Patent Grant
12055343
This application is a U.S. National Stage Application under 35 U.S.C. § 371 of PCT Application No. PCT/KR2020/008969, filed Jul. 8, 2020, which claims priority to Korean Patent Application No. 10-2019-0082640, filed Jul. 9, 2019, whose entire disclosures are hereby incorporated by reference.
The present disclosure relates to a vacuum adiabatic body, a refrigerator, and a method for fabricating the refrigerator.
A vacuum adiabatic body is a product for suppressing heat transfer by vacuuming the inside of a main body thereof. The vacuum adiabatic body may reduce heat transfer by convection and conduction, and hence is applied to heating apparatuses and refrigerating apparatuses. In a typical adiabatic method applied to a refrigerator, although it is differently applied in refrigeration and freezing, a foam urethane adiabatic wall having a thickness of about 30 cm or more is generally provided. However, the internal volume of the refrigerator is therefore reduced.
In order to increase the internal volume of a refrigerator, there is an attempt to apply a vacuum adiabatic body to the refrigerator.
First, Korean Patent No. 10-0343719 (Reference Document 1) of the present applicant has been disclosed. According to Reference Document 1, there is disclosed a method in which a vacuum adiabatic panel is prepared and then built in walls of a refrigerator, and the outside of the vacuum adiabatic panel is finished with a separate molding as Styrofoam. According to the method, additional foaming is not required, and the adiabatic performance of the refrigerator is improved. However, fabrication cost is increased, and a fabrication method is complicated.
As another example, a technique of providing walls using a vacuum adiabatic material and additionally providing adiabatic walls using a foam filling material has been disclosed in Korean Patent Publication No. 10-2015-0012712 (Reference Document 2). According to Reference Document 2, fabrication cost is increased, and a fabrication method is complicated.
As further another example, there is an attempt to fabricate all walls of a refrigerator using a vacuum adiabatic body that is a single product. For example, a technique of providing an adiabatic structure of a refrigerator to be in a vacuum state has been disclosed in U.S. Patent Laid-Open Publication No. US2004/0226956A1 (Reference Document 3). However, it is difficult to obtain a practical level of an adiabatic effect by providing a wall of the refrigerator with sufficient vacuum. In detail, there are limitations that it is difficult to prevent a heat transfer phenomenon at a contact portion between an outer case and an inner case having different temperatures, it is difficult to maintain a stable vacuum state, and it is difficult to prevent deformation of a case due to a negative pressure of the vacuum state. Due to these limitations, the technology disclosed in Reference Document 3 is limited to a cryogenic refrigerator, and does not provide a level of technology applicable to general households.
Alternatively, the present applicant has applied for Korean Patent Publication No. 10-2017-0016187 (Reference Document 4) that discloses a vacuum adiabatic body and a refrigerator. According to the present disclosure, both the door and the main body of the refrigerator are provided as a vacuum adiabatic body, and a large adiabatic material is added to the edge of the door to prevent cool air from leaking from the edge of the main body and the door. However, there is a limitation in that the fabrication is complicated, and an internal volume of the refrigerator is greatly reduced.
An evaporator is provided in the refrigerator, and frost is thickly generated on the evaporator according to the cumulative use of the evaporator. Since the frost of the evaporator adversely affects performance of the evaporator, it is periodically melted and removed. Here, the removing of the frost from the evaporator is called a defrosting operation. Defrosting water generated during the defrosting operation is discharged to the outside of the refrigerator.
As a technique for discharging the defrosting water to the outside of the refrigerator, U.S. Pat. No. 9,863,689B2 (Reference Document 5) has been suggested. In Reference Document 5, a hose for discharging defrosting water and a valve for opening and closing the hose are provided outside the refrigerator. The hose passes through a foam adiabatic material and then is guided to the outside.
The techniques of Reference Document 5 may be applied in the case of a refrigerator using a foam. Specifically, the refrigerator using the foam uses an adiabatic portion having a thickness of several tens of centimeters. On the other hand, when the refrigerator uses a vacuum adiabatic body, the adiabatic portion having a thickness of only a few tens of millimeters is used even though the adiabatic portion is thick. In addition, when using the foam and when using the vacuum adiabatic body, there are many differences such as a vacuum degree and material differences.
Due to such a structural difference, in the case of the refrigerator using the vacuum adiabatic body, there is a limitation that a large amount of cool air is lost through a gap between a discharge structures of the defrosting water because the thin thickness.
In the case of the refrigerator using the vacuum adiabatic body, there is a limitation in that a conduction cooling loss between the portions is large because vacuum is provided by a metal connection body and their welding.
In the refrigerator using the vacuum adiabatic body, a large amount of cool air is permeated due to the small thickness. In this case, there is a limitation that malfunction occurs due to freezing of the defrosting water.
In the case of the refrigerator using the vacuum adiabatic body, a temperature change is large due to the metal structure and dew generated around the metal structure due to the temperature change during the defrosting operation adversely affect reliability of the product.
Embodiments provide a refrigerator in which a cool air loss through a thin gap passing through a vacuum adiabatic body is reduced.
Embodiments also provide a refrigerator in which a conduction cooling loss between portions due to high thermal conductivity of a metal structure constituting a vacuum adiabatic body is reduced.
Embodiments also provide a refrigerator in which defrosting water due to a small thickness of a vacuum adiabatic body is prevented from being frozen to prevent a product from being broken down.
Embodiments also provide a refrigerator in which dew is prevented from being generated around a metal structure due to a temperature change during a defrosting operation of the refrigerator to improve reliability of a product.
In one embodiment, a vacuum adiabatic body includes: a thin pipe configured to connect an opening of the first plate to an opening of the second plate, the thin pipe being configured to define at least a portion of a wall of a third space of the plate; and an adiabatic material having an extension provided inside the thin pipe to perform an adiabatic operation with respect to the thin pipe and a head provided on an end of the extension at at least one side of the first plate and the second plate, wherein defrosting water passes through an inside of the adiabatic material.
A through pipeline passing through an inside of the adiabatic material to allow a material to pass between a first space and the second space may be further provided to allow the defrosting water to pass without being frozen.
The head may prevent the plates from being exposed to a space defined by each of the plates to prevent thermal conduction between the head and the plates from occurring.
The thin pipe may be a wrinkle pipe, and the wrinkle pipe may have a cross-section including: two vertical portions; two horizontal portions; and a rounded extension distance portion disposed between the two vertical portions and the two horizontal portions. Thus, a thermal conduction transfer amount may be reduced while using an inexpensive component that are capable of mass production to reduce a price of an adiabatic product using the vacuum adiabatic body.
