c may be disposed at the other side of the first evaporator 240.
The second path 322 may be heated by receiving heat from the heating source 310. In particular, the connecting side path 322c of the second path 322 may be heated by receiving heat from the heating source 310.
For this purpose, the connecting side path 322c may pass through an adjacent portion of the heating source 310. For example, the connecting side path 322c of the second path 322 may be configured to pass sequentially through the heat exchange fins 241 of the lowest row (6th column) of the first evaporator 240. Accordingly, the connecting side path 322c may be heated by the heating source 310 located adjacent to the lowest row of the first evaporator 240.
Since the connecting side path 322c may be heated by the heating source 310, even if the temperature of the hot gas (high-temperature refrigerant) is lowered in the process of passing through the inlet side path 322a, the temperature may be increased again before being provided to the outlet side path 322b. Accordingly, hot gas flowing along the outlet path 322b may also provide heat required for defrosting the first evaporator 240.
A refrigerant inlet of the inlet side path 322a may be positioned at an opposite side of a portion of the first evaporator 240 where the heating source 310 is located. That is, the refrigerant of the hottest temperature is introduced into the portion of the first evaporator 240 that is least affected by the heating source 310.
A refrigerant outlet of the outlet side path 322b may be positioned at an opposite side of a portion of the first evaporator 240 where the heating source 310 is located. For example, the refrigerant outlet of the outlet side path 322b may be located at a side portion of the refrigerant inlet of the inlet side path 322a. That is, the hot gas is introduced from the heat exchange fin 241 located at the end of the first row, and the hot gas is finally discharged from the heat exchange fin 241 (located at the end of the first row).
The second path 322 of the hot gas flow path 320 may be coupled to pass through the heat exchange fins 241 and then contact each of the heat exchange fins 241 through an expansion process. That is, the second path 322 of the hot gas flow path 320 may defrost the heat exchange fins 241 through thermal conduction.
The second path 322 may be located between the inlet side refrigerant tube 242a and the outlet side refrigerant tube 242b among the heat exchange fins 241 of each row constituting the first evaporator 240. That is, as shown in
Accordingly, the hot gas flowing along the second path 322 may be evenly conducted to the entire portion of the first evaporator 240.
Although not shown, the second path 322 may be provided outside the refrigerant tubes 242a and 242b of the first evaporator 240. That is, the second path 322 may be intensively provided at a portion where a larger amount of frost is formed than the other portion of the first evaporator 240 (for example, a refrigerant inlet side portion of the refrigerant tube), or the hot gas inlet side of the second path 322 may be disposed at a portion where a larger amount of frost is formed in the first evaporator 240.
Meanwhile, the first path 321 and the third path 323 may be formed to have the same diameter as the discharge flow path 222 from the condenser 220 to the flow path switching valve 330. Accordingly, it is possible to share the discharge flow path 222, the first path 321, and the third path 323.
The second path 322 may be formed to have a larger diameter than the first path 321. Accordingly, the hot gas passing through the second path 322 may be sufficiently thermally conductive to the first evaporator 240.
The second path 322 may be formed to have a diameter smaller than that of the refrigerant tubes 242a and 242b passing through the first evaporator 240 among the first refrigerant flow path 201. That is, the refrigerant tubes 242a and 242b of the first evaporator 240 are formed to have a larger diameter than the second path 322, thereby providing higher heat exchange performance during the cooling operation of the first storage compartment 101.
Next, the refrigerator according to the embodiment of the present disclosure may include a heat transfer member 340.
The heat transfer member 340 may be formed to conduct heat of the heating source 310 to the hot gas flow path 320.
A portion of the hot gas flow path 320 may be configured to be in direct contact with the heating source 310 without using the heat transfer member 340. For example, at least a portion of the connecting side path 322c may protrude to be in contact with the heating source 310, or at least a portion of the heating source 310 may protrude to be in contact with the connecting side path 322c.
