阅读说明：本技术 真空绝热体以及冰箱 (Vacuum insulator and refrigerator ) 是由 金大雄 南贤植 于 2018-07-31 设计创作，主要内容包括：提供了一种真空绝热体。真空绝热体包括保持第三空间的支撑单元。支撑单元包括一个侧支撑板和另一个侧支撑板,该一个侧支撑板通过联接至少两个局部板以支撑第一板构件和第二板构件中的一个而设置,另一个侧支撑板支撑第一板构件和第二板构件中的另一个。(A vacuum thermal insulator is provided. The vacuum heat insulator includes a support unit maintaining the third space. The support unit includes one side support plate provided by coupling at least two partial plates to support one of the first plate member and the second plate member and another side support plate supporting the other of the first plate member and the second plate member.)

1. A vacuum thermal insulator, comprising:

a first plate;

a second plate;

a sealing member sealing the first plate and the second plate to provide a vacuum space;

a support maintaining the vacuum space;

wherein the support member includes:

a first support plate comprising at least two partial plates coupled to each other; and

a second support plate coupled to the first support plate.

2. The vacuum thermal insulator according to claim 1,

wherein the second support plate comprises an overlapping support plate coupled to overlap a boundary of the partial plate; and/or

Wherein the second support plate comprises a single support plate coupled with a single partial plate without the at least two partial plates overlapping.

3. The vacuum thermal insulator of claim 1, wherein the second support plate further comprises:

a maximum standardized size support plate; and

at least one smaller support plate corresponding to a portion of the maximum standardized size support plate.

4. The vacuum thermal insulator of claim 1, wherein a first support plate formed by coupling the at least two partial plates to each other supports one of the first plate and the second plate; and the second support plate supports the other of the first plate and the second plate.

5. The vacuum thermal insulator according to claim 1, wherein when an imaginary line is drawn from a first edge of one of said first support plate and said second support plate in a direction toward a second edge thereof, said imaginary line passes through said at least two partial plates, and at least two of said at least two partial plates have the same shape.

6. The vacuum thermal insulator of claim 5, wherein said at least two partial plates comprise two partial plates disposed along said imaginary line different from each other.

7. The vacuum thermal insulator of claim 1, comprising a radiation-resistant sheet.

8. The vacuum thermal insulator of claim 7, wherein the radiation resistant sheet is placed between a stepped protrusion provided with a bar and a groove provided with the second support plate, the bar being disposed between the first support plate and the second support plate.

9. The vacuum thermal insulator as set forth in claim 1, wherein said support member comprises a resin selected from the group consisting of Polycarbonate (PC), glass fiber PC, low outgassing PC, polyphenylene sulfide (PPS), and Liquid Crystal Polymer (LCP).

Technical Field

The present disclosure relates to a vacuum heat insulator and a refrigerator.

Background

The vacuum heat insulator is a product in which heat transfer is suppressed by vacuum-treating the inside of its body. The vacuum insulator can reduce heat transfer by convection and conduction, and thus is applied to heating and cooling apparatuses. In the conventional heat insulating method applied to a refrigerator, a foamed polyurethane heat insulating wall having a thickness of about 30cm or more is generally provided, although the application is different in cooling and freezing. However, the inner capacity of the refrigerator is thus reduced.

In order to increase the internal capacity of the refrigerator, attempts have been made to apply a vacuum insulator to the refrigerator.

First, korean patent No. 10-0343719 (reference 1) of the present applicant has been disclosed. According to reference 1, a method of preparing and constructing a vacuum insulation panel in a wall of a refrigerator is disclosed, and the outside of the vacuum insulation panel is completed using a separate molded piece of styrofoam. According to the method, additional foaming is not required, and the heat insulation performance of the refrigerator is improved. However, the manufacturing cost is increased and the manufacturing method is complicated. As another example, a technique of providing a wall using a vacuum insulation material and additionally providing an insulation wall using a foam filling material has been disclosed in korean patent laid-open publication No. 10-2015-0012712 (reference 2). According to reference 2, the manufacturing cost increases, and the manufacturing method is complicated.

As another example, attempts have been made to make all the walls of a refrigerator using a single product vacuum insulation. For example, U.S. patent publication No. US 2040226956a1 (reference 3) discloses a technique of setting an insulating structure of a refrigerator in a vacuum state. However, it is difficult to obtain a practical level of heat insulation effect by providing a sufficient vacuum to the walls of the refrigerator. In detail, there are the following limitations: it is difficult to prevent a heat transfer phenomenon from occurring at a contact portion between the outer case and the inner case having different temperatures, to maintain a stable vacuum state, and to prevent deformation of the case due to a negative pressure of the vacuum state. Due to these limitations, the technique disclosed in reference 3 is limited to a low-temperature refrigerator, and does not provide a level of technique suitable for general households.

In view of the above limitations, the applicant has filed patent application No. 10-2015-0109727. In the above document, a refrigerator including a vacuum heat insulator is proposed. In particular, a resin material suitable for a material for forming a supporting unit of a vacuum heat insulator is proposed.

Even in this document, there is a limitation that the shape of the supporting unit is different from the designed shape, and it is difficult to manufacture and handle the supporting unit, and the productivity of the product is low.

Disclosure of Invention

Technical problem

Embodiments provide a vacuum heat insulator in which a shape of a supporting unit is maintained as a design shape, and a refrigerator.

Embodiments also provide a vacuum heat insulator which is easy to manufacture and handle, and a refrigerator.

Embodiments also provide a vacuum heat insulator in which a defect factor occurring when a supporting unit is manufactured is reduced, thereby improving the yield of products, and a refrigerator.

Technical scheme

In order to maintain the shape of the support unit provided in the vacuum heat insulator in a design shape, the support unit may include one side support plate and another side support plate that support the plate members, respectively, and the one side support plate may be provided by coupling at least two plates to each other, thereby allowing the members to be provided with a small size.

In order to easily manufacture and operate the support unit, the partial plate may have a rectangular shape, and a concave coupling structure and a convex coupling structure may be provided on an edge of the partial plate.

In order to improve the yield of the support unit, at least one of one side support plate and the other side support plate may be provided by coupling at least two members having the same shape, which are separated from each other in the extending direction of the respective plate members. In addition, a large-sized plate member may be cut to be used.

The details of one or more embodiments are set forth in the accompanying drawings and the description below. Other features will be apparent from the description and drawings, and from the claims.

The invention has the advantages of

According to the present disclosure, the following advantages may be provided: the design shape of the supporting unit is correctly manufactured and the finish (finish) and reliability of the product are improved. Also, components may be shared to reduce inventory.

According to the present disclosure, small components may be manufactured and transported to be assembled in order to manufacture large-sized components, so that the manufacturing and handling of the support unit is simple and easy.

According to the present disclosure, even if a resin poor in moldability, i.e., melt fluidity is used, the productivity of the support unit can be improved by applying a plurality of parts. Further, even in the case of poor molding, only the parts need to be discarded, so that the productivity of the supporting unit can be further improved.