The first space may have a low temperature compared to the second space, the head may be provided at a side of the first plate, and the head may be configured to block exposure of an adjacent portion of the opening of the first plate to the first space so as to interrupt convection cooling of the adjacent portion of the opening of the first plate. Thus, a cool air loss from a low-temperature space of a side of the first plate may be reduced. Here, the head may not be provided at a side of the second plate to allow heat to be transferred from a high-temperature side, thereby preventing a product from being damaged by the defrosting water and moisture of the peripheral portion thereof.
A pipe may be coupled to one side of the thin pipe to provide an equipment that is convenient for mass production and product application.
A guide plate may be coupled to one side or both sides of the thin pipe so that coupling and assembly of the guide plate is more simply. Here, when the opening of the plate corresponding to the one side of the thin pipe to which the guide plate is coupled is larger than the opening of the other plate, a worker may more simply mount a drain structure of the defrosting water. Alternatively, it may be possible to prolong a product lifespan by preventing a product failure and suppressing a stress occurrence.
In another embodiment, a refrigerator includes: a drain provided in a main body to discharge defrosting water generated in an evaporator to an outside of an accommodation space, wherein the drain includes: a thin pipe; a drain pipe provided inside the thin pipe to discharge the defrosting water; and an adiabatic material having an extension extending along the drain pipe to block heat transfer between the drain pipe and the thin pipe and a head provided at only one side of both sides of the extension, which is close to the accommodation space. Since the head is provided at only the one side, a convection operation in both directions may be balanced, and thermal equilibrium within the extension may be achieved. Cooling of the defrosting water and moisture in the peripheral portion may be suppressed, and leakage heat may be reduced.
The head may block convection cooling between the accommodation space and the wall surface of the accommodation space as the accommodation space is in close contact with the wall surface. Thus, the cooling leakage due to convection transmission may be prevented.
Convection heating of the thin pipe may be allowed on the other side of the extension, which is far from the accommodation space. Thus, external heat may be used as heat for dissolving the defrosting water.
The main body may use the vacuum adiabatic body, and the thin pipe may include an extension distance portion to increase in heat conduction distance, thereby reducing the heat conduction between the plate. Thus, it is possible to reduce an amount of conduction heat transfer flowing to the inside and outside of the vacuum adiabatic body.
The thin pipe may include: a main body including at least two extension distance portions; and a coupling portion coupled to each of the plates at an end of the main body to increase in distance for the conduction heat transfer.
In further another embodiment, a method for fabricating a refrigerator including a vacuum adiabatic body, which includes a thin pipe and is used as a main body, includes: providing a coupling structure to at least one side of the thin pipe; fixing the one side of the thin pipe to one of the plates; and fixing the other side of the thin pipe to the other one of the plates. Thus, a portion passing through the vacuum adiabatic body may be conveniently mounted in the refrigerator without being broken down.
A guide plate may be coupled to the other side of the thin pipe to more conveniently insert the portion into the vacuum adiabatic body.
The opening of the plate corresponding to the other side of the thin pipe may be larger than the opening of the plate corresponding to the one side of the thin pipe so that the portion is more easily inserted into one side.
The guide plate may have an outer diameter greater than that of the opening of the plate corresponding to the other side of the thin pipe to allow the guide plate to be hooked.
The thin pipe may include a main body having a plurality of wrinkles, and the coupling structure may be a pipe coupled to both ends of the main body. Thus, the portion that is capable of mass production may be used inexpensively.
Before the other side of the thin pipe and the other one of the plates are coupled to each other, the pair of plates may be coupled to each other. Thus, it may have an advantage of smoothing the supply and demand of components and a flow of manufacturing sites.
After the one side of the thin pipe is fixed to the one of the plates, the pair of plates may be coupled to each other. Thus, it may have an advantage of smoothing the supply and demand of components and a flow of fabricating sites.
According to the embodiment, it may be possible to reduce the convective heat loss leaking through the discharge structure of the defrosting water provided as the thin wall.
According to the embodiment, the conduction cooling loss between the portions due to the high thermal conductivity of the metal structure constituting the vacuum adiabatic body may be reduced.
According to the embodiment, it may be possible to prevent the freezing that may occur in the discharge passage of the narrow defrosting water by the cool air permeation, thereby preventing the product from being broken down.
According to the embodiment, it may be possible to prevent the occurrence of the dew around the metal structure due to the temperature change during the defrosting operation of the refrigerator and to improve the reliability of the product, and to prevent the failure of the product due to the freezing of the generated dew.
Hereinafter, exemplary embodiments will be described with reference to the accompanying drawings. The invention may, however, be embodied in many different forms and should not be construed as being limited to the embodiments set forth herein, and a person of ordinary skill in the art, who understands the spirit of the present invention, may readily implement other embodiments included within the scope of the same concept by adding, changing, deleting, and adding components; rather, it will be understood that they are also included within the scope of the present invention.
The drawings shown below may be displayed differently from the actual product, or exaggerated or simple or detailed components may be deleted, but this is intended to facilitate understanding of the technical idea of the present invention. It should not be construed as limited. However, it will try to show the actual shape as much as possible.
The following embodiments may be applied to the description of another embodiment unless the other embodiment does not collide with each other, and some configurations of any one of the embodiments may be modified in a state in which only a specific portion is modified in another configuration may be applied.
In the following description, the vacuum pressure means any pressure state lower than the atmospheric pressure. In addition, the expression that a vacuum degree of A is higher than that of B means that a vacuum pressure of A is lower than that of B.
Referring to
Components constituting a refrigeration cycle in which cool air is supplied into the cavity 9. In detail, the components include a compressor 4 for compressing a refrigerant, a condenser 5 for condensing the compressed refrigerant, an expander 6 for expanding the condensed refrigerant, and an evaporator 7 for evaporating the expanded refrigerant to take heat. As a typical structure, a fan may be installed at a position adjacent to the evaporator 7, and a fluid blown from the fan may pass through the evaporator 7 and then be blown into the cavity 9. A freezing load is controlled by adjusting the blowing amount and blowing direction by the fan, adjusting the amount of a circulated refrigerant, or adjusting the compression rate of the compressor, so that it is possible to control a refrigerating space or a freezing space.
Referring to
The first plate 10 may define at least a portion of a wall for a first space provided thereto. The second plate 20 may define at least a portion of a wall for a second space provided thereto. The first space and the second space may be defined as spaces having different temperatures. Here, the wall for each space may serve as not only a wall directly contacting the space but also a wall not contacting the space. For example, the vacuum adiabatic body of the embodiment may also be applied to a product further having a separate wall contacting each space.
Factors of heat transfer, which cause loss of the adiabatic effect of the vacuum adiabatic body, are thermal conduction between the first and second plates 10 and 20, heat radiation between the first and second plates 10 and 20, and gas conduction of the vacuum space 50.
Hereinafter, a heat resistance unit provided to reduce adiabatic loss related to the factors of the heat transfer will be provided. Meanwhile, the vacuum adiabatic body and the refrigerator of the embodiment do not exclude that another adiabatic means is further provided to at least one side of the vacuum adiabatic body. Therefore, an adiabatic means using foaming or the like may be further provided to another side of the vacuum adiabatic body.