However, when a portion of the connecting side path 322c protrudes or a portion of the heating source 310 protrudes, it may be difficult to couple the connecting side path 322c or the heating source 310 to each heat exchange pin 241.
Therefore, it is desirable to additionally provide the heat transfer member 340 that may be selectively coupled to the heating source 310 and the hot gas flow path 320, and to allow the heat of the heating source 310 to be conducted to the hot gas flow path 320 by the heat transfer member 340.
One end of the heat transfer member 340 may be in contact with the heating source 310. For this purpose, a first contact end 341 for contacting the heating source 310 is formed at one end of the heat transfer member 340. Thus, the heat transfer member 340 may receive the heat of the heating source 310.
The first contact end 341 of the heat transfer member 340 may be formed to be in surface contact while surrounding at least a portion of the heating source 310. For example, the first contact end 341 of the heat transfer member 340 may be formed to have an inner surface having the same shape as a part of the outer surface of the heating source 310. As a result, the contact area between the heating source 310 may be increased.
The other end of the heat transfer member 340 may be in contact with the hot gas flow path 320. For this purpose, a second contact end 342 for contacting the hot gas flow path 320 is formed at the other end of the heat transfer member 340. As a result, heat conducted to the heat transfer member 340 may be conducted to the hot gas flow path 320.
The second contact end 342 of the heat transfer member 340 may be formed to be in surface contact while surrounding at least a portion of the hot gas flow path 320. For example, the second contact end 342 of the heat transfer member 340 may be formed to have an inner surface having the same shape as a part of the outer surface of the hot gas flow path 320. As a result, the contact area between the hot gas flow path 320 may be increased.
The heat transfer member 340 may be formed of a metal. That is, the thermal conductivity may be improved by forming the heat transfer member 340 with a metal material.
The heat transfer member 340 may be formed of a plate material. That is, the heat transfer member 340 may be formed of a plate material to increase a heat conduction area.
Two or more heat transfer members 340 may be provided. In this case, one heat transfer member may be connected to any one portion of the connecting side path 322c, and the other heat transfer member may be connected to another portion of the connecting side path 322c. The heat transfer members 340 may be disposed adjacent to each other to reduce heat loss due to heat exchange with the outside air.
Although not shown, at least one heat transfer member 340 may be formed to contact any one portion of the outlet side path 322b. For example, the heat transfer member 340 may contact a portion of the outlet side path 322b having the lowest temperature.
The heat transfer member 340 may be formed to be elastically deformable. Accordingly, even if the interval between the hot gas flow path 320 and the heating source 310 is different from the designed interval, the heat transfer member 340 may be coupled with them.
At least a portion of the heat transfer member 340 may be rounded or bent to elastically deform the heat transfer member 340. That is, the heat transfer member 340 may have elasticity by the round or bent shape. The bending direction or bending angle of the heat transfer member 340 may be differently formed depending on the distance between the hot gas flow path 320 and the heating source 310 or the shape of the heating source 310.
Hereinafter, the operation of the refrigerator having the refrigeration system according to the first embodiment of the present disclosure and the operation of the defrosting operation will be described in detail.
Before describing the disclosure, the refrigerator according to the embodiment of the present disclosure may perform various operations by a controller. The controller may be a controller provided in the refrigerator or a control means (for example, a home network or an online service server) on a network connected to remotely control the controller of the refrigerator.
First, cold air is supplied or stopped to the first storage compartment 101 according to the upper limit reference temperature (NT1+Diff) and the lower limit reference temperature (NT1−Diff).
For example, when the internal temperature of the first storage compartment 101 exceeds the upper limit reference temperature (NT1+Diff) and reaches a dissatisfaction temperature, the cold air is supplied to the first storage compartment 101. On the other hand, when the internal temperature of the first storage compartment 101 reaches the lower limit reference temperature (NT1−Diff), the supply of cold air to the first storage compartment 101 is stopped.
When cold air is supplied to the first storage compartment 101, the compressor 210 of the refrigeration system is operated, and the flow path switching valve 330 is operated to allow the refrigerant to flow through the first refrigerant flow path 201.