Drawings

Fig. 1 is a perspective view of a refrigerator according to an embodiment.

Fig. 2 is a view schematically showing a vacuum insulator used in a main body and a door of a refrigerator.

Fig. 3 is a view showing various embodiments of an internal configuration of a vacuum space part.

Fig. 4 is a graph showing the results obtained by testing the resin.

Fig. 5 shows the results obtained by performing an experiment on the vacuum retention property of the resin.

Fig. 6 shows the results obtained by analyzing the components of the gas discharged from PPS and low outgassing PC.

Fig. 7 shows the results obtained by measuring the maximum deformation temperature at which the resin is damaged by atmospheric pressure in high-temperature discharge.

Fig. 8 is a view showing various embodiments of the conductive resistance sheet and a peripheral portion thereof.

Fig. 9 is a view illustrating any one side portion of the support unit according to the embodiment.

Fig. 10 is a plan view of a partial plate.

Fig. 11 is an enlarged view of a portion a of fig. 10, and fig. 12 is an enlarged view of a portion B of fig. 10.

Fig. 13 is an enlarged view of a portion C of fig. 10.

Fig. 14 is a view for explaining coupling between one side support plate and the other side support plate.

Fig. 15 is an enlarged view of a portion D of fig. 14.

Fig. 16 is a sectional view taken along line a-a' of fig. 15.

Fig. 17 is a view of a support unit according to another embodiment.

Fig. 18 shows a graph showing a change in gas conductivity and a change in adiabatic performance with respect to vacuum pressure by applying a simulation.

Fig. 19 is a graph illustrating a result obtained by observing the time and pressure during which the inside of the vacuum insulator is discharged when the supporting unit is used.

Fig. 20 is a graph obtained by comparing vacuum pressure with gas conductance.

Detailed Description

Hereinafter, exemplary embodiments will be described with reference to the accompanying drawings. However, the present invention may be embodied in many different forms and should not be construed as limited to the embodiments set forth herein, and those skilled in the art who have the spirit of the present invention understand that other embodiments may be easily implemented, which are included within the scope of the same concept by adding, changing, deleting, and adding components; rather, it should be understood that they are also included within the scope of the present invention.

The drawings shown below may be shown differently from an actual product or exaggerated or simple or detailed parts may be deleted, but it is intended to facilitate understanding of the technical idea of the present invention. Which should not be construed as limiting.

In the following description, vacuum pressure means any specific pressure state below atmospheric pressure. In addition, the expression that the degree of vacuum of a is higher than that of B means that the vacuum pressure of a is lower than that of B.

Fig. 1 is a perspective view of a refrigerator for a vehicle according to an embodiment.

Referring to fig. 1, a refrigerator 1 includes: a main body 2 provided with a chamber 9 capable of storing stored articles; and a door 3 provided to open/close the main body 2. The door 3 may be rotatably or slidably movably provided to open/close the chamber 9. The chamber 9 may provide at least one of a refrigerating chamber and a freezing chamber.

The plurality of components constitute a freezing cycle in which cool air is supplied into the chamber 9. For example, these 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 obtain heat. As a typical structure, a fan may be installed at a position adjacent to the evaporator 7, and fluid blown from the fan may pass through the evaporator 7 and then be blown into the chamber 9. The freezing load is controlled by adjusting the blowing amount and the blowing direction by a fan, by adjusting the amount of refrigerant circulated, or by adjusting the compression ratio of a compressor, so that the refrigerating space or the freezing space can be controlled.

Other parts constituting the refrigeration cycle may be constituted by applying a member including a thermoelectric module.

Fig. 2 is a view schematically showing a vacuum insulator used in a main body and a door of a refrigerator. In fig. 2, the body-side vacuum heat insulator is shown in a state where the top wall and the side wall are removed, and the door-side vacuum heat insulator is shown in a state where a part of the front wall is removed. Further, for ease of understanding, sections of the portions at the conductive resistant sheet are provided.

Referring to fig. 2, the vacuum thermal insulator includes: a first plate member 10 for providing a wall of a low temperature space; a second plate member 20 for providing a wall of the high temperature space; a vacuum space part 50 defined as a spacing part between the first plate member 10 and the second plate member 20. Also, the vacuum heat insulator includes the conduction resistance sheets 60 and 63 for preventing heat conduction between the first plate member 10 and the second plate member 20. A sealing means 61 for sealing the first plate member 10 and the second plate member 20 is provided so that the vacuum space part 50 is in a sealed state.

When the vacuum insulation is applied to a refrigerator or a heating apparatus, the first plate member 10 providing a wall of an inner space of the refrigerator may be referred to as an inner case, and the second plate member 20 providing a wall of an outer space of the refrigerator may be referred to as an outer case.

A machine room (machine room)8 accommodating components providing a freezing cycle is placed at the lower rear side of the main body side vacuum heat insulator, and a discharge port 40 for discharging air in the vacuum space part 50 to form a vacuum state is provided at either side of the vacuum heat insulator. In addition, a pipe 64 passing through the vacuum space part 50 may be installed to install a defrosting water pipe and an electric wire.

The first plate member 10 may define at least a portion of a wall on which the first space is disposed. The second plate member 20 may define at least a portion of a wall for disposing the second space thereon. The first space and the second space may be defined as spaces having different temperatures. Here, the wall of each space may be a wall that not only directly contacts the space but also does not contact the space. For example, the vacuum heat insulator of the present embodiment may also be applied to a product also having a separate wall contacting each space.

Factors that contribute to the heat transfer that results in the loss of the insulating effect of the vacuum insulation are: heat conduction between the first plate member 10 and the second plate member 20, radiant heat between the first plate member 10 and the second plate member 20, and gas conduction of the vacuum space part 50.

In the following, a heat resistant unit is provided, which is arranged to reduce the insulation losses associated with these factors of heat transfer. Meanwhile, the vacuum heat insulator and the refrigerator of the present embodiment do not exclude another heat insulating means from being provided to at least one side of the vacuum heat insulator. Therefore, a heat insulating means using foaming or the like may be further provided to the other side of the vacuum heat insulator.

Fig. 3 is a view showing various embodiments of an internal configuration of a vacuum space part.

First, referring to fig. 3a, a vacuum space part 50 may be provided in a third space having a pressure different from each of the first and second spaces, preferably in a vacuum state, thereby reducing adiabatic loss. The temperature of the third space may be set to be between the temperature of the first space and the temperature of the second space. Since the third space is set as a space in a vacuum state. Thereby, the first plate member 10 and the second plate member 20 receive a force contracting in a direction to bring them close to each other due to a force corresponding to a pressure difference between the first space and the second space. Therefore, the vacuum space part 50 can be deformed in the direction in which it decreases. In this case, the adiabatic loss may occur due to the following reasons: an increase in the amount of heat radiation, a contraction of the vacuum space part 50 and an increase in the amount of heat conduction, and contact between the plate members 10 and 20.