First, referring to
The support 30 may be provided to reduce the deformation of the vacuum space 50. The support 30 includes a bar 31. The bar 31 may extend in a substantially vertical direction with respect to the plates to support a distance between the first plate and the second plate. A support plate 35 may be additionally provided on at least any one end of the bar 31. The support plate 35 may connect at least two or more bars 31 to each other to extend in a horizontal direction with respect to the first and second plates 10 and 20. The support plate 35 may be provided in a plate shape or may be provided in a lattice shape so that an area of the support plate contacting the first or second plate 10 or 20 decreases, thereby reducing heat transfer. The bars 31 and the support plate 35 are fixed to each other at at least a portion so as to be inserted together between the first and second plates 10 and 20. The support plate 35 contacts at least one of the first and second plates 10 and 20, thereby preventing the deformation of the first and second plates 10 and 20. In addition, based on the extension direction of the bars 31, a total sectional area of the support plate 35 is provided to be greater than that of the bars 31, so that heat transferred through the bars 31 may be diffused through the support plate 35.
The support 30 may be made of a resin selected from PC, glass fiber PC, low outgassing PC, PPS, and LCP to obtain high compressive strength, a low outgassing and water absorption rate, low thermal conductivity, high compressive strength at a high temperature, and superior processability.
A radiation resistance sheet 32 for reducing heat radiation between the first and second plates 10 and 20 through the vacuum space 50 will be described. The first and second plates 10 and 20 may be made of a stainless material capable of preventing corrosion and providing a sufficient strength. Since the stainless material has a relatively high emissivity of 0.16, a large amount of radiation heat may be transferred. In addition, the support 30 made of the resin has a lower emissivity than the plates, and is not entirely provided to inner surfaces of the first and second plates 10 and 20. Thus, the support 30 does not have great influence on the radiation heat. Therefore, the radiation resistance sheet 32 may be provided in a plate shape over a majority of the area of the vacuum space 50 so as to concentrate on reduction of radiation heat transferred between the first and second plates 10 and 20. A product having a low emissivity may be used as the material of the radiation resistance sheet 32. In an embodiment, an aluminum foil having an emissivity of 0.02 may be used as the radiation resistance sheet 32. Also, since the transfer of radiation heat may not be sufficiently blocked using one radiation resistance sheet, at least two radiation resistance sheets 32 may be provided at a certain distance so as not to contact each other. Also, at least one radiation resistance sheet may be provided in a state of contacting the inner surface of the first or second plate 10 or 20.
Referring back
In this embodiment, the vacuum adiabatic body may be fabricated without the radiation resistance sheet 32.
Referring to
In this embodiment, the vacuum adiabatic body may be fabricated without the support 30. That is to say, the porous material 33 may perform the function of the radiation resistance sheet 32 and the function of the support 30 together.
First, a conductive resistance sheet proposed in
The conductive resistance sheet 60 may be provided with the seal 61 at which both ends of the conductive resistance sheet 60 are sealed to define at least a portion of the wall for the third space and maintain the vacuum state. The conductive resistance sheet 60 may be provided as a thin foil in unit of micrometer so as to reduce the amount of heat conducted along the wall for the third space. The seals 61 may be provided as a weld. That is, the conductive resistance sheet 60 and the plates 10 and 20 may be fused to each other. To cause a fusing operation between the conductive resistance sheet 60 and the plates 10 and 20, the conductive resistance sheet 60 and the plates 10 and 20 may be made of the same material, and a stainless material may be used as the material. The seal 61 may not be limited to the weld and may be provided through a process such as cocking. The conductive resistance sheet 60 may be provided in a curved shape. Thus, a thermal conduction distance of the conductive resistance sheet 60 is provided longer than a linear distance of each of the plates so that an amount of thermal conduction is further reduced.
A change in temperature occurs along the conductive resistance sheet 60. Therefore, to block the heat transfer to the outside of the conductive resistance sheet 60, a shield 62 may be provided at the outside of the conductive resistance sheet 60 so that an adiabatic operation occurs. In other words, in case of the refrigerator, the second plate 20 has a high temperature, and the first plate 10 has a low temperature. In addition, thermal conduction from high temperature to low temperature occurs in the conductive resistance sheet 60, and thus the temperature of the conductive resistance sheet 60 is suddenly changed. Therefore, when the conductive resistance sheet 60 is opened with respect to the outside thereof, the heat transfer through the opened place may seriously occur. To reduce the heat loss, the shield 62 is provided outside the conductive resistance sheet 60. For example, when the conductive resistance sheet 60 is exposed to any one of the low-temperature space and the high-temperature space, the conductive resistance sheet 60 does not serve as a conductive resistor as well as the exposed portion thereof, which is not preferable.
The shield 62 may be provided as a porous material contacting an outer surface of the conductive resistance sheet 60. The shield 62 may be provided as an adiabatic structure, e.g., a separate gasket, which is placed at the outside of the conductive resistance sheet 60. The shield 62 may be provided as a portion of the vacuum adiabatic body, which is provided at a position facing a corresponding conductive resistance sheet 60 when the main body-side vacuum adiabatic body is closed with respect to the door-side vacuum adiabatic body. To reduce the heat loss even when the main body and the door are opened, the shield 62 may be provided as a porous material or a separate adiabatic structure.
A conductive resistance sheet proposed in
In the door-side vacuum adiabatic body, it is difficult to place the conductive resistance sheet 60 on a front end of the vacuum space, i.e., an edge side portion of the vacuum space. This is because, unlike the main body, a corner edge of the door is exposed to the outside. In more detail, if the conductive resistance sheet 60 is placed on the front end of the vacuum space, the corner edge of the door is exposed to the outside, and hence there is a disadvantage in that a separate adiabatic portion has to be configured so as to thermally insulate the conductive resistance sheet 60.
A conductive resistance sheet proposed in
A heat transfer path between the first and second plates 10 and 20 will be described with reference back to
The transfer heat may be changed depending on various depending on various design dimensions. For example, the support may be changed so that the first and second plates 10 and 20 may endure a vacuum pressure without being deformed, the vacuum pressure may be changed, the distance between the plates may be changed, and the length of the conductive resistance sheet may be changed. The transfer heat may be changed depending on a difference in temperature between the spaces (the first and second spaces) respectively provided by the plates. In the embodiment, a preferred configuration of the vacuum adiabatic body has been found by considering that its total heat transfer amount is smaller than that of a typical adiabatic structure formed by foaming polyurethane. In a typical refrigerator including the adiabatic structure formed by foaming the polyurethane, an effective heat transfer coefficient may be proposed as 19.6 mW/mK.
