REFRIGERATOR

TECHNICAL FIELD

The present disclosure relates to a refrigerator in which a hot gas flow path is provided for supplying heat with a high-temperature refrigerant.

BACKGROUND ART

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.

Meanwhile, 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.

In particular, 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.

Accordingly, in the prior 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 defrosting heaters installed in the corresponding evaporator. When the defrosting operation is performed by heating of the defrosting heaters, a cooling operation for each storage compartment is stopped.

However, using only the defrosting heater 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 defrosting heater 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 prior art, a hot gas defrosting method using a hot 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 (prior art 1).

However, in the above-described prior 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 defrosting heater (increase in power consumption and impact on the storage).

Additionally, recently, a technology for defrosting using hot gas in a refrigerator that performs a cooling operation for two evaporators with one compressor has been provided. This is as presented in Korean Patent Publication No. 10-2017-0013766 (Prior Art 2) and Korean Patent Publication No. 10-2017-0013767 (Prior Art 3).

However, in the technologies of Prior Art 2 and Prior Art 3, the hot gas passing through one evaporator passes through an expansion valve for the other evaporator when the hot gas is introduced into the other evaporator. Accordingly, there is a problem in that it is difficult to adjust the amount of refrigerant introduced into the other evaporator.

That is, the refrigerant flowing directly through the condenser and into one evaporator and the refrigerant flowing into the other evaporator after passing through the condenser and the one evaporator have different pressures and temperatures. For this reason, a difference in heat exchange performance is inevitably generated due to a difference in pressure in a process of passing through the same expansion valve.

In addition, when the refrigerant performing defrosting while passing through any one evaporator and cooling the other evaporator while also passing through the other evaporator, and returning to the compressor, a return flow path (suction pipe) may be over-cooled and the liquid refrigerant, which is an incompressible fluid, may be introduced into the compressor.

Accordingly, problems such as damage to a valve inside the compressor caused by the liquid refrigerant may occur.

DETAILED DESCRIPTION OF THE DISCLOSURE
Technical Problem

The present disclosure is intended to solve various problems according to the prior art, and the purpose of the present disclosure is to protect a compressor by allowing a refrigerant to form a gaseous state when the refrigerant defrosts any one evaporator through a hot gas flow path, cools the other evaporator, and is returned to the compressor.

In addition, the purpose of the present disclosure is to prevent over-cooling of the return flow path for guiding an inflow of the refrigerant into the compressor during the defrosting operation.

In addition, the purpose of the present disclosure is to increase a cooling power by inducing a over-cooling of the refrigerant decompressed while passing through an expansion valve.

Technical Solution

According to a refrigerator of the present disclosure for achieving the above purpose, a hot gas flow path may be in contact with a return flow path. Accordingly, the refrigerant returned to a compressor may be in a gas state to prevent damage to the compressor.

According to a refrigerator of the present disclosure, at least a portion of the hot gas flow path may be in contact with the return flow path, or the entire hot gas flow path may be in contact with the return flow path.

At least a portion of the hot gas flow path may be in contact with only a portion of the return flow path, or at least a portion of the hot gas flow path may be in contact with the entirety of the return flow path.

According to the refrigerator of the present disclosure, a first path of the hot gas flow path may be in contact with the return flow path.

According to the refrigerator of the present disclosure, a contact portion of the hot gas flow path with the return flow path may be fixed by welding.

According to the refrigerator of the present disclosure a contact portion of the hot gas flow path with the return flow path may be fixed by bonding.

According to the refrigerator of the present disclosure, at least a portion of a first expansion valve may be in contact with the return flow path.

According to the refrigerator of the present disclosure, the first expansion valve may be in contact with a circumference of a portion of the return flow path that is different from a portion where the hot gas flow path is in contact with the return flow path.

According to the refrigerator of the present disclosure, the first expansion valve may be in contact with the circumference of the portion where the hot gas flow path is in contact with the return flow path.

According to the refrigerator of the present disclosure, the first expansion valve may be positioned on a side opposite to the position of the hot gas flow path with respect to the center of the return flow path when viewed from the axial direction of the return flow path.

According to the refrigerator of the present disclosure, at least a portion of a second expansion valve may be in contact with the return flow path.