The support unit 30 may be provided to reduce deformation of the vacuum space part 50. The support unit 30 includes a rod 31. The rod 31 may extend in a substantially perpendicular direction with respect to the plate member to support the distance between the first plate member and the second plate member. A support plate 35 may be additionally provided on at least either end of the rod 31. The support plate 35 may connect at least two or more rods 31 to each other to extend in a horizontal direction with respect to the first and second plate members 10 and 20. The support plate 35 may be provided in a plate shape, or may be provided in a lattice shape, so as to reduce an area of the support plate contacting the first plate member 10 or the second plate member 20, thereby reducing heat transfer. The rod 31 and the support plate 35 are fixed to each other at least one portion so as to be inserted together between the first plate member 10 and the second plate member 20. The support plate 35 contacts at least one of the first plate member 10 and the second plate member 20, thereby preventing deformation of the first plate member 10 and the second plate member 20. Further, the total sectional area of the support plate 35 is set larger than that of the rod 31 based on the extending direction of the rod 31, so that the heat transferred through the rod 31 can be diffused through the support plate 35.

The material of the supporting unit 30 will be described.

The supporting unit 30 has high compressive strength to withstand vacuum pressure. In addition, the support unit 30 will have a low outgassing rate and a low water absorption rate to maintain a vacuum state. Also, the support unit 30 will have a low thermal conductivity in order to reduce the thermal conduction between the plate members. Also, the supporting unit 30 will ensure compressive strength at high temperature to withstand the high temperature discharge process. In addition, the supporting unit 30 should have excellent machinability to be molded. Also, the support unit 30 will have a low cost molding. Here, the time required to perform the discharging process takes about several days. Accordingly, time is reduced, thereby greatly improving manufacturing costs and productivity. Therefore, since the discharge rate increases as the temperature at which the discharge process is performed increases, the compressive strength is ensured at high temperature. The inventors carried out various tests under the above conditions.

First, ceramics or glasses have low outgassing rate and low water absorption, but their machinability is significantly reduced. Therefore, ceramics and glass may not be used as the material of the supporting unit 30. Therefore, the resin may be considered as a material of the support unit 30.

Fig. 4 is a graph showing the results obtained by testing the resin.

Referring to fig. 4, the present inventors have examined various resins, and most of the resins cannot be used because their outgassing rate and water absorption rate are very high. Thus, the present inventors have examined resins that approximately satisfy the conditions of outgassing rate and water absorption rate. As a result, PE is not suitable for use due to its high outgassing rate and low compressive strength. Since PCTFE is too expensive, it is not desirable to use PCTFE. PEEK is not suitable for use because of its high outgassing rate. Therefore, it was determined that a resin selected from the group consisting of Polycarbonate (PC), glass fiber PC, low outgassing PC, polyphenylene sulfide (PPS), and Liquid Crystal Polymer (LCP) can be used as a material of the supporting unit. However, the outgassing rate of PC was 0.19, which is at a low level. Therefore, as the time required for performing baking (in which discharging is performed by applying heat) increases to a certain level, PC may be used as a material of the supporting unit.

The present inventors have found the optimum material through various studies on the resin expected to be used inside the vacuum space part. Hereinafter, the results of the study conducted will be described with reference to the drawings.

Fig. 5 is a view showing a result obtained by an experiment on vacuum retention performance of a resin.

Referring to fig. 5, a graph showing results obtained by manufacturing a support unit using a corresponding resin and then testing the vacuum retention performance of the resin is shown. First, a supporting unit made of a selected material was cleaned using alcohol, left under low pressure for 48 hours, exposed to air for 2.5 hours, and then subjected to a discharging process at 90 ℃ for about 50 hours in the following state: the supporting unit was put into a vacuum insulator, thereby measuring the vacuum holding performance of the supporting unit.

It can be seen that in the case of LCP, the initial discharge performance is the best, but the vacuum retention performance is poor. This is expected to be due to the sensitivity of LCP to temperature. Furthermore, it can be expected from the characteristics of the graph that when the final allowable pressure is 5 × 10^-3The vacuum performance will be maintained for about 0.5 years at Torr (Torr). Therefore, LCP is not suitable as a material of the supporting unit.

It can be seen that in the case of glass fiber PC (G/F PC), the discharge rate is fast, but the vacuum retention performance is low. It was determined that this would be affected by the additives. Additionally, by the characteristics of this graph, it is expected that the glass fiber PC will retain its vacuum performance for a period of about 8.2 years under the same conditions. Therefore, LCP is not suitable as a material of the supporting unit.

In comparison to the two materials described above, it is expected that in the case of low outgassing PC (O/G PC), its vacuum retention performance is very good, and its vacuum performance will be maintained under the same conditions for about 34 years. However, it can be seen that the initial emission performance of the low outgassing PC is low, and therefore, the production efficiency of the low outgassing PC is lowered.

It can be seen that in the case of PPS, the vacuum retention property thereof is excellent, and the discharge property thereof is also excellent. Therefore, based on the vacuum holding property, PPS is most preferably considered as a material of the support unit.

FIG. 6 shows a graph showing analysis of the composition of gases emitted from PPS and low outgassing PCThe results obtained, wherein the horizontal axis represents the mass number of the gas and the vertical axis represents the concentration of the gas. Fig. 6a shows the results obtained by analyzing the gas emitted from the low outgassing PC. In FIG. 6a, H can be seen₂Series (I) and H₂O series (II), N₂/CO/CO₂/O₂The series (III) and the hydrocarbon series (IV) were likewise discharged (equiallely). Fig. 6b shows the results obtained by analyzing the gas vented from the PPS. In FIG. 6b, H can be seen₂Series (I) and H₂O series (II), N₂/CO/CO₂/O₂The emission levels of series (III) are relatively weak. Fig. 6c is the result obtained by analyzing the gas emitted from the stainless steel. In fig. 6c, it can be seen that a gas similar to PPS is emitted from the stainless steel. Therefore, it can be seen that the gas discharged from PPS is similar to stainless steel.

Due to the analysis results, it can be confirmed again that PPS is excellent as a material of the supporting unit.

Fig. 7 shows the results obtained by measuring the maximum deformation temperature at which the resin is damaged by atmospheric pressure in high-temperature discharge. At this time, a rod 31 having a diameter of 2mm was provided at a distance of 30 mm. Referring to fig. 7, it can be seen that in the case of PE, cracking occurs at 60 ℃; in the case of low outgassing PC, cracking occurs at 90 ℃; in the case of PPS, the fracture occurs at 125 ℃.

As a result of the analysis, it can be seen that PPS is most preferably used as a resin used inside the vacuum space part. However, in terms of manufacturing cost, a low outgassing PC may be used.