By performing a relative analysis on heat transfer amounts of the vacuum adiabatic body of the embodiment, a heat transfer amount by the gas conduction heat {circle around (3)} may become the smallest. For example, the heat transfer amount by the gas conduction heat {circle around (3)} may be controlled to be equal to or smaller than 4% of the total heat transfer amount. A heat transfer amount by solid conduction heat defined as a sum of the surface conduction heat {circle around (1)} and the support conduction heat {circle around (2)} is the largest. For example, the heat transfer amount by the solid conduction heat may reach 75% of the total heat transfer amount. A heat transfer amount by the radiation transfer heat {circle around (3)} is smaller than the heat transfer amount by the solid conduction heat but larger than the heat transfer amount of the gas conduction heat. For example, the heat transfer amount by the radiation transfer heat {circle around (3)} may occupy about 20% of the total heat transfer amount.
According to the heat transfer distribution, effective heat transfer coefficients (eK: effective K) (W/mK) of the surface conduction heat {circle around (1)}, the support conduction heat {circle around (2)}, the gas conduction heat {circle around (3)}, and the radiation transfer heat {circle around (4)} may have an order of Math Equation 1 when comparing the transfer heat {circle around (1)}, {circle around (2)}, {circle around (3)}, and {circle around (4)}.
eKsolid conduction heat>eKradiation conduction heat>eKgas conduction heat [Equation 1]
Here, the effective heat transfer coefficient (eK) is a value that may be measured using a shape and temperature differences of a target product. The effective heat transfer coefficient (eK) is a value that may be obtained by measuring a total heat transfer amount and a temperature at least one portion at which heat is transferred. For example, a calorific value (W) is measured using a heating source that may be quantitatively measured in the refrigerator, a temperature distribution (K) of the door is measured using heats respectively transferred through a main body and an edge of the door of the refrigerator, and a path through which heat is transferred is calculated as a conversion value (m), thereby evaluating an effective heat transfer coefficient.
The effective heat transfer coefficient (eK) of the entire vacuum adiabatic body is a value given by k=QL/AΔT. Here, Q denotes a calorific value (W) and may be obtained using a calorific value of a heater. A denotes a sectional area (m2) of the vacuum adiabatic body, L denotes a thickness (m) of the vacuum adiabatic body, and ΔT denotes a temperature difference.
For the surface conduction heat, a conductive calorific value may be obtained through a temperature difference ΔT between an entrance and an exit of the conductive resistance sheet 60 or 63, a sectional area A of the conductive resistance sheet, a length L of the conductive resistance sheet, and a thermal conductivity (k) of the conductive resistance sheet (the thermal conductivity of the conductive resistance sheet is a material property of a material and may be obtained in advance). For the support conduction heat, a conductive calorific value may be obtained through a temperature difference ΔT between an entrance and an exit of the support 30, a sectional area A of the support, a length L of the support, and a thermal conductivity (k) of the support. Here, the thermal conductivity of the support may be a material property of a material and may be obtained in advance. The sum of the gas conduction heat {circle around (3)}, and the radiation transfer heat {circle around (4)} may be obtained by subtracting the surface conduction heat and the support conduction heat from the heat transfer amount of the entire vacuum adiabatic body. A ratio of the gas conduction heat {circle around (3)}, and the radiation transfer heat {circle around (4)} may be obtained by evaluating radiation transfer heat when no gas conduction heat exists by remarkably lowering a vacuum degree of the vacuum space 50.
When a porous material is provided inside the vacuum space 50, porous material conduction heat {circle around (5)} may be a sum of the support conduction heat {circle around (2)} and the radiation transfer heat {circle around (4)}. The porous material conduction heat may be changed depending on various variables including a kind, an amount, and the like of the porous material.
According to an embodiment, a temperature difference ΔT1 between a geometric center formed by adjacent bars 31 and a point at which each of the bars 31 is located may be provided to be less than 0.5° C. Also, a temperature difference ΔT2 between the geometric center formed by the adjacent bars 31 and an edge of the vacuum adiabatic body may be provided to be less than 0.5° C. In the second plate 20, a temperature difference between an average temperature of the second plate and a temperature at a point at which a heat transfer path passing through the conductive resistance sheet 60 or 63 meets the second plate may be the largest. For example, when the second space is a region hotter than the first space, the temperature at the point at which the heat transfer path passing through the conductive resistance sheet meets the second plate becomes lowest. Similarly, when the second space is a region colder than the first space, the temperature at the point at which the heat transfer path passing through the conductive resistance sheet meets the second plate becomes highest.
This means that the amount of heat transferred through other points except the surface conduction heat passing through the conductive resistance sheet should be controlled, and the entire heat transfer amount satisfying the vacuum adiabatic body may be achieved only when the surface conduction heat occupies the largest heat transfer amount. For this, a temperature variation of the conductive resistance sheet may be controlled to be larger than that of the plate.
Physical characteristics of the components constituting the vacuum adiabatic body will be described. In the vacuum adiabatic body, force due to a vacuum pressure is applied to all of the components. Therefore, a material having a strength (N/m2) of a certain level may be used.
Under such circumferences, the plates 10 and 20 and the side frame 70 may be made of a material having sufficient strength with which the plates 10 and 20 are not damaged by even the vacuum pressure. For example, when the number of bars 31 decreases to limit the support conduction heat, the deformation of each of the plates occurs due to the vacuum pressure, which may bad influence on an outer appearance of the refrigerator. The radiation resistance sheet 32 may be made of a material that has a low emissivity and may be easily subjected to thin film processing. Also, the radiation resistance sheet 32 has to ensure strength enough without being deformed by an external impact. The support 30 is provided to strength that is enough to support the force by the vacuum pressure and endure the external impact, and is to have processability. The conductive resistance sheet 60 may be made of a material that has a thin plate shape and may endure the vacuum pressure.
In an embodiment, the plate, the side frame, and the conductive resistance sheet may be made of stainless materials having the same strength. The radiation resistance sheet may be made of aluminum having weaker strength than that of each of the stainless materials. The support may be made of a resin having weaker strength than that of the aluminum.
Unlike the strength from the point of view of the materials, an analysis from the point of view of stiffness is required. The stiffness (N/m) may be a property that is not be easily deformed. Thus, although the same material is used, its stiffness may vary depending on its shape. The conductive resistance sheets 60 or 63 may be made of a material having strength, but the stiffness of the material may be low so as to increase in heat resistance and minimize the radiation heat as the conductive resistance sheet is uniformly spread without any roughness when the vacuum pressure is applied. The radiation resistance sheet 32 requires stiffness having a certain level so as not to contact another component due to deformation. Particularly, an edge of the radiation resistance sheet may generate the conduction heat due to drooping caused by the self-load of the radiation resistance sheet. Therefore, the stiffness having the certain level is required. The support 30 requires a stiffness enough to endure compressive stress from the plate and the external impact.