The refrigerant compressed by the operation of the compressor 210 is condensed in a process of passing through the condenser 220, and the condensed refrigerant is decompressed and expanded while passing through the first expansion valve 231. The refrigerant is heat-exchanged with air flowing around through the heat exchange fin 241 while passing through the refrigerant tubes 242a and 242b of the first evaporator 240, and then flows to the compressor 210 to repeat the compressed circulation operation.
The air in the first storage compartment 101 may pass through the first evaporator 240 by the operation of the first storage compartment blowing fan 281, and then be supplied repeatedly into the first storage compartment 101. In this process, the air is heat-exchanged with the first evaporator 240 to be supplied into the first storage compartment 101 at a lower temperature to lower the temperature in the first storage compartment 101. This is shown in
During the operation of maintaining the set reference temperature (NT1) of the first storage compartment 101, whether the defrosting operation for the first evaporator 240 is satisfied (whether the defrosting operation is performed) is continuously determined.
Whether the defrosting operation is satisfied may be determined by various methods. For example, it may be possible to determine whether the defrost operation is satisfied by checking whether the accumulated operation time of the compressor 210 has passed a set time, checking the air flow rate or flow speed before and after the evaporator 240, or checking whether the first storage compartment 101 reaches the dissatisfaction temperature for a certain period of time.
When it is confirmed that the defrosting operation is satisfied by the at least one method, the defrosting operation for the first evaporator 240 is performed.
The defrosting operation may be performed by the heating of the heating source 310, the operation of the compressor 210 and the flow path switching valve 330.
The flow path switching valve 330 is operated to allow the refrigerant discharged to the discharge flow path 222 through the condenser 220 to flow to the hot gas flow path 320. Accordingly, the high-temperature refrigerant (hot gas) compressed by the compressor 210 is guided to pass through the first evaporator 240 through the hot gas flow path 320 after passing through the condenser 220, thereby supplying heat to the first evaporator 240. When the hot gas is supplied by the hot gas flow path 320, the cooling fan 221 cooling the condenser 220 is controlled to stop. That is, the temperature of the high-temperature refrigerant passing through the compressor 210 by the non-operation of the cooling fan 221 may be maintained at a high temperature without lowering the temperature while passing through the condenser 220. This is shown in
Accordingly, the first evaporator 240 receives heat from the heating source 310 and the hot gas flow path 320.
The hot gas (high-temperature refrigerant) provided to the hot gas flow path 320 through the discharge flow path 222 is introduced into the first evaporator 240 along the first path 321.
Thereafter, the hot gas (high-temperature refrigerant) sequentially passes through the heat exchange fins 241 of each row along the second path 322 to provide conduction heat to the corresponding heat exchange fins 241.
Accordingly, the hot gas introduced into the inlet side path 322a of the second path 322 removes frost formed in the heat exchange fin 241 while providing conduction heat to the heat exchange fin 241 while passing through a portion of the first evaporator 240.
Meanwhile, the temperature of the hot gas flowing along the inlet side path 322a is gradually lowered by sequential heat exchange with the heat exchange fins 241. However, since the connecting side path 322c receives the heat of the heating source 310 from the heat transfer member 340, the hot gas whose temperature is lowered while passing through the inlet side path 322a is re-heated while passing through the connecting side path 322c.
The reheated hot gas flows along the outlet side path 322b, provides conduction heat to the other part of the first evaporator 240, and then is discharged to the third path 323. Accordingly, the first evaporator 240 may be provided with sufficient heat for defrosting at all portions where the hot gas flow path 320 is located. That is, the problem that the side of the first evaporator 240 from which the hot gas is discharged (e.g. the side where the refrigerant outlet side of the outlet side path 322b is located) is not sufficiently heated is solved.