The radiation shield sheet 32 that reduces heat radiation between the first plate member 10 and the second plate member 20 by the vacuum space part 50 will be described. The first plate member 10 and the second plate member 20 may be made of a stainless steel material capable of preventing corrosion and providing sufficient strength. The stainless material has a relatively high emissivity of 0.16, and thus, a large amount of radiant heat can be transferred. Further, the support unit 30 made of resin has a lower emissivity than the plate members, and is not integrally provided to the inner surfaces of the first plate member 10 and the second plate member 20. Therefore, the support unit 30 does not have much influence on the radiant heat. Thus, the radiation shield 32 may be provided in a plate shape over a large area of the vacuum space part 50 so as to intensively reduce the radiant heat transmitted between the first plate member 10 and the second plate member 20. A product having a low emissivity may be preferably used as the material of the radiation-resistant sheet 32. In one embodiment, an aluminum foil having an emissivity of 0.02 may be used as the radiation-resistant sheet 32. Also, since the use of one radiation-resistant sheet may not be sufficient to block the transmission of the thermal radiation, at least two radiation-resistant sheets 32 may be disposed at a distance so as not to contact each other. In addition, at least one radiation resistant sheet may be provided in a state of being in contact with the inner surface of the first plate member 10 or the second plate member 20.

Referring back to fig. 3b, the distance between the plate members is maintained by the support unit 30, and the porous material 33 may be filled into the vacuum space part 50. The porous material 33 may have a higher emissivity than the stainless steel material of the first and second plate members 10, 20. However, since the porous material 33 is filled in the vacuum space part 50, the porous material 33 has high efficiency for blocking radiation heat transfer.

In the present embodiment, the vacuum thermal insulator can be manufactured without the radiation shield sheet 32.

Fig. 8 is a view illustrating various embodiments of a conductive resistance sheet and a peripheral portion of the conductive resistance sheet. The structure of the conductive resistance sheet is simply illustrated in fig. 2, but will be understood in detail with reference to the drawings.

First, the conductive resistance sheet proposed in fig. 8a may be preferably applied to the body-side vacuum insulator. Specifically, the first plate member 10 and the second plate member 20 are sealed so that the inside of the vacuum insulator forms a vacuum. In this case, since the two plate members have different temperatures from each other, heat transfer may occur between the two plate members. The conductive resistance sheet 60 is provided to prevent heat conduction between two different plate members.

The conductive resistance sheet 60 may be provided with a sealing part 61 where both ends of the conductive resistance sheet 60 are sealed to define at least one portion of a wall for the third space and maintain a vacuum state. The conductive resistance sheet 60 may be provided as a thin foil in a micrometer unit in order to reduce the amount of heat conducted along the wall of the third space. The plurality of sealing members 610 may be provided as a plurality of welding members. That is, the conductive resistance sheet 60 and the plate members 10 and 20 may be welded to each other. In order to produce a welding effect between the conductive resistance sheet 60 and the plate members 10 and 20, the conductive resistance sheet 60 and the plate members 10 and 20 may be made of the same material, and a stainless material may be used as this material. The sealing member 610 is not limited to a welding member, but may be provided by a process such as tapping. The conductive resistance sheet 60 may be provided in a curved shape. Thereby, the heat conducting distance of the conductive resistance sheet 60 is set longer than the linear distance of each plate member, so that the amount of heat conduction can be further reduced.

A temperature change is generated along the conductive resistance sheet 60. Therefore, in order to block heat conduction to the outside of the conductive resistance sheet 60, a shielding member 62 may be provided at the outside of the conductive resistance sheet 60 so as to generate a heat insulating effect. In other words, in the refrigerator, the second plate member 20 has a high temperature, and the first plate member 10 has a low temperature. In addition, heat conduction from a high temperature to a low temperature occurs in the conductive resistance sheet 60, so the temperature of the conductive resistance sheet 60 may change abruptly. Therefore, when the conductive resistance sheet 60 is opened toward the outside thereof, heat transfer through the opened position may seriously occur. To reduce heat loss, a shielding member 62 is provided outside the conductive resistance sheet 60. For example, when the conductive resistance sheet 60 is exposed to any one of a low temperature space and a high temperature space, the conductive resistance sheet 60 and the exposed portion thereof do not function as a conductive resistance body, but it is not preferable.

The shielding member 62 may be provided as a porous material contacting the outer surface of the conductive resistance sheet 60. The shielding member 62 may be provided as a heat insulating structure, such as a separate gasket disposed outside the conductive resistance sheet 60. The shielding member 62 may be provided as a portion of the vacuum heat insulator, which is disposed at a position facing the corresponding conduction resistance sheet 60 when the body-side vacuum heat insulator is closed with respect to the door-side vacuum heat insulator. In order to reduce heat loss when the main body and the door are opened, the shielding member 62 may preferably be provided as a porous material or a separate vacuum structure.

The conductive resistance sheet proposed in fig. 8b may be preferably applied to a door-side vacuum insulator. In fig. 8b, portions different from those in fig. 8a are described in detail, and the same description is used for the same portions as those in fig. 8 a. The side frame 70 is also disposed at the outer side of the conductive resistance sheet 60. Components for sealing between the door and the main body, a discharge port required for a discharge process, a degassing port for maintaining vacuum, etc. are disposed on the side frame 70. This is because the installation of the components in the main body-side vacuum heat insulator is convenient, but the installation positions of the components are limited to the door-side vacuum heat insulator.

In the door-side vacuum heat insulator, it is difficult to arrange the conduction preventing piece 60 at the front end portion of the vacuum space portion, i.e., the corner side portion of the vacuum space portion. This is because, unlike the main body, the corner edge portion of the door is exposed to the outside. More particularly, if the conductive resistance sheet 60 is positioned at the front end portion of the vacuum space part, the corner edge portion of the door is exposed to the outside, and thus there is a disadvantage in that a separate heat insulation member should be provided to thermally insulate the conductive resistance sheet 60.

The conductive resistance sheet proposed in fig. 8c may be preferably installed in a duct passing through the vacuum space part. In fig. 8c, a portion different from fig. 8a and 8b is described in detail, and the same description is used for the same portion as fig. 8a and 8 b. A conductive resistance sheet, preferably corrugated, 63 having the same shape as fig. 8a may be provided at a peripheral portion of the pipe 64. Therefore, the heat transfer path can be extended, and deformation caused by the pressure difference can be prevented. In addition, a separate shielding member may be provided to improve the heat insulating property of the conductive resistance sheet.

Referring back to fig. 8a, a heat transfer path between the first plate member 10 and the second plate member 20 will be described. The heat passing through the vacuum insulation can be divided into: a surface heat conduction (r) conducted along the surface of the vacuum heat insulator, more particularly, the conduction resistance sheet 60, a supporter heat conduction (r) conducted along the supporting unit 30 provided in the vacuum heat insulator, a gas heat conduction (r) conducted through the internal air in the vacuum space part, and a radiation heat conduction (r) conducted through the vacuum space part.

The heat transfer may vary according to various design dimensions. For example, the supporting unit may be changed such that the first plate member 10 and the second plate member 20 may withstand vacuum pressure without being deformed, the vacuum pressure may be changed, the distance between the plate members may be changed, and the length of the conductive resistance sheet may be changed. The heat transfer may be changed according to a temperature difference between the spaces (the first space and the second space) respectively provided through the plate members. In this embodiment, a preferable configuration of the vacuum heat insulator has been found by considering that the total heat transfer amount thereof is smaller than that of a typical heat insulating structure formed by foaming polyurethane. In a typical refrigerator including a heat insulating structure formed by foaming polyurethane, an effective heat transfer coefficient may be suggested to be 19.6 mW/mK.