In an embodiment, the plate and the side frame may have the highest stiffness so as to prevent the deformation caused by the vacuum pressure. The support, particularly, the bar may have the second highest stiffness. The radiation resistance sheet may have stiffness that is lower than that of the support but higher than that of the conductive resistance sheet. Lastly, the conductive resistance sheet may be made of a material that is easily deformed by the vacuum pressure and has the lowest stiffness.
Even when the porous material 33 is filled in the vacuum space 50, the conductive resistance sheet may have the lowest stiffness, and each of the plate and the side frame may have the highest stiffness.
Hereinafter, the vacuum pressure may be determined depending on internal states of the vacuum adiabatic body. As already described above, a vacuum pressure is to be maintained inside the vacuum adiabatic body so as to reduce heat transfer. Here, it will be easily expected that the vacuum pressure is maintained as low as possible so as to reduce the heat transfer.
The vacuum space may resist to heat transfer by only the support 30. Here, a porous material 33 may be filled with the support inside the vacuum space 50 to resist to the heat transfer. The heat transfer to the porous material may resist without applying the support.
The case in which only the support is applied will be described.
Referring to
Referring to
In the embodiment, a point at which the vacuum pressure is not substantially decreased any more even though the gas is exhausted by operating the vacuum pump is set to the lowest limit of the vacuum pressure used in the vacuum adiabatic body, thereby setting the minimum internal pressure of the vacuum space 50 to 1.8×10−6 Torr.
Referring to
It was seen that, since the size of the gap is small at a point corresponding to a typical effective heat transfer coefficient of 0.0196 W/mK, which is provided to an adiabatic material formed by foaming polyurethane, the vacuum pressure is 2.65×10−1 Torr even when the size of the gap is 2.76 mm. Meanwhile, it was seen that the point at which reduction in adiabatic effect caused by the gas conduction heat is saturated even though the vacuum pressure decreases is a point at which the vacuum pressure is approximately 4.5×10−3 Torr. The vacuum pressure of 4.5×10−3 Torr may be defined as the point at which the reduction in adiabatic effect caused by the gas conduction heat is saturated. Also, when the effective heat transfer coefficient is 0.1 W/mK, the vacuum pressure is 1.2×10−2 Torr.
When the vacuum space 50 is not provided with the support but provided with the porous material, the size of the gap ranges from a few micrometers to a few hundreds of micrometers. In this case, the amount of radiation heat transfer is small due to the porous material even when the vacuum pressure is relatively high, i.e., when the vacuum degree is low. Therefore, an appropriate vacuum pump is used to adjust the vacuum pressure. The vacuum pressure appropriate to the corresponding vacuum pump is approximately 2.0×10−4 Torr. Also, the vacuum pressure at the point at which the reduction in adiabatic effect caused by the gas conduction heat is saturated is approximately 4.7×10−2 Torr. Also, the pressure where the reduction in adiabatic effect caused by gas conduction heat reaches the typical effective heat transfer coefficient of 0.0196 W/mK is 730 Torr.
When the support and the porous material are provided together in the vacuum space, a vacuum pressure may be created and used, which is middle between the vacuum pressure when only the support is used and the vacuum pressure when only the porous material is used. When only the porous material is used, the lowest vacuum pressure may be used.
The vacuum adiabatic body includes a first plate defining at least a portion of a wall for the first space and a second plate defining at least a portion of a wall for the second space and having a temperature different from the first space. The first plate may include a plurality of layers. The second plate may include a plurality of layers
The vacuum adiabatic body may further include a seal configured to seal the first plate and the second plate so as to provide a third space that is in a vacuum state and has a temperature between a temperature of the first space and a temperature of the second space.
When one of the first plate and the second plate is disposed in an inner space of the third space, the plate may be represented as an inner plate. When the other one of the first plate and the second plate is disposed in an outer space of the third space, the plate may be represented as an outer plate. For example, the inner space of the third space may be a storage room of the refrigerator. The outer space of the third space may be an outer space of the refrigerator.
The vacuum adiabatic body may further include a support that maintains the third space.
The vacuum adiabatic body may further include a conductive resistance sheet connecting the first plate to the second plate to reduce an amount of heat transferred between the first plate and the second plate.
At least a portion of the conductive resistance sheet may be disposed to face the third space. The conductive resistance sheet may be disposed between an edge of the first plate and an edge of the second plate. The conductive resistance sheet may be disposed between a surface on which the first plate faces the first space and a surface on which the second plate faces the second space. The conductive resistance sheet may be disposed between a side surface of the first plate and a side surface of the second plate.
At least a portion of the conductive resistance sheet may extend in a direction that is substantially the same as the direction in which the first plate extends.
A thickness of the conductive resistance sheet may be thinner than at least one of the first plate or the second plate. The more the conductive resistance sheet decreases in thickness, the more heat transfer may decrease between the first plate and the second plate.
The more the conductive resistance sheet decreases in thickness, the more it may be difficult to couple the conductive resistance sheet between the first plate and the second plate.
One end of the conductive resistance sheet may be disposed to overlap at least a portion of the first plate. This is to provide a space for coupling one end of the conductive resistance sheet to the first plate. Here, the coupling method may include welding.
The other end of the conductive resistance sheet may be arranged to overlap at least a portion of the second plate. This is to provide a space for coupling the other end of the conductive resistance sheet to the second plate. Here, the coupling method may include welding.
As another embodiment of replacing the conductive resistance sheet, the conductive resistance sheet may be deleted, and one of the first plate and the second plate may be thinner than the other. In this case, any thickness may be greater than that of the conductive resistance sheet. In this case, any length may be greater than that of the conductive resistance sheet. With this configuration, it is possible to reduce the increase in heat transfer by deleting the conductive resistance sheet. Also, this configuration may reduce difficulty in coupling the first plate to the second plate.
At least a portion of the first plate and at least a portion of the second plate may be disposed to overlap each other. This is to provide a space for coupling the first plate to the second plate. An additional cover may be disposed on any one of the first plate and the second plate, which has a thin thickness. This is to protect the thin plate.
The vacuum adiabatic body may further include an exhaust port for discharging a gas in the vacuum space.
Hereinafter, a configuration for discharging defrosting water will be briefly described.
Referring to
As an operation of the evaporator 7 is accumulated, frost is accumulated on an outer surface of the evaporator 7, and when a certain amount of frost is accumulated, a defrosting operation is performed to remove the frost.
The defrosting operation may be performed by applying heat to the frost, and the defrosting water removed by the heat may be collected in a drain pan 71 and then discharged to the outside.
A drain 72 is provided on a wall of the main body 2 connecting the drain pan 71 to the outside. The main body 2 may be provided as a vacuum adiabatic body, and the drain 72 may be provided by opening the vacuum adiabatic body. A drain pipe 85 guiding the defrosting water may pass through the drain 72.