Each part 322a, 322b, and 322c of the second path through which the hot gas flows heats the heat exchange fins 241 faster than the heating source 310 providing radiant heat, considering that each part 322a, 322b, and 322c of the second path is in contact with the heat exchange fins 241 in each row. As a result, the upper side of the first evaporator 240, where frost is most severe, may be provided with sufficient heat to quickly complete defrosting and a defrosting failure of the corresponding portion may be prevented.
The hot gas passing through the first evaporator 240 is returned to the compressor 210 along a return flow path 211 and is compressed and then flows to the condenser 220, repeating the circulation.
In the refrigerator of the present disclosure, since the defrosting operation is performed while the heating source 310 and the hot gas (high-temperature refrigerant) are used together, the time for the defrosting operation is shortened. In addition, power consumption for the defrosting operation is reduced.
In particular, in the refrigerator of the present disclosure, since the hot gas flow path 320 is re-heated with the heat generated by the heating source 310 using the heat transfer member 340, it is possible to provide sufficient heat for defrosting until the hot gas completely passes through the first evaporator 240.
Meanwhile, the refrigerator of the present disclosure may be configured differently from the above-described embodiment.
For example, the hot gas flow path 320, the heating source 310, and the heat transfer member 340 may be applied to a refrigeration system having two or more evaporators, unlike the refrigeration system of the first embodiment described above.
Next, a refrigerator having a refrigeration system according to a second embodiment of the present disclosure will be described with reference to
Prior to the description, the same names and the same reference numerals are assigned to the same structure as the refrigeration system according to the first embodiment of the present disclosure, and repeated descriptions of the same configuration will be omitted.
For example, the compressor, condenser, and heating source of the refrigeration system according to the second embodiment of the present disclosure are provided in the same manner as the compressor, condenser, and heating source of the refrigeration system according to the first embodiment of the present disclosure.
The refrigeration system according to the second embodiment of the present disclosure may include a second expansion valve 232 that decompresses and expands the refrigerant flowing to a second evaporator 250 through the condenser 220.
The refrigeration system according to the second embodiment of the present disclosure may include a second evaporator 250 that exchanges heat between the refrigerant and the air in the refrigerator.
In the second evaporator 250, the refrigerant decompressed by the second expansion valve 232 and the air (cold air) flowing in the second storage compartment 102 are heat-exchanged with each other.
The second evaporator 250 may be located in the second storage compartment 102. Although not shown, the second evaporator 250 may be located at a portion other than the second storage compartment 102.
The second evaporator 250 may exchange heat between the air flowing by the driving of a second storage compartment blowing fan 291.
The refrigeration system according to the second embodiment of the present disclosure may include a second refrigerant flow path 202.
The second refrigerant flow path 202 is connected to the discharge flow path 222 to guide the flow of the refrigerant provided to the second evaporator 250 through the second expansion valve 232.
The second refrigerant flow path 202 may be formed to selectively receive the refrigerant by the flow path switching valve 330. In this case, the flow path switching valve 330 may be configured to selectively provide the refrigerant guided from the discharge flow path 222 to any one of the first refrigerant flow path 201, the second refrigerant flow path 202, and the hot gas flow path 320. For this purpose, the flow path switching valve 330 may be formed of a four-way valve.
Meanwhile, the refrigerant returned to the compressor 210 through each of the evaporators 240 and 250 may be returned along the return flow path 211 connected to the compressor 210.
The refrigeration system according to the second embodiment of the present disclosure may include a physical property adjustment part 270.
The physical property adjustment part 270 provides resistance to the flow of the refrigerant flowing through the hot gas flow path 320, through the first evaporator 240, and into the second evaporator 250. That is, resistance is provided to the flow of the refrigerant provided to the second evaporator 250 so that the physical property of the refrigerant is adjusted (changed). The physical property of the refrigerant may include any one of a temperature, a flow rate, and a flow speed of the refrigerant.
The refrigerant condensed and liquified as it passes through the first evaporator 240 may have a physical property that allows heat exchange in the second evaporator 250 as it passes through the physical property adjustment part 270. As a result, problems affecting the operational reliability of the compressor 210 due to excessive liquefaction of the refrigerant returned to the compressor 210 after passing through the second evaporator 250 may be prevented.