According to the refrigerator of the present disclosure, the second expansion valve may be in contact with a circumference of a portion of the return flow path that is different from a portion where the hot gas flow path is in contact with the return flow path.

According to the refrigerator of the present disclosure, the second expansion valve may be in contact with the circumference of the portion where the hot gas flow path is in contact with the return flow path.

According to the refrigerator of the present disclosure, the second expansion valve may be positioned on a side opposite to the position of the hot gas flow path with respect to the center of the return flow path when viewed from the axial direction of the return flow path.

According to the refrigerator of the present disclosure, the first expansion valve and the second expansion valve may be in contact with the return flow path together with the hot gas flow path.

According to the refrigerator of the present disclosure, the first expansion valve and the second expansion valve may be in contact with the circumference of a portion where the hot gas flow path is in contact with the return flow path.

According to the refrigerator of the present disclosure, the first expansion valve, the second expansion valve, and the hot gas flow path may be disposed at portions symmetrical to each other from the center of the return flow path when viewed from the axial direction of the return flow path.

According to the refrigerator of the present disclosure, at least a portion of a physical property adjustment part may be in contact with the return flow path.

According to the refrigerator of the present disclosure, the second expansion valve and the physical property adjustment part may be in contact with the return flow path together with the hot gas flow path.

According to the refrigerator of the present disclosure, the physical property adjustment part may be positioned at a side opposite to the second expansion valve from the center of the return flow path when viewed from the axial direction of the return flow path.

ADVANTAGEOUS EFFECT OF THE DISCLOSURE

A refrigerator of the present disclosure configured as above provides the following respective effects.

In the refrigerator of the present disclosure, a refrigerant returned to a compressor is re-heated by a refrigerant flowing along a hot gas flow path. Accordingly, the refrigerant is prevented from being liquefied when the refrigerant is introduced into the compressor, and the compressor is prevented from being damaged due to the liquefied refrigerant.

In the refrigerator of the present disclosure, since a first path of the hot gas flow path is in contact with a return flow path, a refrigerant passing through the return flow path is sufficiently heated.

In the refrigerator of the present disclosure, in addition to the hot gas flow path, at least one of a first expansion valve, a second expansion valve, or a physical property adjustment part is in contact with the return flow path. Accordingly, the refrigerant passing through the return flow path is sufficiently heated even when the refrigerant is not affected by the hot gas flow path.

In the refrigerator of the present disclosure, since the refrigerant decompressed while passing through the expansion valve is over-cooled by heat exchange with a refrigerant flowing along the return flow path, thereby increasing the cooling capacity.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a perspective view showing an exterior of a refrigerator according to an embodiment of the present disclosure;

FIG. 2 is a view showing an internal structure of the refrigerator according to an embodiment of the present disclosure;

FIG. 3 is a view showing a refrigeration system and a heat providing structure of the refrigerator according to an embodiment of the present disclosure;

FIG. 4 is a view showing a state of a pipe in which a refrigerant of the refrigerator flows according to an embodiment of the present disclosure;

FIG. 5 is an enlarged view of portion “A” of FIG. 4.

FIG. 6 is an enlarged view of a portion “B” of FIG. 4.

FIG. 7 is a view showing a flow of a refrigerant during a cooling operation of a first storage compartment of the refrigerator according to an embodiment of the present disclosure;

FIG. 8 is a view showing a flow of a refrigerant during a cooling operation of a second storage compartment of the refrigerator according to an embodiment of the present disclosure;

FIG. 9 is a view showing a flow of a refrigerant during an operation of supplying heat to a first evaporator of the refrigerator according to an embodiment of the present disclosure;

FIGS. 10 to 16 are views showing respective embodiments for heating a return flow path of the refrigerator according to an embodiment of the present disclosure.

FIG. 17 is a graph showing temperature changes according to time and input values of each evaporator and each flow path when the hot gas flow path is not in contact with the return flow path;

FIG. 18 is a graph showing temperature changes according to time and input values of each evaporator and each flow path when the hot gas flow path is in contact with the return flow path according to an embodiment of the present disclosure.

BEST MODE OF THE DISCLOSURE

Hereinafter, a preferred embodiment of a refrigerator of the present disclosure will be described with reference to FIGS. 1 to 18.