Since the adiabatic wall of the vacuum adiabatic body is in a high vacuum state, it may be provided with a significantly thinner thickness than the foamed adiabatic wall provided by typical urethane foam. Likewise, the drain 72 is also provided to a thin thickness. Nevertheless, it is necessary to reduce a loss of cool air that may be caused by heat conduction and tropical flow and to prevent pipeline blockage due to freezing of the defrosting water. In addition, it is preferable to reduce an occurrence of dew generated by the temperature change in the peripheral portion, thereby improving reliability of the device.
Hereinafter, a configuration and operation of a structure providing the drain capable of achieving the above object will be described.
Referring to
The wrinkle pipe 90 may be understood as a kind of the wrinkle-type conductive resistance sheet 63, but has the advantage of being capable of mass production due to the convenience of molding. The wrinkle pipe 90 may also be called a thin film tube, which is a tube having a thin thickness by naming the wrinkle-type conductive resistance sheet 63 together. The thin pipe may be provided to a thin thickness to resist to thermal conductivity. The thin pipe may resist to the heat conduction by using a narrow heat conduction area. The thin pipe may be provided in a state in which wrinkles are removed if it resists to only conduction, but it is preferable that wrinkles are provided to lengthen a heat conduction path. The configuration of the wrinkle pipe and the wrinkle-type conductive sheet may be clearly understood in the description of each of the portions.
The wrinkle pipe 90 may be provided in a substantially cylindrical shape. The wrinkle pipe 90 includes a cylindrical body 93 (or a main body) in which many wrinkles are provided in an annular shape, one coupling portion 91 coupled to the first plate 10, and the other coupling portion 92 coupled to the second plate 20. The coupling portions 91 and 92 serve to seal the third space and may be coupled to each relative portion by welding or the like.
The wrinkle pipe adiabatic material 80 includes a head 81 contacting an inner surface of the first plate 10 that provides at least one wall of the first space inside the refrigerator, and an extension 82 extending from the head 81 to the second plate 20, and a hole 83 passing through the inside of each of the head 81 and the extension 82.
Although the defrosting water is provided in the hole 83 as an example, a material that is not limited to the defrosting water may be discharged from the inside of the refrigerator to the outside of the refrigerator. A drain pipe 85 guiding the defrosting water to the outside may be inserted into the hole 83. When other materials or articles are discharged through the drain pipe, the drain pipe may be referred to as a through pipeline, and a case in which a structure such as an electric wire passes through the hole 83 may be sufficiently considered. However, the case in which the drain pipe passes through the hole 83 may be most preferably illustrated.
Referring to
The extension 82 of the wrinkle pipe adiabatic material 80 may be interposed between the inner surface of the wrinkle pipe 90 and the drain pipe 85 to block heat exchange between the wrinkle pipe 90 and the drain pipe 85.
The head 81 of the wrinkle pipe adiabatic material 80 may extend from an upper end of the extension 82. The head 81 may extend concentrically along the inner surface of the first plate 10. The head 81 may be provided as a portion having a predetermined diameter and a predetermined thickness.
The head 81 may prevent the first plate 10 from being exposed to the first space. Thus, the heat transfer by natural convection and forced convection from the cool air within the refrigerator to the first plate 10 may be blocked. In other words, the first plate 10 overlapping the head 81 may have a temperature higher than that of a gas within the refrigerator. Of course, this case may be limited in the case of the refrigerator.
Here, it is necessary to note that the head 81 is provided only to the first plate 10 and is not provided to the second plate 20. Thus, the second plate 20 may perform the natural convection and the forced convection on the whole portion with respect to a gas outside the refrigerator. In other words, in view of the opening of each plate, the second plate 20 has the convective heat exchange with the all portions connected to the openings. On the other hand, the first plate 10 may be heat-exchanged with air within the refrigerator from a portion that is spaced a predetermined distance from the opening, i.e., a point that gets out of the head 81.
As a result, a distance for the conduction heat transfer from the inside to the outside of the refrigerator increases so much. In other words, when observed from a center of the first plate 10, a temperature is lowest at a point aligned with an outer edge of the head 81, and then, the temperature may increase as it enters. That is, a portion of the first plate 10 may function as a conductive resistance portion that resists to the thermal conduction.
Of course, a place on which the function of the largest conductive resistance in the drain 72 may be the wrinkle pipe 90. Nevertheless, the lack of a cool air loss to the wrinkle pipe 90 may be supplemented by a method of blocking the convection between the air inside the refrigerator and the plate by using the head 81.
On the other hand, the second plate 20 has the convective heat exchange with the air outside the refrigerator at all portions connected to the openings. Thus, the heat outside the refrigerator may be introduced along the wrinkle pipe 90 by a predetermined distance.
In this case, freezing of the defrosting water inside the drain pipe 85 may be prevented to prevent the drain pipe 85 from being blocked. In addition, according to changes in an operation mode such as a normal operation and a defrosting operation, dew that may be generated on the periphery of the drain pipe 85, the wrinkle pipe 90, and the plates 10 and 20 may be evaporated through a predetermined heat. Thus, it is possible to prevent the product from being damaged due to freezing of the dew and to prevent the product from being degraded due to moisture.
A main body 93 of the wrinkle pipe 90 is provided with a plurality of wrinkles. The wrinkles are intended to prevent the cool air loss by increasing in heat conduction length between the plates 10 and 20. Like the wrinkle-type conductive resistance sheet 63, the thickness may be reduced to reduce the conduction heat transfer amount, and also, the conduction heat transfer amount may be further reduced by using the pleats.
A wrinkle unit of the wrinkle pipe 90 may include two vertical portions 95 and 98, two horizontal portions 96 and 97, and an extension distance portion 94 provided therebetween. The extension distance portion 94 has a shape connecting the horizontal portions 96 and 97 to each other in a round manner and may be provided larger than a width of each of the horizontal portions 96 and 97.
According to the above shape, when only the vertical portions 95 and 98 are provided, the extension distance portion 94 may increase in path of the cool air and heat, which flow along the wrinkle pipe when compared to the case in which only the vertical portions 95 and 98 and the horizontal portions 96 and 97 are provided. In other words, it is possible to obtain an effect of further reducing the heat transfer amount by the conduction heat transfer.
Here, the meanings of the vertical and horizontal (the horizontal plane and the vertical plane are the same) refer to two extension directions crossing each other, and not only orthogonal directionality.
The wrinkle pipe adiabatic material 80 may be processed by a foaming material, an elastically deformable material, a soft material, a sealing material, an intervening or mixed material, or adding of the seal. Thus, a contact surface between the wrinkle pipe 90 and the extension 82, a contact surface between the drain pipe 854 and the extension 82, and a contact surface between the head 81 and the first plate 10 may be completely sealed. Thus, convection cooling by the natural convection and the forced convection through the contact surfaces between the portions may be blocked.