The resistance provided by the physical property adjustment part 270 may be different from the resistance provided by the second expansion valve 232. Accordingly, a difference in physical properties between the refrigerant flowing through the first evaporator 240 and the second evaporator 250, and the refrigerant flowing into the second evaporator 250 without passing through the first evaporator 240 may be minimized.
The physical property value adjustment part 270 may be provided as a tube through which the refrigerant flows.
The physical property adjustment part 270 may be designed in consideration of a flow path length, a pressure in the flow path, and a density formed by the refrigerant in the flow path. That is, the resistance may be adjusted by changing at least one of the flow path length, the pressure in the flow path, and the density formed by the refrigerant in the flow path of the physical property adjustment part 270.
The physical property adjustment part 270 may be formed to have a different diameter or a different length from the second expansion valve 232. That is, the physical property of the refrigerant flowing into the second evaporator 250 via the first evaporator 240 and the physical property of the refrigerant flowing into the second evaporator 250 from the condenser 220 are different from each other. Accordingly, the physical property of the refrigerant flowing into the second evaporator 250 via the first evaporator 240 may be substantially similar or identical to the physical property of the refrigerant passing through the second expansion valve 232 by using the physical property adjustment part 270.
As an example, the physical property adjustment part 270 may be formed to have the same diameter as the second expansion valve 232, but may be formed to have a different length. For example, the physical property adjustment part 270 may be formed to be shorter than the second expansion valve 232. The physical property adjustment part 270 and the second expansion valve 232 may be commonly used when the diameters of the physical property adjustment part 270 and the second expansion valve 232 are the same.
As another example, the physical property adjustment part 270 may have the same length as the second expansion valve 232, while the tube diameter of the physical property adjustment part 270 may be different from that of the second expansion valve 232. For example, a diameter of the physical property adjustment part 270 may be larger than that of the second expansion valve 232.
The refrigeration system according to the second embodiment of the present disclosure may include a guide flow path 350.
The guide flow path 350 may be formed to guide the refrigerant flowing to the second evaporator 250 through the second expansion valve 232 or the physical property adjustment part 270.
That is, the refrigerant passing through the second expansion valve 232 or the physical property adjustment part 270 may pass through the guide flow path 350 or may be mixed with each other in the guide flow path 350 and then flow to the second evaporator 250. Accordingly, the difference between the physical properties of the refrigerant flowing into the second evaporator 250 through the second expansion valve 232 and the physical properties of the refrigerant flowing into the second evaporator 250 through the physical property adjustment part 270 may be reduced.
Hereinafter, the operation of each storage compartment and a heat supply operation of the refrigerator having the refrigeration system according to the second embodiment of the present disclosure will be described in detail.
First, the cooling operation for each of the storage compartments 101 and 102 is performed by supplying cold air or stopping the supply of cold air according to an upper limit reference temperature (NT1+Diff, NT2+Diff) and a lower limit reference temperature (NT1−Diff, NT2−Diff) based on the set reference temperature (NT1, NT2) for each of the storage compartments 101 and 102.
For example, when the internal temperature of the first storage compartment 101 exceeds the upper limit reference temperature (NT1+Diff), the cold air is supplied to the first storage compartment 101. On the other hand, when the internal temperature of the first storage compartment 101 reaches the lower limit reference temperature (NT1−Diff), the supply of cold air to the first storage compartment 101 is stopped.
When cold air is supplied to the first storage compartment 101, the compressor 210 and the first storage compartment blowing fan 281 are operated, and the flow path switching valve 330 is operated to allow the refrigerant to flow along the first refrigerant flow path 201.
The refrigerant compressed by the operation of the compressor 210 is condensed in a process of passing through the condenser 220, and the condensed refrigerant is decompressed and expanded while passing through the first expansion valve 231. Subsequently, the refrigerant passes through the first evaporator 240 to exchange heat with the air flowing around and then flows to the compressor 210 through the return flow path 211 to be compressed, and this circulation is repeated.