FIG. 1 is a view showing an exterior of the refrigerator according to the embodiment of the present disclosure, and FIG. 2 is a view showing an internal structure of the refrigerator according to the embodiment of the present disclosure.

As shown in these drawings, the refrigerator according to the embodiment of the present disclosure may be provided such that a return flow path 211 of a compressor 210 may be affected by a refrigerant (hot gas) flowing along a hot gas flow path 320. Accordingly, damage to the compressor 210 due to a liquid refrigerant returned to the compressor 210 may be prevented.

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 includes a main body 100.

The main body 100 may form an exterior of the refrigerator and may provide a storage compartment therein.

The storage compartment may be a storage space for storing stored item. At least one storage compartment may be provided in the main body 100. For example, the main body 100 may be formed to provide a first storage compartment 101 and a second storage compartment 102.

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. Although not shown, the first storage compartment 101 and the second storage compartment 102 may be simultaneously opened and closed by one door, or may be partially opened and closed with two or more doors.

The first storage compartment 101 is operated to be maintained at a first set reference temperature (NT1). The first set reference temperature (NT1) may be a temperature at which the 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 operated to be maintained at a different temperature range from the first storage compartment 101.

The second storage compartment 102 may be operated to be maintained at a second set reference temperature (NT2). The second set reference temperature (NT2) may be a temperature at which the stored object is not frozen. The second set reference temperature (NT2) may be a temperature range higher than the first set reference temperature (NT1).

For example, the second set reference temperature (NT2) may be a temperature equal to or less than 32° C. and higher than 0° C. The second set reference temperature (NT2) may be set to be higher than 32° C. (e.g. depending on a room temperature outside the refrigerator or the type of stored objects), or may be set to be equal to or lower than 0° C., if necessary.

In the embodiment of the present disclosure, the first storage compartment 101 is a freezer compartment, and the second storage compartment 102 is a refrigerating compartment.

Meanwhile, each of the storage compartments 101 and 102 described above 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).

Next, the refrigerator according to the embodiment of the present disclosure includes a refrigeration system as shown in FIG. 3.

That is, cold air is supplied by the refrigeration system so that each of the storage compartments 101 and 102 may be maintained at the set reference temperature (NT1, NT2). 74. The refrigeration system may include a compressor 210. The compressor 210 may compress a refrigerant. The compressor 210 may be disposed in a machine room 103 in the main body 100.

The compressor 210 may operate when an operation condition of each of the storage compartments 101 and 102 is satisfied. For example, if an internal temperature of any one storage compartment falls within a dissatisfaction region (a temperature exceeding NT1+Diff, NT2+Diff), it is determined that the operation condition is satisfied, and the compressor 210 is operated.

The compressor 210 may be configured to operate during a defrosting operation on a first evaporator 250. That is, during the defrosting operation, a high-temperature refrigerant may be supplied to the first evaporator 250 through a condenser 220 by the operation of the compressor 210 to defrost the first evaporator 250. Of course, the compressor 210 may stop or temporarily stop during the defrosting operation.

A return flow path 211 may be connected to the compressor 210. The return flow path 211 is a flow path for guiding a suction flow of a refrigerant returned to the compressor 210. The return flow path 211 may be formed of a pipe.

The return flow path 211 may be connected to each flow path (for example, a first flow path, a second flow path, a hot gas flow path, or the like) through which a refrigerant flows to be combined into one and returned to the compressor 210. Although not shown, two or more return flow paths 211 may be provided and connected to each flow path individually or in a plurality.

As shown in FIG. 3, the refrigeration system may include a condenser 220. The refrigerant compressed in the compressor 210 may be condensed by the condenser 220. The condenser 220 may be located in the machine room 103 in the main body 100.

The condenser 220 may be configured to have a cooling fan 221. The cooling fan 221 may be operated to cool and condense the refrigerant passing through the condenser 220.

If the refrigerant passing through the condenser 220 is not condensed, the cooling fan 221 is maintained in a stopped state. Accordingly, the high-temperature refrigerant compressed from the compressor 210 may be provided to the hot gas flow path 320 without a sudden temperature decrease in a process of passing through the condenser 220.