Referring to
Referring to
The cases are divided with reference to
In the horizontal axis length of the graph of
A temperature change curve according to each of the cases will be described.
In the case (a) of the adiabatic wall using the foam, a distance of the conduction path and a temperature change are proportional to each other. In the case (b) using only the wrinkle pipe, although the cool air loss is reduced by the adiabatic effect of the wrinkle pipe itself, it may be observed that the cool air loss is greater than the other two cases.
In the case (c) of the embodiment, when compared to the case (d) using the wrinkle pipe 90 and the wrinkle pipe adiabatic material having the heads at both the ends, there is the cool air loss. However, since a high temperature is maintained in the path {circle around (2)} of the vacuum space, cooling of the defrosting water may be prevented. In other words, the convective heating of the plate contacting the wrinkle pipe from the outside may be allowed to prevent the defrosting water from being cooled.
Also, in the case (c) of the embodiment, the cool air loss may be reduced due to the low thermal conduction when compared to the case (b) in which only the wrinkle pipe is used.
As a result, an operation in which a certain amount of heat is absorbed from the heat inside the refrigerator to the drain 72 to prevent the defrosted water from being frozen and an operation in which the head 81 is provided on the wrinkle pipe adiabatic material 80 only inside the refrigerator to prevent the air cold loss inside the refrigerator from occurring may be performed at the same time.
Hereinafter, another example of focusing on the viewpoint of fixing the drain will be described.
The contents described with reference to
In
Referring to
When compared to the wrinkle pipe 90, the maximum diameter of the wrinkle-type conductive resistance sheet 63 is considerably large. Thus, the wrinkle-type conductive resistance sheet 63 may be produced in a custom-made method using welding or the like between the portions, and as a result, a high production cost may be required.
One side pipe 101 may be coupled to one side of the wrinkle-type conductive resistance sheet 63, and the other side pipe 102 may be coupled to the other side of the wrinkle-type conductive resistance sheet 63. A maximum diameter L2 of the wrinkle-type conductive resistance sheet 63 is considerably larger than a diameter L1 of each of the one side pipe 101 and the other side pipe 102. Here, the pipe may be configured to couple the wrinkle pipe and may be referred to as a coupling structure for the thin pipe. When the thin pipe has a separate coupling structure, a separate coupling structure such as a pipe may not be required.
A support plate 35 and a bar 31 providing a support 30 may be provided inside the vacuum space.
A wrinkle pipe adiabatic material 80 may be provided inside the wrinkle-type conductive resistance sheet 63 and on an inner surface of the first plate 10, like the original embodiment, and thus, convective heat transfer may be reduced.
Referring to
The first process will be described.
First, a support plate 35 disposed at one side is seated on the plates 10 and 20 disposed at one side (S1). Here, one side and the other side means any one of the portions that may be provided in a pair and do not have directionality. The same goes for the following.
A radiation resistance sheet 32 is seated on the one side support plate 35 (S2). The radiation resistance sheet 32 may be placed on the one side support plate 35 to be fixed without moving.
Thereafter, the other side support plate 35 may be seated to correspond to the one side support plate 35. The one side support plate and the other side support plate may be understood as portions corresponding to inner surfaces of the first and second plates, respectively.
In the second process, one side pipe 101 and the other side pipe 102 may be coupled to both opened ends of the wrinkle-type conductive resistance sheet 63 (S4). When this process is ended, a wrinkle-type assembly in which the pipe and the wrinkle-type conductive resistance sheet are integrated may be provided.
Thereafter, a third process in which the two portions are integrated is performed.
First, the wrinkle-type assembly may be seated and inserted into a through-hole of the one side plate (S10). The through-hole of the one side plate may have a diameter so that the pipe 101 is inserted and may be provided before the support plate is placed (S1), but is not limited thereto. Since the through-hole of the one-side plate is less than a maximum diameter of the wrinkle type conductive resistance sheet, the wrinkle-type conductive resistance sheet may be fixed in position without being separated from the through-hole.
Thereafter, the inserted one side pipe 101 may be coupled to the one side plate 10 (S11). Here, both portions may be metal portions and be coupled to each other through welding or the like.
Thereafter, the other side plate 20 is seated so that the other side pipe 102 is inserted into the through-hole of the other side plate 20 (S12), and the other side pipe 102 and the other side plate 20 are coupled to each other (S13).
Here, even in the process (S12) in which the other side pipe 102 is seated on the other side plate 20, since the through-hole of the other side plate is less than the maximum diameter of the wrinkle type conductive resistance sheet, the wrinkle-type conductive resistance shape may be fixed in position without being separated from the through-hole.
The coupling (S11 to S13) between the pipes 101 and 102 and the plates 10 and 20 may be performed in different manners.
For example, before the process (S11) of coupling the one side pipe 101 to the one side plate 10 by the method such as the welding, in a state in which only the one side pipe 101 and the one side plate 10 are seated, the other side pipe 102 and the other side plate 20 may also be seated (S12). Thereafter, the coupling (S11) of the one side pipe 101 and the one side plate 10 and the coupling (S13) of the other side pipe 102 and the other side plate 20 may be completed.
Also, the coupling of the one side pipe 101 and the one side plate 10, and the coupling of the other side pipe 102 and the other side plate 20, i.e., the two coupling processes may be performed at once or may be performed separately.
The wrinkle-type conductive resistance sheet 63 having the pipe in the pair of plates 10 and 20 may be accurately positioned through the above-described processes.
Thereafter, the pair of plates 10 and 20 are sealed to each other (S14), and air may be drawn out to create an inner vacuum space (S15).
In the above embodiment, if there is an integrated boss enough to overlap the plate at an end of the wrinkle-type conductive sheet, the pipes 101 and 102 may not be used as separate components but may be fixed in position relative to the plates. However, to deform a shape that is enough to change the maximum diameter and the minimum diameter of the wrinkle-type conductive resistance sheet, a separate pipe may be applied because of difficulty in processing.
Hereinafter, another embodiment will be described in which the viewpoint of fixing the drain is mainly observed. The contents described with reference to
In
Referring to
As may be clearly understood through the above description, the wrinkle pipe 90 may be provided to a maximum diameter less than that of the wrinkle-type conductive resistance sheet 63. As a result, the wrinkle pipe 90 may be more conveniently and simply mounted on the vacuum adiabatic body.
A structure of the drain according to further another embodiment will be described in detail.
One side of the wrinkle pipe 90 may be coupled to the first plate 10, and the other side of the wrinkle pipe 90 may be coupled to the second plate 10. One side of the wrinkle pipe 90 may be indirectly coupled to the first plate 10 in a state in which the guide plate 111 is coupled. The other side of the wrinkle pipe 90 may be coupled directly or indirectly to the second plate 20 in a state in which the other side pipe 102 is coupled.