During the cooling operation of the first storage compartment 101, the first storage compartment blowing fan 281 is operated. Accordingly, the air in the first storage compartment 101 may pass through the first evaporator 240 and then be supplied repeatedly into the first storage compartment. While the air is circulated, the air is heat-exchanged with the first evaporator 240 to be supplied into the first storage compartment 101 at a lower temperature to lower the temperature in the first storage compartment 101. The refrigerant flow during the cooling operation of the first storage compartment 101 is shown in
Meanwhile, when the internal temperature of the second storage compartment 102 reaches the dissatisfaction temperature, cold air is supplied to the second storage compartment 102.
When cold air is supplied to the second storage compartment 102, the compressor 210 and a second storage compartment blowing fan 282 may be operated, and the flow path switching valve 330 may be operated to flow cold air along the second refrigerant flow path 202.
The refrigerant compressed by the operation of the compressor 210 is condensed in a process of passing through the condenser 220, and the condensed refrigerant is decompressed and expanded while passing through the second expansion valve 232. Subsequently, the refrigerant passes through the second evaporator 250 to be heat-exchanged with the air flowing around the second evaporator 250, and then flows to the compressor 210 through the return flow path 211 to be compressed, and this circulation is repeated.
During the cooling operation of the second storage compartment 102, the second storage compartment blowing fan 282 is operated. Accordingly, the air in the second storage compartment 102 repeats a circulation operation that passes through the second evaporator 250 and is resupplied into the second storage compartment 102. While the air is circulated, the air is heat-exchanged with the second evaporator 250 and supplied into the second storage compartment 102 at a lower temperature to lower the temperature in the second storage compartment 102. The refrigerant flow during the cooling operation of the second storage compartment 102 is shown in
If the internal temperature of the first storage compartment 101 and the second storage compartment 102 are both in the dissatisfaction region, cold air may be supplied to any one storage compartment, cold air may be preferentially supplied to any one storage compartment, and then cold air may be supplied to the other storage compartment.
For example, cold air may be preferentially supplied to the second storage compartment 102 to achieve the satisfaction temperature, and then cold air is supplied to the first storage compartment 101. This is because the second storage compartment 102 is maintained at a temperature above freezing point, so the items stored in the storage compartment 102 may be sensitive to temperature changes.
During the operation of maintaining the set reference temperatures (NT1, NT2) for each of the storage compartments 101 and 102, it may be continuously determined whether to perform the heat supply operation for the first evaporator 240. The heat supply operation may include a defrosting operation that provides heat to the first evaporator 240 for defrosting the first evaporator 240.
The satisfaction of the heat supply operation (satisfying a condition for performing the defrosting operation) may be determined by various methods.
For example, it may be determined whether the heat supply operation is satisfied according to at least one method of checking whether an accumulated operation time of the compressor 210 has passed a set time, checking the air flow rate or flow speed before and after the evaporator 240, checking whether the first storage compartment 101 reaches the dissatisfaction temperature for a certain period of time, or checking using sensors (not shown).
If it is confirmed that the heat supply operation (defrosting operation) is satisfied by at least one method, the heat supply operation for the first evaporator 240 may be performed.
The heat supply operation may be performed by the heating of the heating source 310, the operation of the compressor 210 and the flow path switching valve 330. During the heat supply operation, the flow path switching valve 330 is operated to allow the refrigerant (hot gas) to flow to the hot gas flow path 320.