By performing a correlation analysis on the heat transfer amount of the vacuum heat insulator of this embodiment, the heat transfer amount of the gas heat transfer (c) can be minimized. For example, the heat transfer amount of the gas heat transfer (c) may be controlled to be equal to or less than 4% of the total heat transfer amount. The amount of heat transfer is maximum, defined as the solid heat transfer of the sum of the surface heat transfer (r) and the support heat transfer (r). For example, the heat transfer capacity of solid heat transfer can be up to 75% of the total heat transfer capacity. The heat transfer amount of the radiation heat transfer (c) is smaller than that of solid heat transfer but larger than that of gas heat transfer. For example, the amount of heat transferred by radiation may account for about 20% of the total heat transferred.

According to this heat transfer distribution, the effective heat transfer coefficients (eK: effective K) (W/mK) of the surface heat conduction (r), the support heat conduction (r), the gas heat conduction (r), and the radiation heat conduction (r) can have the order of mathematical equation 1.

[ EQUATION 1 ]

eK_{Solid heat conduction}>eK_{Radiation heat transfer}>eK_{Gas heat transfer}

Here, the effective heat transfer coefficient (eK) is a value that can be measured using the shape and temperature difference of the target product. The effective heat transfer coefficient (eK) is a value that can be obtained by measuring the temperature at least a part of the heat transfer and the total heat transfer amount. For example, a heat value (W) is measured using a heat source, which can be quantitatively measured in a refrigerator, a temperature distribution (K) of a door is measured using heat transmitted through edges of a main body and a refrigerator door, respectively, and a path through which heat is transferred is calculated as a conversion value (m), thereby estimating an effective heat transfer coefficient.

The effective heat transfer coefficient (eK) of the entire vacuum thermal insulator is a value given by k-QL/a Δ T. Here, Q represents a heat value (W), and may be obtained using a heat value of the heater. A represents the cross-sectional area (m) of the vacuum thermal insulator²) L represents the thickness (m) of the vacuum thermal insulator, and Δ T represents the temperature difference.

For the surface heat conduction, the heat transfer conduction value may be obtained by a temperature difference (Δ T) between an inlet and an outlet 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 the material and may be obtained in advance). For the support heat conduction, the heat conduction calorific value may be obtained by a temperature difference (Δ T) between the inlet and the outlet of the support unit 30, a sectional area (a) of the support unit, a length (L) of the support unit, and a heat conductivity (k) of the support unit. Here, the thermal conductivity of the support unit is a material property of the material and may be obtained in advance. The sum of the gas heat conduction (c) and the radiation heat conduction (c) can be obtained by subtracting the surface heat conduction and the support heat conduction from the heat transfer amount of the entire vacuum insulator. The ratio of the gas heat conduction (c) and the radiation heat transfer (c) can be obtained by estimating the radiation heat transfer when there is no gas heat conduction by significantly reducing the degree of vacuum of the vacuum space part 50.

When the porous material is provided in the vacuum space part 50, the porous material heat conduction (c) may be the sum of the supporter heat conduction (c) and the radiation heat conduction (c). The porous material thermal conductivity may vary depending on various variables including the kind, amount, etc. of the porous material.

According to an embodiment, the temperature difference Δ T between the geometric center formed by adjacent rods 31 and the point where each rod 31 is located₁It may be preferably set to less than 0.5 deg.c. Also, the temperature difference DeltaT between the geometric center formed by the adjacent rods 31 and the edge portion of the vacuum heat insulator₂May preferably be set to less than 0.5 deg.c. In the second plate member 20, the second plate is flatThe temperature difference between the average temperature and the temperature at the point where the heat transfer path through the conductive resistance sheet 60 or 63 intersects the second plate may be the largest. For example, when the second space is a hotter area than the first space, the temperature at the point where the heat conduction path through the conductive resistance sheet intersects the second plate member becomes the lowest. Similarly, when the second space is a cooler area than the first space, the temperature at the point where the heat conduction path through the conductive resistance sheet intersects the second plate member becomes highest.

This means that heat transfer through other points should be controlled in addition to surface heat conduction through the conductive resistance sheet, and that the entire heat transfer amount of the vacuum insulator can be satisfied only when the surface heat conduction occupies the maximum heat transfer amount. For this reason, the temperature change of the conductive resistance sheet may be controlled to be greater than the temperature change of the plate member.

Physical characteristics of the components constituting the vacuum thermal insulator will be described. In the vacuum heat insulator, a force generated by vacuum pressure is applied to all components. Therefore, it may be preferable to use a light source having a certain level of intensity (N/m)²) The material of (1).

In this case, the plate members 10 and 20 and the side frames 70 may preferably be made of a material having sufficient strength with which even vacuum pressure does not damage them. For example, when the number of the rods 31 is reduced to limit the supporting heat conduction, deformation of the plate member occurs due to the vacuum pressure (the deformation may adversely affect the external appearance of the refrigerator). The radiation-resistant sheet 32 may preferably be made of a material having a low emissivity, and may be easily subjected to a thin film process. Also, the radiation shield 32 serves to secure sufficient strength against deformation due to external impact. The supporting unit 30 is provided with sufficient strength to support the force generated by the vacuum pressure and to endure external impact, and has workability. The conductive resistance sheet 60 may preferably be made of a material having a thin plate shape and may endure vacuum pressure.

In an embodiment, the plate member, the side frames, and the conductive resistance sheet may be made of stainless steel materials having the same strength. The radiation-resistant sheet may be made of aluminum having a strength weaker than that of the stainless steel material. The support unit may be made of resin having a strength weaker than that of aluminum.

Unlike the material strength, the analysis needs to be performed from a stiffness point of view. The rigidity (N/m) is a property of being hardly deformed. Although the same material is used, its rigidity may be changed according to its shape. The conductive resistance sheet 60 or 63 may be made of a material having strength, but the rigidity of the material is preferably low in order to increase heat resistance and minimize radiant heat because the conductive resistance sheet is uniformly spread without any roughness when vacuum pressure is applied. The radiation-resistant sheet 32 requires a certain level of rigidity so as not to contact another member due to deformation. In particular, the edge portion of the radiation-resistant sheet may generate heat conduction due to sagging of the radiation-resistant sheet caused by self-load. Therefore, a certain level of rigidity is required. The support unit 30 needs to have sufficient rigidity to withstand the compressive stress and external impact from the plate member.

In an embodiment, the plate member and the side frames may preferably have the highest rigidity in order to prevent deformation caused by vacuum pressure. The support unit, in particular the rod, may preferably have a second highest stiffness. The rigidity of the radiation resistant sheet may preferably be lower than that of the support unit but higher than that of the conductive resistant sheet. Finally, the conductive resistance sheet may preferably be made of a material that is easily deformed by vacuum pressure, and has the lowest rigidity.

The conductive resistance sheet may preferably have the lowest rigidity even when the porous material 33 is filled in the vacuum space part 50, and the plate member and the side frame may preferably have the highest rigidity.