A through-holes of the first plate and a through-holes of the second plate may have different diameters. This is because it is difficult to manage an alignment dimension of the two through-holes in a production process of a product. In other words, no matter how precise the position is, quality of the product may be affected because misaligned positions occur in the two through-holes in spite of the small diameter.
To prevent this phenomenon, according to further another embodiment, the through-hole of the first plate 10 may be greater than the through-hole of the second plate 20. When the two plates 10 and 20 are aligned vertically, an area of the through-hole of the first plate 10 includes an entire area of the through-hole of the second plate 20.
Accordingly, even if the position is slightly distorted after the plate 10 and 20 are fabricated, the guide plate 111 may close the through-hole of the first plate 10 in the state in which the wrinkle pipe 90 is seated on the second plate 20. Thus, there is no problem in mounting the wrinkle pipe 90 and sealing the vacuum space.
To provide the above-described configuration and operation, a diameter of each portion providing the drain may have the following mutual relation.
First, an outer diameter L6 of the guide plate 111 may be provided to be greater than a diameter L7 of the through-hole of the first plate 10. Accordingly, the guide plate 111 may achieve the sealing between the plates.
The diameter L7 of the through-hole of the first plate 10 may be provided to be greater than or equal to a maximum diameter L4 of the wrinkle pipe. Accordingly, the wrinkle pipe 90 may be mounted into the vacuum space in the state in which the plates 10 and 20 are coupled. Of course, the diameter L7 of the through-hole of the first plate 10 may be provided to the same maximum diameter L4 of the wrinkle pipe. However, due to convenience of fabrication and the characteristics of the portion made of a metal, the diameter L7 of the through-hole of the first plate 10 may be slightly greater than the maximum diameter L4 of the wrinkle pipe.
An inner diameter L8 of the guide plate 111 may be provided to be less than the maximum diameter L4 of the wrinkle pipe and greater than a diameter L3 of an end of the wrinkle pipe 90. Accordingly, the guide plate 111 may be supported by being hooked with the end of the wrinkle pipe. Here, the diameter of the end of the wrinkle pipe may be referred to as its outer diameter.
The diameter L3 of the end of the wrinkle pipe 90 may be provided to be equal or greater than the diameter L5 of the other side pipe 102. Accordingly, the coupling of the wrinkle pipe and the other side pipe may be easily performed.
A diameter L9 of the through-hole of the second plate may be provided to be greater than each of the diameter L3 of the end of the wrinkle pipe and the diameter of the other side pipe 102. Accordingly, the wrinkle pipe 90 may be coupled to the second plate 20. Of course, for reliable welding between the portions in the future, the diameter L9 of the through-hole of the second plate may be provided to be less than the maximum diameter L4 of the wrinkle pipe. Accordingly, it is possible to improve the convenience of the sealing. Furthermore, the diameter L9 of the through-hole of the second plate is not provided too large, so that a distance between both the portions decreases as much as possible. Accordingly, it is desirable to increase in reliability of the sealing operation through the welding or the like.
On the other hand, for example, the place to which the other side pipe 102 is coupled may be the second plate 20 of the first and second plates 10 and 20, i.e., the plate providing at least a portion of the wall in the space inside the refrigerator. The reason is that it is preferable to guide the withdrawal of the drain pipe by a predetermined length and to eliminate the additionally protruding pipe because the space inside the refrigerator is narrow.
Without being limited thereto, the other side pipe 102 may be installed on the inside of the refrigerator, that is, on the first plate 10. In this case, an increase in cool air transfer to the wrinkle pipe, which is generated when the guide plate 111 is installed inside the refrigerator may be suppressed. In other words, when the guide plate 111 is installed inside the refrigerator, a thickness of the portion that is heat-conducted as much as the guide plate 111 may increase in thickness at a place that is aligned vertically with the head 81 of the wrinkle pipe adiabatic material.
In this case, there is a disadvantage that the reduction in cool air loss due to the convective heat transfer, which may be obtained by the head 81 of the wrinkle pipe adiabatic material, may be lowered, but when the guide plate is thinly provided, it may be ignored because capacity of the cool air conduction is reduced.
Referring to
The first process and the second process may be performed at different times in separate places, like another embodiment.
The wrinkle pipe assembly may be inserted into a through-hole of the plate (S30). When the wrinkle pipe assembly is inserted into the through-hole of each of the plates 10 and 20, the other side pipe 102 may be inserted first into the first plate 10 (S30). The insertion of the wrinkle pipe assembly may be performed until the guide plate 111 is hooked and supported on an inner surface of the first plate 10. Since the through-hole of the first plate 10 is greater than the wrinkle pipe, the wrinkle pipe assembly may be easily inserted.
In the state in which the guide plate 111 is seated on the first plate 10, preferably, the through-hole of the second plate 20 may match a center of the other side pipe 102. On the other hand, a center of the guide plate 111 and a center of the through-hole of the first plate 10 may not match each other. Nevertheless, the coupling between the portions may be easily performed as already described.
Thereafter, the other side pipe 102 and the second plate 20 may be coupled to each other (S31). Thereafter, the guide plate 111 and the first plate 10 may be coupled to each other (S32).
In the coupling operation of the wrinkle pipe, the coupling process (S32) with the first plate is performed later than the coupling process (S31) with the second plate. The reason is that during the coupling process (S31) with the second plate, displacement may occur in the wrinkle pipe, and in this case, the displacement may be absorbed by allowing the guide plate 111 to move.
On the other hand, when the coupling process (S32) with the first plate is performed first, the other side pipe 102 may not absorb the displacement. Thus, the displacement of the wrinkle pipe remains in the wrinkle pipe, which may lead to deterioration and breakage of the product.
Thereafter, a sealing operation of the drain 72 is completed, and a vacuum may be generated inside the vacuum adiabatic body to terminate the operation (S33).
In this embodiment, it is seen that, even if the dimensions of each portion and the mutual positions between components do not exactly match, an accurate assembly operation is completed. This embodiment is due to the intrinsic limitation of the product in which the performance of the vacuum adiabatic body is not exerted because of leading to the vacuum destruction even by the assembly defects due to small errors.
According to the embodiments, it is possible to improve the product reliability of the drain that leads the defrosting water of the evaporator disposed inside the refrigerator to the outside by providing the pipe passing through the inside and outside of the vacuum adiabatic body.
According to the embodiments, since the objectives of securing semi-permanent reliability of the vacuum adiabatic body, reducing the heat loss, and preventing the failure due to the freezing of the pipeline fluid are achieved, it may be said that its application is urgently expected in the refrigerator industry.
| Number | Date | Country | Kind |
|---|---|---|---|
| 10-2019-0082640 | Jul 2019 | KR | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/KR2020/008969 | 7/8/2020 | WO |
| Publishing Document | Publishing Date | Country | Kind |
|---|---|---|---|
| WO2021/006641 | 1/14/2021 | WO | A |
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