That is, heat is supplied to the first evaporator 240 by the heating source 310, and hot gas (high-temperature refrigerant) flows to the hot gas flow path 320 to provide heat to the first evaporator 240. The flow of the refrigerant during the heat supply operation to the first evaporator 240 is shown in
The hot gas is introduced into the upper end of the first evaporator 240 along the inlet side path 322a of the second path 322 and then sequentially passes through the heat exchange fins 241 of each row to provide conduction heat to the corresponding heat exchange fins 241. The hot gas (refrigerant) flowing along the connecting side path 322c of the second path 322 is heated by the heating source 310 while passing through a portion adjacent to the heating source 310. For example, the connecting side path 322c is heated by the heat of the heating source 310 or is heated by the heat conducted to the heat transfer member 340, thereby heating the hot gas flowing along the connecting side path 322c.
Thereafter, the hot gas sequentially passes through the heat exchange fins 241 of each row along the outlet side path 322b, thereby providing the heat exchange fins 241 with conductive heat.
In particular, the second path 322 through which the hot gas flows heats the heat exchange fins 241 faster than the heating source 310 providing radiant heat, considering that the second path 322 is in contact with the heat exchange fins 241 in each row. As a result, the upper side of the first evaporator 240, where frost is most severe, may be provided with sufficient heat to quickly complete defrosting.
That is, the heat supply operation using the heating source 310 and the hot gas (high-temperature refrigerant) may achieve a higher temperature than the heat supply operation using the heating source and a L-cord heat source (L-cord), and the time for the heat supply operation (defrosting operation) may be shortened.
Meanwhile, the refrigerant (heat-exchanged refrigerant) passing through the first evaporator 240 passes through the physical property adjustment part 270 before being provided to the second evaporator 250. Accordingly, the refrigerant may have an advantageous property for passing through the second evaporator 250.
The refrigerant passing through the physical property adjustment part 270 is provided to the second evaporator 250 through the guide flow path 350. Subsequently, the refrigerant passes through the second evaporator 250, exchanges heat with the air (cold air) in the second storage compartment 102, and is then returned to the compressor through the return flow path 211.
As such, the refrigerator of the present disclosure performs the cooling operation for supplying cold air to the second storage compartment 102 even though the heat supply operation of the first evaporator 240 is performed while using the hot gas.
Accordingly, since only the operation for cooling the first storage compartment 101 is performed after the defrosting operation is completed, the time for returning the first storage compartment to the satisfaction temperature (between the set reference temperature (NT1) and the lower limit reference temperature (NT-Diff)) may be shortened.
That is, it may be seen that the temperature of the first storage compartment 101 immediately after the end of the heat supply operation is the lowest when the heating source and the hot gas are used together. Also, when the heating source and the hot gas are used together, the time for returning the temperature of the first storage compartment 101 to the satisfaction temperature (between the set reference temperature (NT1) and the lower limit reference temperature (NT1−Diff)) is the shortest.
In the refrigerator of the present disclosure, since the defrosting operation is performed using the heating source 310 and the hot gas together, the time for the heat supply operation to the first evaporator 240 may be shortened. In addition, power consumption for the heat supply operation is reduced.
That is, the heat supply operation of the present disclosure may consume less power and shorten the defrosting time than the conventional defrosting operation performed by simultaneously using the defrosting heater and the L-cord heater or using only the L-cord heater. This may be seen through the bar shown in the graph of
Meanwhile, since only the cooling operation of the first storage compartment 101 is performed after the defrosting operation, the refrigerator of the present disclosure may reduce power consumption. That is, as shown in the graph of
In particular, when operating for cooling the second storage compartment 102, the refrigerator of the present disclosure may obtain higher cooling power even with a lower output when operating using hot gas than the normal cooling operation. This is shown in the pH diagram of
The refrigerator of the present disclosure may be formed such that the first path 321 has the same diameter as the discharge flow path 222. Accordingly, pressure fluctuation in the process of transferring the refrigerant (hot gas) may be prevented, and the same tube may be used.
That is, the flow resistance may be reduced by optimizing the diameter or length of each part of the hot gas flow path 320 to increase the flow rate of the refrigerant.