A discharge tube 203 may be formed in the condenser 220. The discharge tube 203 guides the discharge flow of the refrigerant that has passed through the condenser 220.

As shown in FIG. 3, the refrigeration system may include a first expansion valve 230 and a second expansion valve 240. The refrigerant condensed in the condenser 220 may be decompressed by the first expansion valve 230 and the second expansion valve 240.

The first expansion valve 230 decompresses the refrigerant flowing through the condenser 220 to the first evaporator 250. The second expansion valve 240 decompresses the refrigerant flowing through the condenser 220 to the second evaporator 260.

As shown in FIG. 3, the refrigeration system may include a first evaporator 250 and a second evaporator 260.

The refrigerant decompressed in the first expansion valve 230 is evaporated by the first evaporator 250. Air (cold air) flowing in the first storage compartment 101 by driving of a first blowing fan 281 is heat-exchanged with the first evaporator 250. At least a portion of the first evaporator 250 may be located in the first storage compartment 101.

The refrigerant decompressed in the second expansion valve 240 is evaporated by the second evaporator 260. Air (cold air) flowing in the second storage compartment 102 by driving of a second blowing fan 291 is heat-exchanged with the second evaporator 260. At least a portion of the second evaporator 260 may be located in the second storage compartment 102.

Although not illustrated, each of the evaporators 250 and 260 may not be located entirely within each of the storage compartments 101 and 102, but may be located on an upper side, a lower side of each storage compartment, or another storage compartment.

The first blowing fan 281 may be disposed in a first grille assembly 280 for guiding the supply of cold air into the first storage compartment 101. That is, the air (cold air) in the first storage compartment 101 may be heat-exchanged with the refrigerant passing through the first evaporator 250 while passing through the first evaporator 250 by the operation of the first blowing fan 281, and then may be supplied back into the first storage compartment 101. Accordingly, the temperature of the first storage compartment 101 may be gradually lowered.

The second blowing fan 291 may be disposed in a second grille assembly 290 for guiding the supply of cold air into the second storage compartment 102. That is, the air (cold air) in the second storage compartment 102 may be heat-exchanged with the refrigerant passing through the second evaporator 260 while passing through the second evaporator 260 by the operation of the second blowing fan 291, and then may be supplied back into the storage compartment 102. Accordingly, the temperature of the second storage compartment 102 may be gradually lowered.

As shown in FIG. 3, the refrigeration system may include a first flow path 201.

The first flow path 201 guides the flow of the refrigerant passing through the first expansion valve 230 and the first evaporator 250 from the condenser 220. That is, the first flow path 201 may be a flow path of the refrigerant for the cooling operation of the first storage compartment 101.

The first flow path 201 may be connected to the return flow path 211 returned to the compressor 210 after passing through the first evaporator 250.

As shown in FIG. 3, the refrigeration system may include a second flow path 202.

The second flow path 202 is formed to guide the flow of the refrigerant passing through the second expansion valve 230 and the second evaporator 260 from the condenser 220. That is, the second flow path 202 may be a flow path of the refrigerant for the cooling operation of the second storage compartment 102.

The second flow path 202 may be connected to the return flow path 211 returned to the compressor 210 after passing through the second evaporator 260.

Meanwhile, as shown in FIGS. 3 to 5, at least a portion of the first expansion valve 230 or the second expansion valve 240 may be welded or bonded to at least a portion of the first flow path 201 or the second flow path 202. That is, the refrigerant flowing along the first flow path 201 or the second flow path 202 is affected by a refrigerant decompressed while passing through the first expansion valve 230 or the second expansion valve 240, so that the temperature is lowered and the cooling efficiency is improved.

As shown in FIG. 3, the refrigeration system may include a hot gas flow path 320.

The hot gas flow path 320 supplies high-temperature heat to a place where heat is required.

The hot gas flow path 320 may be formed to guide the high-temperature refrigerant passing through the condenser 220. That is, the hot refrigerant (hot gas) guided by the hot gas flow path 320 provides heat.

For example, the hot gas flow path 320 may guide the flow of the refrigerant to the second evaporator 260 through the condenser 220 and the first evaporator 250. That is, the hot gas flow path 320 may be formed to heat the second evaporator 260 with the high temperature refrigerant that has been compressed in the compressor 210 and passed through the condenser 220.