The vacuum space part may resist heat transfer only by the support unit 30. Here, the porous material 33 may be filled in the inside of the vacuum space part 50 together with the support unit to resist heat transfer. It is possible to prevent heat transfer to the porous material without applying the supporting unit.

In the above description, as a material suitable for the support unit, a resin of PPS has been proposed. The rods 31 are disposed on the support plate 35 at intervals of 2cm to 3cm, and the rods 31 have a height of 1cm to 2 cm. These resins generally have poor resin flow during molding. In many cases, the molded article has no design value. In particular, since the resin is unevenly injected into a portion away from the liquid injection port of the liquid, the shape of a molded product such as a rod having a short length cannot be usually provided appropriately.

Which may then damage the support unit or cause defective vacuum insulators.

The support unit 30 is a substantially two-dimensional structure, but its area is rather large. Therefore, if a defect occurs in one of the portions, it is difficult to discard the entire structure. This limitation is becoming more apparent as the size of refrigerators and heating devices is becoming larger to meet consumer demand.

Hereinafter, a supporting unit for solving the above-described limitations will be described.

Fig. 9 is a view illustrating any one side of the supporting unit according to the embodiment.

Referring to fig. 9, one side support plate 350 is provided with at least two partial plates coupled to each other. In other words, the partial plates having a small rectangular shape are coupled to each other to provide one side support plate 35 having a large rectangular shape. For example, in the drawing, the second partial plate 352 and the fourth partial plate 354 are coupled to the lower side and the right side of the first partial plate 351. The second and fourth partial plates 352 and 354 are coupled to left and upper sides of the third partial plate 353.

In one embodiment, the partial plates may have the same shape. Thus, the one side support plate 350 may be up to four times the size of the partial plate. When the number of the partial plates 351, 352, 353, and 354 having the same shape and structure coupled to each other is changed, the size of the one side support plate 350 may be changed. It is easy to guess that the size of the one side support plate 350 is differently set according to the size of the vacuum insulator.

According to this configuration, when the partial plates are liquid such as PPS, the partial plates can be manufactured by using resin having poor fluidity, and the partial plates can be coupled. Since the partial plates are small in size, defects during molding can be prevented, and even if molding failure occurs, only the corresponding partial plates are discarded, so that it is not necessary to discard the entire support plate.

After the production of the small partial plate, the partial plate is assembled at an assembling position of the vacuum insulator and then placed in the vacuum insulator. Therefore, the device has the advantages of convenient operation and transportation. In addition, a restriction that damage may occur during the operation of a large part can be prevented.

A plurality of small partial plates can be manufactured, and various types of support units having a desired area can be obtained.

Fig. 10 is a plan view of a partial plate.

Referring to fig. 10, the partial plate 351 has one side base 355 of a lattice structure, and pillars 356 are provided at intersections of the lattice on the one side base 355. The one side base 355 may maintain a vacuum space inside the plate members 10 and 20 by contacting the inner surfaces of the plate members 10 and 20. The posts 356 may provide a portion of the rod 31 to maintain the spacing between the plate members 10 and 20.

The lattice ends of the lattice structure constituting one base 351 may have male and female coupling structures for coupling different partial plates 351 to each other. For example, the upper and left edges may have male coupling features, while the right and lower edges may have female coupling features. The extension of the arrows in the figure indicates the edges with the same coupling structure.

Fig. 11 is an enlarged view of a portion a of fig. 10, and fig. 12 is an enlarged view of a portion B of fig. 10.

Referring to fig. 11 and 12, the male coupling structure (see fig. 11) has an insert 357 at the end of the branches of the lattice providing one base 355. The insertion portion 357 may be provided in a structure in which the end of the branch is elongated. The male coupling structure (see fig. 12) may be provided with a retaining portion 358, the retaining portion 358 being retained at an end of one base portion 355. The holding portion 358 may be provided with a recess 359 at the end of the branch. The recess 359 may be shaped to correspond to the shape of the insert 357. The insert 357 may be inserted into the recess 359.

The male coupling structure of an adjacent partial plate is vertically aligned with the female coupling structure of another partial plate, and the insert 357 and the recess 359 serve as references for vertical alignment. Thereafter, when the insert 357 is moved to the recess 359 in the vertical direction, the coupling between the partial plates may be completed. Here, the vertical direction may be a direction perpendicular to the plane of the corresponding plate member.

For example, the right and lower side male coupling structures of the first partial plate 351 are coupled with the male coupling structures of the fourth partial plate 354 and the male coupling structures of the second partial plate 352. The coupling structure may be the same for the other partial plates.

The partial plate male coupling structures and the male coupling structures are used to use as little resin as possible and are intended to achieve a connection while reducing the size as much as possible. Thus, the movement in one direction, i.e., up and down direction, is allowed to be coupled. However, movement in two dimensions, i.e., in the area direction, is not allowed, so that coupling is performed.

The male coupling structure and the male coupling structure need not be fully adapted to each other, e.g. they are coupled to each other. This is because not only movement in two dimensions is allowed, but also vertical movement of the individual partial plates, which is then fixed by a separate component. In addition, this is due to the characteristic of poor liquid fluidity of the resin, and therefore it is necessary to easily couple a slight loose coupling by the movement of the coupling in the up-down direction. That is, this is because the value of the coupling structure for press-fitting may cause damage to the partial plates at the time of coupling.

This structure reduces the amount of resin as much as possible to reduce the amount of outgas, so that no limitation is caused on vacuum retention of the vacuum space portion, and even when a resin poor in moldability is used, molding of the male coupling structure and the female coupling structure is prevented from becoming difficult.

Fig. 13 is an enlarged view of a portion C of fig. 10.

Referring to fig. 13, in the case of this embodiment, all the partial plates are in contact with each other, and the partial plates have the same shape. The insertion portion 357 is fixed to the holding portion 358 in the vertical direction. The holding portions 358 and 357 provided on the respective partial plates 351, 352, 353, and 354 are coupled to each other so that the movement of the partial plates in two dimensions, i.e., one support plate 350 can provide a large area. The area of one side support plate 350 can be achieved by attaching the necessary number of partial plates. When the size and number of the partial plates are changed, the size of one side support plate 350 having various shapes and sizes can be obtained.

The pillars 356 disposed at the intersections of the respective lattices constituting one base 355 may include two types. For example, the posts 356 may include a spacer post 3561 for maintaining a space between the plate members 10 and 20 and a support post 3562, the support post 3562 supporting the radiation-resistant sheet 32.

The spacing post 3561 is coupled to a groove (see reference numeral 373 in fig. 16) of another support plate (see reference numeral 370 in fig. 14) to maintain the spacing between the plate members 10 and 20. To facilitate coupling with groove 373 and to ensure moldability using liquid resin, spacer post 3561 has a diameter H1 at its lower end, which diameter H1 is greater than diameter H2 at its upper end. Although the cross-sectional shape of the spacer 3561 may not be circular, the cross-sectional dimension of the upper end may be small. However, the cross-sectional shape of the spacer 3561 may be provided in a circular shape to ensure the formation shape of the spacer 3561 and the coupling between the spacer 3561 and the groove 373.