Accordingly, for the same period of time, the cooling rate of the second storage compartment 102 using the hot gas may be faster than the cooling rate of the second storage compartment 102 by the normal cooling operation. This is shown in the graph of
The refrigerator of the present disclosure may further reduce the temperature difference between the refrigerant inlet and the outlet side of the second evaporator 250 (see
In the refrigerator of the present disclosure, the hot gas passing through the first evaporator 240 is provided to the second evaporator 250 after the physical properties (e.g. pressure or temperature) of the hot gas are adjusted while passing through the physical property adjustment part 270.
Accordingly, heat exchange failure due to a difference in physical properties between the refrigerant provided to the second evaporator 250 during the defrosting operation of the first evaporator 240 and the refrigerant provided to the second evaporator 250 during the cooling operation of the second storage compartment 102 is prevented.
In particular, the physical property adjustment part 270 is formed to have a different length from the second expansion valve 232 in consideration of the diameter of the second path 322 and the state (temperature or pressure) of the refrigerant (hot gas) passing therethrough. Accordingly, heat exchange failure in the process of passing through the second evaporator 250 and compression failure in the process of passing through the compressor 210 are prevented.
Meanwhile, a refrigerator having the refrigeration system according to the second embodiment of the present disclosure may be implemented in various forms not shown, unlike the above-described embodiment.
In one embodiment, a refrigerator having the refrigeration system according to the second embodiment of the present disclosure may not provide the heating source 310. That is, the hot gas flow path 320 may be configured to perform the function of the heating source 310 (heat supply to a portion requiring heat).
In another embodiment, in a refrigerator having the refrigeration system according to the second embodiment of the present disclosure, when the heating source 310 is not provided, the position of the hot gas inlet side and the hot gas outlet side of the second path 322 of the hot gas flow path 320 may be designed differently from the above-described embodiment.
In another embodiment, in a refrigerator having the refrigeration system according to the second embodiment of the present disclosure, heat caused by the refrigerant (hot gas) flowing through the hot gas flow path 320 may be used for other purposes than the defrosting operation of the first evaporator 240.
For example, the hot gas flow path 320 may be used to heat an area that requires heat (e.g. to remove ice from an ice maker, to prevent frost on a door, to prevent overcooling in each storage compartment, and the like).
In another embodiment, in a refrigerator having the refrigeration system according to the second embodiment of the present disclosure, the hot gas flow path 320 is not divided into the first path 321 and the second path 322 and may be formed as a tube having the same outer diameter (or inner diameter).
In another embodiment, in a refrigerator having the refrigeration system according to the second embodiment of the present disclosure, the flow path switching valve 330 may be operated to open two or more flow paths at the same time.
For example, the refrigerant passing through the condenser 220 may flow while the first refrigerant flow path 201 and the hot gas flow path 320, the second refrigerant flow path 202 and the hot gas flow path 320, or the first refrigerant flow path 201 and the second refrigerant flow path 202 are simultaneously opened.
In another embodiment, in a refrigerator having the refrigeration system according to the second embodiment of the present disclosure, the hot gas flow path 320 may be formed to branch from the flow path between the compressor 210 and the condenser 220. That is, the high-temperature refrigerant passing through the compressor 210 may be formed to pass directly through the first evaporator 240 without passing through the condenser 220 and the first expansion valve 231 by the hot gas flow path 320.
In another embodiment, in a refrigerator having the refrigeration system according to the second embodiment of the present disclosure, the hot gas flow path 320 may be used to cool the second storage compartment 102.
That is, the refrigerant passing through the first evaporator 240 through the hot gas flow path 320 may flow to the second evaporator 250 after passing through the physical property adjustment part 270, thereby supplying cold air to the second storage compartment 102. At this time, if the cooling fan 221 provided in the condenser 220 (within the machine room) is controlled to operate, simultaneous cooling operation of the first storage compartment 101 and the second storage compartment 102 may also be possible.
| Number | Date | Country | Kind |
|---|---|---|---|
| 10-2021-0090868 | Jul 2021 | KR | national |
| 10-2021-0090869 | Jul 2021 | KR | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/KR2022/008428 | 6/14/2022 | WO |