As shown in FIG. 3, the refrigeration system may include a physical property adjustment part 270.

The physical property adjustment part 270 may be provided in the hot gas flow path 320.

For example, the physical property adjustment part 270 may be disposed between the first evaporator 250 and the second evaporator 260 of the hot gas flow path 320.

The physical property adjustment part 270 may provide resistance to the flow of the refrigerant flowing to the second evaporator 260 through the first evaporator 250. That is, by providing resistance to the flow of the refrigerant, the physical property of the refrigerant may be changed.

The physical property of the refrigerant may include any one of a temperature, a flow rate, and a flow speed.

For example, the physical property adjustment part 270 may be formed as a tube for decompressing and expanding the refrigerant flowing to the second evaporator 260 through the first evaporator 250 of the hot gas flow path 320. That is, the refrigerant condensed and liquefied while passing through the first evaporator 250 may be provided to the second evaporator 260 in a re-expanded state while passing through the physical property adjustment part 270. Accordingly, the problem of 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 260 may be prevented.

At least a portion of the physical property adjustment part 270 may be welded or bonded to the return flow path 211.

As shown in FIG. 3, a flow path switching valve 330 may be included in the refrigeration system.

The refrigerant passing through the condenser 220 may be guided to the discharge tube 203, and the first flow path 201, the second flow path 202, and the hot gas flow path 320 may be branched from the discharge tube 203, respectively.

The flow path switching valve 330 may be installed at a portion where each flow path 201, 202, 320 is branched from the discharge tube 203. That is, the refrigerant flowing into the discharge tube 203 by the operation of the flow path switching valve 330 may be supplied to one of the first flow path 201, the second flow path 202, or the hot gas flow path 320.

For example, the flow path switching valve 330 may be provided as a four-way valve. The flow path switching valve 330 may be provided as a three-way valve or any other multi-way valve, or two or more unidirectional valves.

Meanwhile, as shown in FIGS. 3, 4, and 6, the hot gas flow path 320 may be in contact with the return flow path 211.

That is, the refrigerant flowing along the hot gas flow path 320 heats the refrigerant flowing along the return flow path 211 to prevent the liquefaction of the refrigerant returned to the compressor 210. Accordingly, inflow of the liquid refrigerant into the compressor 210 may be prevented, and damage to the compressor 210 due to the liquid refrigerant may be prevented.

The hot gas flow path 320 may be welded or bonded to the return flow path 211. That is, at least a portion of the hot gas flow path 320 is always in contact with the return flow path 211 by fixing the hot gas flow path 320 to the return flow path 211. The hot gas flow path 320 may be in contact with the return flow path 211 in an engaging coupling structure.

Only a portion of the hot gas flow path 320 may be in contact with the return flow path 211 or the entire hot gas flow path 320 may be in contact with the return flow path 211. For example, the length of the hot gas flow path 320 may be determined in consideration of the length of the return flow path 211.

At least a portion of the hot gas flow path 320 may be in contact with only a portion of the return flow path 211, or at least a portion of the hot gas flow path 320 may be in contact with the entire return flow path 211. For example, the length of the return flow path 211 may be determined in consideration of the length of the hot gas flow path 320.

The hot gas flow path 320 may include a first path 321 from the discharge tube 203 to the first evaporator 250. The hot gas flow path 320 may include a second path 322 extending from the first path 321 and passing through the first evaporator 250. The hot gas flow path 320 may include a third path 323 from the first evaporator 250 to the physical property adjustment part 270.

The first path 321 may be in contact with the return flow path 211. That is, since a refrigerant inflow side portion (the first path) guiding the refrigerant inflow to the first evaporator 250 has a higher temperature than the second path 322 passing through the first evaporator 250 or a refrigerant outflow side portion guiding the refrigerant outflow of the first evaporator 250, it is more advantageous to prevent the return flow path 211 from being overcooled.

Heat loss may occur in a process in which the first path 321 passes through the first evaporator 250 due to heat exchange with the return flow path 211. However, the benefit of preventing damage to the compressor 210 due to overcooling of the return flow path 211 is greater than the heat loss of the hot gas flow path 320 due to the heat exchange.