As in the case of the spacer posts 3561, in order to ensure coupling and moldability, the support posts 3562 preferably have a smaller cross-sectional dimension of the support posts 3562 toward the upper end. In addition, in order to support the radiation-resistant sheet 32, the support column 3562 may be provided with a stepped protrusion 3563. A plurality of support columns 3562 may be disposed at predetermined intervals to stably support the radiation shield 32. The function of the support post 3562 will be described in more detail below.

As described above, the movement of one side support plate 350 in the vertical direction is restricted while the one side support plate 350 is freely moved in the vertical direction. Thus, a configuration for limiting the vertical movement of each partial plate may be provided. The support unit 30 may be in contact with the inner surface of the plate member to support the interval of the plate members 10 and 20. When the support unit is in contact with the plate member, point contact may provide a stable supporting force compared to line contact. Thus, a configuration may be provided such that the posts 356 do not directly contact the inner surface of the plate member.

To achieve this, another side support plate 370 corresponding to one side support plate 350 may be further provided. Hereinafter, one side support plate 350 and the other side support plate 370 will be described.

Fig. 14 is a view for explaining coupling between one side support plate and the other side support plate.

Referring to fig. 14, at least two partial plates are coupled to each other to provide one side support plate 350. One side support plate 350 is restricted to be separated in the area direction, but upward and downward movement is not restricted. In order to restrict the vertical separation of the one side support plate 350 and securely secure the interval of the plate members 10 and 20 while more securely coupling the one side support plate 350 in the area-separated direction, a support plate 370 is provided. Another side support plate 370 may be coupled to the one side support plate 350.

The other side support plate 370 may be understood as a member for supporting a plate member opposite to the plate member supported by the one side support plate 350. The other side support plate 370 may be used together with another standardized side plate member having a predetermined size, or the standardized side plate member may be separated at a predetermined position by cutting or the like. Thus, it will be appreciated that the other plate member has the same construction but with a different area applied.

Of course, another side plate member may be provided as a unit having an area corresponding to one side support plate 350, but in order to maximize the effect of the components, the same configuration as the embodiment may be more preferably assumed.

In one embodiment, another side plate member of an original size, which is not cut, is formed at a central portion of one side support plate 350, at which the partial plates 351, 352, 353, and 354 and the other side plate 371 are coupled to overlap with each other. In this case, another plate member is coupled to overlap the boundary of the different partial plates, thereby enhancing the coupling force between the respective partial plates and functioning to restrict the movement in the area direction. In this case, needless to say, a function of restricting the movement of the partial plate in the vertical direction and a function of maintaining the interval of the plate members 10 and 20 may be performed.

In other words, the boundaries of each partial plate constituting one support plate and another plate member constituting another support plate (which may include both the overlapped another plate and the single another plate) cross each other and ideally do not overlap each other. If the borders overlap each other, it is possible that the components of the respective support plates, i.e. the partial plate and the further plate component, are separated from each other or together.

The other plate member may be provided in the same shape as the overlapping plate 371 coupled to the central portion of one side support plate 350.

The further plate member may be coupled to a single partial plate without at least two partial plates overlapping. In this case, a portion of the other side plate member may be referred to as a single other side plate 372. In this case, needless to say, a function of restricting the movement of the partial plate in the vertical direction and a function of maintaining the interval of the plate members 10 and 20 may be performed. However, it is impossible to perform an action of restricting the movement of each partial plate in the area direction and enhancing the bonding force between the partial plates.

In the case of one embodiment, four other plate members 370 having the same area as the partial plates 351, 352, 353, and 354 may be used.

One of the four support plates 350 is coupled with the center of the other support plate 350, which is the overlapped second side plate 371, and two of the four plates are cut in horizontal and vertical directions and coupled with the overlapped second side plate 371 to correspond to the centers of the four edges of the other side support plate 350. In these, horizontally and vertically separated plates are omitted to avoid complication of the drawings.

One of the four plates may be quadrupled and coupled as a single other plate 372 corresponding to the apex portion of the other support plate 350.

As described above, the other side plate member may include the larger-sized other side plate member and the smaller-sized side plate member derived from the largest other side plate by standardization by separation and transfer. According to this configuration, it is possible to provide the other side support plate of various shapes and structures without providing a separate second side plate member according to the shape and shape of the vacuum insulator.

The arrangement of the partial plate and the further plate member may be a preferred embodiment and a person skilled in the art of the invention may suggest other embodiments included within the scope of the same idea.

Fig. 15 is an enlarged view illustrating a portion a of fig. 14.

Referring to fig. 15, the other side support plate 370 has another side base 378 similar to the lattice of the one side support plate 350 and a groove 373 coupled to the column 356 at the intersection of the lattice of the other side base 378.

The radiation shield 32 may be supported between the stepped protrusion 3563 and the groove 373. The up-down position of the radiation shield 32 may be restricted between the groove 373 and the end of the stepped protrusion 3563, and the movement in the area direction may be restricted by the support column 3562.

Fig. 16 is a sectional view taken along line a-a' of fig. 15.

Referring to fig. 16, the support position of the radiation shield 32 in the vertical direction is restricted between the stepped protrusion 3563 and the groove 373. For this reason, it is preferable that the size of the hole provided in the radiation shield 32 is smaller than the size of the end of the stepped protrusion 3563 and the size of the end of the groove 373.

The vacuum insulation can be manufactured in various sizes, shapes and sizes. For example, the vacuum heat insulator disposed on the wall of a large-sized refrigerator would be disposed in a large plane, and the vacuum heat insulator disposed on the wall of a small-sized refrigerator may be disposed in a small plane.

As described above, it is not preferable to manufacture the respective support plates in order to cope with the sizes of the various shapes of the refrigerator because the cost of the product may increase. This is because the parts stock increases due to the inability to share the parts, and it is difficult to purchase the parts in the right place according to the demand.

To overcome this limitation, the present inventors have proposed to use partial plates 351, 352, 353, and 354, but it is difficult to cope with vacuum insulators having various sizes only by the partial plate concept.

Fig. 17 is a view of a support unit according to another embodiment.

Referring to fig. 17, one side support plate 3500 and the other side support plate 3700 may be manufactured as two partial plates. The partial plate may include a transverse length ratio of 3: 5, and a second type of partial plate 4002 having a lateral length ratio of 4: 10. The length ratio of the partial plates 4001 and 4002 may vary, and the above length ratio is merely an example. In addition, although the length ratio in the left-right direction is assumed to be 1 in the drawings: 1, but the embodiment is not limited thereto, and support plates having various shapes and sizes can be provided according to a combination of two partial plates.

The one side support plate 3500 and the other side support plate 3700 may be provided in a state of being rotated 90 degrees from each other. Due to this configuration, it is possible to prevent a reduction in coupling force at a portion where the partial plates are connected.

The coupling between one side support plate 3500 and the partial plate placed inside the other side support plate 3700 can be applied as such in the already described embodiment.