Next, as shown in FIG. 3, the refrigerator according to the 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 260 through the second expansion valve 240 or the physical property adjustment part 270.

That is, the refrigerant passing through the second expansion valve 240 or the physical property adjustment part 270 may pass through the guide flow path 350, respectively, or may be mixed with each other in the guide flow path 350 and then flow to the second evaporator 260. Accordingly, the difference between the physical properties of the refrigerant flowing into the second evaporator 260 passing through the second expansion valve 240 and the physical properties of the refrigerant flowing into the second evaporator 260 passing through the physical property adjustment part 270 may be reduced.

Hereinafter, the operation of the refrigerator of the present disclosure described above will be described in detail.

Prior to the description, the refrigerator performs various operations by a controller. Although not described in detail, various driving operations may be performed by a control means (for example, a home network, an online service server, or the like) on a network connected through wired or wireless communication so as to control a control unit of the refrigerator rather than a corresponding refrigerator.

First, the refrigerator of the present disclosure may perform a cooling operation of the first storage compartment 101.

The cooling operation is performed by supplying cold air or stopping the supply of cold air according to the upper limit reference temperature (NT1+Diff) and the lower limit reference temperature (NT1−Diff) based on the set reference temperature (NT1) of the first storage compartment 101.

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, as shown in FIG. 7, the compressor 210 and the first blowing fan 281 of the refrigeration system are operated, and the flow path switching valve 330 is operated to allow the refrigerant to flow through the first flow path 201.

Accordingly, 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 230. Subsequently, the refrigerant passes through the first evaporator 250 to exchange heat with the air flowing around the first evaporator 250, and then flows to the compressor 210 to be compressed and this circulation is repeated.

The air in the first storage compartment 101 may pass through the first evaporator 250 by the operation of the first 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 250 to be supplied into the first storage compartment 101 at a lower temperature to lower the temperature in the first storage compartment 101.

The refrigerator of the present disclosure may perform a cooling operation of the second storage compartment 102.

The cooling operation may be performed by supplying cold air or stopping the supply of cold air according to an upper limit reference temperature (NT2+Diff) and a lower limit reference temperature (NT2−Diff) based on the set reference temperature (NT2) of the second storage compartment 102.

For example, when the internal temperature of the second storage compartment 102 exceeds the upper limit reference temperature (NT2+Diff) and reaches the dissatisfaction temperature, the cold air is supplied to the second storage compartment 102. On the other hand, when the internal temperature of the second storage compartment 102 reaches the lower limit reference temperature (NT2−Diff), the supply of cold air to the second storage compartment 102 is stopped.

When cold air is supplied to the second storage compartment 102, as shown in FIG. 8, the compressor 210 and the second blowing fan 291 of the refrigeration system are operated, and the flow path switching valve 330 is operated to flow cold air through the second 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 240. Subsequently, the refrigerant passes through the second evaporator 260 to exchange heat with the air flowing around the second evaporator 260, and then flows to the compressor 210 to be compressed, and this circulation is repeated.

In addition, by the operation of the second blowing fan 291, the air in the second storage compartment 102 passes through the second evaporator 260 and is repeatedly supplied into the second storage compartment 102. In this process, the air is heat-exchanged with the second evaporator 260 and supplied into the second storage compartment 102 at a lower temperature to lower the temperature in the second storage compartment 102.

If the internal temperature the of first storage compartment 101 and the second storage compartment 102 are both in the dissatisfaction region, 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.

In the refrigerator of the present disclosure, an operation in which the refrigerant flows through the hot gas flow path 320 may be performed.

For example, the defrosting operation for the first evaporator 250 may be performed using the refrigerant flowing along the hot gas flow path 320.

In this case, as shown in FIG. 9, the refrigerant passing through the first evaporator 250 along the hot gas flow path 320 is guided to be returned to the compressor 210 through the return flow path 211 after additionally passing through the second evaporator 260.

When the refrigerant is returned to the compressor 210 through the return flow path 211, the refrigerant passing through the hot gas flow path 320 provides heat to the return flow path 211. Accordingly, the refrigerant returned along the return flow path 211 is prevented from liquefying, and damage to the compressor 210 due to the inflow of the liquid refrigerant may be prevented.

In particular, the hot gas flow path 320 provides heat to the return flow path 211 by the first path 321 having a relatively higher temperature than the second path 322. Accordingly, sufficient heat to prevent the liquefaction of the refrigerant may be provided even when the room temperature outside the refrigerator is low.

Since the second path 322 of the hot gas flow path 320 contacts the return flow path 211, the heat of the second path 322 is transferred to the return flow path 211 through heat conduction. Accordingly, sufficient heat may be provided to the return flow path 211.

Meanwhile, the refrigerator of the present disclosure may be performed in a different form from the above-described embodiment.

For example, according to another embodiment of the present disclosure, as shown in FIG. 10, the hot gas flow path 320 and the first expansion valve 230 may be in contact with the return flow path 211. In this case, some or all of the first expansion valve 230 may be in contact with the return flow path 211.

That is, during the cooling operation (freezing operation) for the first storage compartment 101, heat may also be provided to the return flow path 211 while the refrigerant passing through the condenser 220 passes through the first expansion valve 230.

Accordingly, the refrigerant returned to the compressor 210 along the return flow path 211 may be prevented from being liquefied by the heating by the first expansion valve 230 even if the refrigerant is not heated by the hot gas flow path 320.

According to another embodiment of the present disclosure, as shown in FIG. 11, the hot gas flow path 320 and the second expansion valve 240 may be in contact with the return flow path 211. In this case, some or all of the second expansion valve 240 may be in contact with the return flow path 211.

That is, during the cooling operation (freezing operation) for the second storage compartment 102, heat may also be provided to the return flow path 211 while the refrigerant passing through the condenser 220 passes through the second expansion valve 240.

Accordingly, the refrigerant returned to the compressor 210 along the return flow path 211 may be prevented from being liquefied by the heating by the second expansion valve 240 even if the refrigerant is not heated by the hot gas flow path 320.

According to another embodiment of the present disclosure, as shown in FIG. 12, the hot gas flow path 320 and the physical property adjustment part 270 may be in contact with the return flow path 211.

That is, by contacting the return flow path 211, the property adjustment part 270 through which the hot refrigerant (hot gas) passes may prevent the return flow path 211 from being overcooled.

Accordingly, the refrigerant returned to the compressor 210 along the return flow path 211 may be prevented from being liquefied by the heating by the physical property adjustment part 270 even if the refrigerant is not heated by the hot gas flow path 320.

According to another embodiment of the present disclosure, as shown in FIGS. 13 to 15, the hot gas flow path 320, the first expansion valve 230, and the second expansion valve 240 may be in contact with the return flow path 211.

That is, the refrigerant passing through the condenser 220 during the cooling operation (freezing operation) for the respective storage compartments 101 and 102 is heat-exchanged with the return flow path 211 while passing through the first expansion valve 230 or the second expansion valve 240.

Accordingly, the refrigerant returned to the compressor 210 along the return flow path 211 may be prevented from being liquefied by heating by the first expansion valve 230 or the second expansion valve 240 even if the refrigerant is not heated by the hot gas flow path 320.

When the first expansion valve 230 and the second expansion valve 240 are in contact with the return flow path 211, the first expansion valve 230 and the second expansion valve 240 may be provided at the same portion of the return flow path 211.

Only one of the first expansion valve 230 and the second expansion valve 240 is selectively operated. Accordingly, even when the first expansion valve 230 and the second expansion valve 240 are in contact with any part of the return flow paths 211, each expansion valve is not affected by each other.

Meanwhile, if the other expansion valve is operated immediately after the operation of one expansion valve, the other expansion valve may be affected by the one expansion valve. Considering that the two expansion valves 230 and 240 may be designed to operate simultaneously, it may be desirable for the two expansion valves 230 and 240 to be spaced apart so as not to influence each other as much as possible.

In particular, the first expansion valve 230 and the second expansion valve 240 may be in contact with the entire portion of the return flow path 211 together with the hot gas flow path 320. In this case, the two expansion valves 230 and 240 and the hot gas flow path 320 may be in contact with portions that are symmetrical (opposite side portions) with respect to the axial center of the return flow path 211 as viewed from the axial direction.

According to another embodiment of the present disclosure, as shown in FIG. 16, the hot gas flow path 320, the physical property adjustment part 270, and the second expansion valve 240 may be in contact with the return flow path 211.