In this embodiment, when an imaginary line a-a is drawn in a direction along the edges of the one side support plate 3500 and the other side support plate 3700, the following features are exhibited. In the figure, the imaginary line is on the other support plate. Similar results can be obtained for one side support plate.

First, at least two partial plates in a line through which an imaginary line passes are identical. In one embodiment, there are two partial plates 4001 of the first type. This may have technical implications that increase the versatility of the components. That is, since at least two identical partial plates are used, mass production of identical partial plates can be caused.

Secondly, all the partial plates in the line through which the imaginary line passes are not identical. In this embodiment, not only the first type partial plate 4001 but also the second partial plate 4002 is used. This is a technical idea necessary to obtain one side or the other side support plate having various shapes and areas.

Third, at least two kinds of partial plates are used in a line through which an imaginary line passes. Accordingly, more various one side or the other side support plates can be provided, so that vacuum heat insulators of various shapes and sizes can be coped with. More preferably, by using two partial plates, it is expected that vacuum thermal insulators currently having various shapes and sizes can be manufactured while achieving versatility of partial plates.

According to the present embodiment, it can be seen that costs can be reduced by more actively sharing components with respect to vacuum heat insulators of various shapes and sizes.

Hereinafter, a preferred vacuum pressure of the vacuum insulator will be described.

Fig. 18 shows a graph showing the change in the thermal insulation performance and the change in the gas conductivity with respect to the vacuum pressure by applying the simulation.

Referring to fig. 18, it can be seen that as the vacuum pressure is reduced, that is, as the degree of vacuum is increased, the thermal load is reduced in the case of only the body (curve 1) or the case where the body and the door are coupled together (curve 2) compared to the case of a typical product formed by foaming polyurethane, thereby improving the thermal insulation performance. However, it can be seen that the degree of improvement in the heat insulating property gradually decreases. Also, it can be seen that as the vacuum pressure decreases, the gas conductance (curve 3) decreases. However, it can be seen that the ratio of the thermal insulation improving performance and the gas conductance gradually decreases although the vacuum pressure decreases. Therefore, it is preferable that the vacuum pressure is as low as possible. However, it takes a long time to obtain an excessive vacuum pressure, and a large amount of cost is consumed due to excessive use of the getter. In this embodiment, an optimum vacuum pressure is proposed from the above viewpoint.

Fig. 19 is a graph illustrating a result obtained by observing changes in time and pressure during the process of discharging the inside of the vacuum insulator when the supporting unit is used.

Referring to FIG. 19, in order to make the vacuum space part 50 in a vacuum state, gas in the vacuum space part 50 is exhausted by a vacuum pumpWhile evaporating latent gas (latent gas) remaining in the components of vacuum space section 50 by drying. However, if the vacuum pressure reaches a certain level or more, there is a point (Δ T1) where the level of the vacuum pressure cannot be increased any more. Thereafter, the getter (Δ T2) is activated by disconnecting the vacuum space part 50 from the vacuum pump and applying heat to the vacuum space part 50. If the getter is activated, the pressure in the vacuum space part 50 is reduced for a certain period of time, but then normalized to maintain a certain level of vacuum pressure. Maintaining the vacuum pressure at a level of about 1.8X 10 after activation of the getter^-6Torr (Torr).

In this embodiment, the point at which the vacuum pressure is not significantly reduced even though it is discharged by operating the vacuum pump is set to the minimum of the vacuum pressure used in the vacuum heat insulator, thereby setting the minimum internal pressure of the vacuum space part 50 to 1.8 × 10^-6And (4) supporting.

Fig. 20 is a graph obtained by comparing vacuum pressure with gas conductance.

Referring to fig. 20, the gas conductance with respect to the vacuum pressure depending on the size of the gap in the vacuum space part 50 is represented as a curve of the effective heat transfer coefficient (eK). The effective heat transfer coefficient (eK) was measured at three sizes of gaps of 2.76mm, 6.5mm and 12.5mm in the vacuum space part 50. The gap in the vacuum space part 50 is defined as follows. When the radiation shield 32 exists inside the vacuum space part 50, the gap is a distance between the radiation shield 32 and the plate member adjacent thereto. When the radiation resistant sheet 32 is not present inside the vacuum space part 50, the gap is a distance between the first plate member and the second plate member.

It can be seen that, since the size of the gap is small at the point corresponding to a typical effective heat transfer coefficient of 0.0196W/mK (which is provided by the insulation material formed of foamed polyurethane), the vacuum pressure is 2.65X 10 even though the size of the gap is 2.76mm^-1And (4) supporting. Meanwhile, it can be seen that the point at which the reduction of the adiabatic effect by the gas heat conduction is saturated (even if the vacuum pressure is reduced) is that the vacuum pressure is about 4.5 × 10^-3A point of rest. 4.5X 10^-3Vacuum pressure of the trayCan be defined as the point at which the reduction in the adiabatic effect caused by the heat transfer of the gas is saturated. Further, when the effective heat transfer coefficient is 0.1W/mK, the vacuum pressure is 1.2X 10^-2And (4) supporting.

When the vacuum space part 50 is not provided with the supporting unit but with the porous material, the size of the gap ranges from several micrometers to several hundred micrometers. In this case, even when the vacuum pressure is relatively high, that is, the degree of vacuum is low, the amount of radiant heat transfer is small due to the porous material. Therefore, the vacuum pressure is adjusted using an appropriate vacuum pump. Vacuum pressures suitable for corresponding vacuum pumps are about 2.0X 10^-4And (4) supporting. Further, at the point where the decrease in the adiabatic effect by the heat conduction of the gas is saturated, the vacuum pressure is about 4.7 × 10^-2And (4) supporting. Also, the pressure at which the decrease in the adiabatic effect due to the heat transfer of the gas reaches a typical effective heat transfer coefficient of 0.0196W/mK is 730 Torr.

When the support unit and the porous material are provided together in the vacuum space portion, a vacuum pressure that is intermediate between the vacuum pressure when only the support unit is used and the vacuum pressure when only the porous material is used can be generated and used.

In the description of the present disclosure, the means for performing the same action in each embodiment of the vacuum heat insulator may be applied to the other embodiment by appropriately changing the shape or size of the aforementioned other embodiment. Therefore, still another embodiment can be easily proposed. For example, in the detailed description, in the case of a vacuum heat insulator suitable as a door-side vacuum heat insulator, the vacuum heat insulator can be used as a main body-side vacuum heat insulator by appropriately changing the shape and configuration of the vacuum heat insulator.

The vacuum insulator proposed in the present disclosure may be preferably applied to a refrigerator. However, the application of the vacuum heat insulator is not limited to the refrigerator, and may be applied to various apparatuses such as a cryogenic refrigerator, a heating apparatus, and a ventilator.

Industrial applicability

According to the present disclosure, the vacuum insulator may be industrially applied to various heat insulating apparatuses. The heat insulating effect can be enhanced, so that the energy use efficiency can be improved and the effective volume of the equipment can be increased.