The second expansion valve 240 and the physical property adjustment part 270 may be in contact with a portion of the circumference of the return flow path 211 that is different from the portion where the hot gas flow path 320 contacts.

At least a portion of the second expansion valve 240 and the physical property adjustment part 270 may be in contact with the circumference of the return flow path 211, respectively. In this case, the physical property adjustment part 270 may be positioned opposite to the position of the second expansion valve 240 when viewed from the center of the return flow path 211.

Although not shown, the hot gas flow path 320, the physical property adjustment part 270, and the first expansion valve 240 may be in contact with the return flow path 211.

According to another embodiment of the present disclosure, the hot gas flow path 320 may be in contact with a side through which the refrigerant flows into the compressor 210 among each part of the return flow path 211. That is, the refrigerant may be heated as much as possible until the refrigerant is introduced into the compressor 210. Accordingly, a liquefaction of the refrigerant flowing into the compressor 210 may be prevented.

If at least one of the first expansion valve 230, the second expansion valve 240, or the physical property adjustment part 270 is in contact with the return flow path 211, the hot gas flow path 320 may be closer to a refrigerant inflow side portion of the compressor 210 than the first expansion valve 230, the second expansion valve 240, or the physical property adjustment part 270.

As such, in the refrigerator of the present disclosure, since at least a portion of the hot gas flow path 320 is in contact with the return flow path 211, the refrigerant returned to the compressor 210 is re-heated by the refrigerant flowing along the hot gas flow path 320. Accordingly, the refrigerant may be prevented from being liquefied when the refrigerant is introduced into the compressor 210, and the compressor 210 may be prevented from being damaged due to the liquefied refrigerant.

In particular, as shown in the graph in FIG. 17, if the hot gas flow path 320 is configured not to be in contact with the return flow path 211, the temperature of the return flow path 211 is rapidly cooled during the defrosting operation of the first evaporator 250. Accordingly, reliability problems with the first evaporator may occur.

However, as shown in the graph in FIG. 18, if the hot gas flow path 320 is configured to be in contact with the return flow path 211, the temperature of the return flow path 211 is maintained at a constant temperature even during the defrosting operation of the first evaporator 250. Accordingly, reliability problems with the first evaporator 250 may be prevented.

In the refrigerator of the present disclosure, since the first path 321 of the hot gas flow path 320 contacts the return flow path 211, the refrigerant passing through the return flow path 211 may be sufficiently heated.

In the refrigerator of the present disclosure, in addition to the hot gas flow path 320, at least one of the first expansion valve 230, the second expansion valve 240, or the physical property adjustment part 270 is in contact with the return flow path 211. Accordingly, the refrigerant passing through the return flow path 211 may be sufficiently heated even when the refrigerant is not affected by the hot gas flow path 320.

In the refrigerator of the present disclosure, the refrigerant decompressed while passing through the expansion valves 230 and 240 is overcooled by heat exchange with the refrigerant flowing along the return flow path 211. Accordingly, the cooling power of the refrigerator may be further increased.

Meanwhile, the refrigerator of the present disclosure may be implemented in various forms, which are not shown, unlike the above-described embodiments.

For example, the refrigerator of the present disclosure may not include the physical property adjustment part 270 in the hot gas flow path 320.

As another example, the refrigerator of the present disclosure may include a cooling system composed of the compressor 210, the condenser 220, the second expansion valve 240, the second evaporator 260, and the second flow path 202, and the hot gas flow path 320 may be configured to be in contact with the return flow path 211 of the compressor 210.

As another example, the refrigerator of the present disclosure may be configured such that the hot gas flow path 320 is used to heat the second evaporator 260.

As another example, the refrigerator of the present disclosure may be configured such that the hot gas flow path 320 is used to heat components other than the first evaporator 250. That is, the hot gas flow path 320 may be applied to a structure in which the hot gas flow path 320 does not pass through the first evaporator 250.

As another example, the structure of the hot gas flow path 320 constituting the refrigerator of the present disclosure (a structure contacting the return flow path) may also be applied to a refrigerator in which the second expansion valve 240 and the second evaporator 260 are not provided.

REFRIGERATOR

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