RU2776533C2 - Refrigerator, device with cooling and heating function, and vacuum adiabatic case - Google Patents

Abstract

FIELD: refrigerators.

SUBSTANCE: invention relates to refrigeration units for vehicles. A vacuum adiabatic case includes the first plate element forming at least a section of a wall of the first space, the second plate element forming at least a section of a wall of the second space, having a temperature different from that of the first space, a sealing part sealing the first plate element and the second plate element to provide the third space, a temperature of which has a value between the first space temperature and the second space temperature, and which is in a vacuum state, a support node supporting the third space, a heat resistant node reducing the amount of heat transferred between the first plate element and the second plate element, through which air is released from the third space, and a heat-exchange module contacting the inner surface of a cavity formed by the first plate element and the second plate element to perform heat exchange.

EFFECT: increase in a volume of a refrigerator, increase in the energy efficiency, elimination of a limitation related to slow cooling of products, and prevention of noise-related discomfort.

28 cl, 27 dwg

Description

The technical field to which the invention belongs

The present invention relates to a refrigerator, refrigeration or heating device and a vacuum adiabatic housing.

State of the art

Refrigerators are devices for storing food, such as food, refrigerated at low temperatures, including temperatures below freezing. This provides the benefit of improving the consumer experience or extending the shelf life of products.

Refrigerators are divided into stationary refrigerators using a commercial power supply and mobile refrigerators using a portable power supply. In addition, there has recently been an increase in the supply of refrigerators for a vehicle, which are used after being installed on a vehicle. Vehicle refrigerators are becoming more in demand as a result of the increase in the supply of vehicles and the increase in the number of premium vehicles.

Next, a conventional configuration of a refrigerator for a vehicle will be described.

First of all, an example is known in which heat in a refrigerator is forcibly removed to the outside of the refrigerator using a thermocouple. However, in this case, there is a limitation associated with a low cooling rate due to the low thermal efficiency of the thermocouple, which reduces user satisfaction.

Further, an example is known in which refrigerant or cold air is taken from an air conditioning system installed for air conditioning in a vehicle interior and used as a cooling source for a refrigerator in a vehicle.

This example has the disadvantage that a separate air or refrigerant flow path is required to extract air or refrigerant from the vehicle's air conditioning system. In addition, there is a limitation associated with the loss of low temperature energy when moving air or refrigerant along the flow path. In addition, there is a limitation in that, due to the above-described limitations, the installation location of the refrigerator for the vehicle is limited to being close to the air conditioning system of the vehicle.

In addition, an example is known in which a refrigeration cycle using a refrigerant is applied.

However, in this example, because the structure constituting the refrigeration cycle is large, most of the components are installed in the trunk, and only the refrigerator door opens into the interior of the vehicle. In this case, there is a restriction associated with the restriction of the installation location of the refrigerator for the vehicle. In addition, there is a limitation that the volume of the trunk is significantly reduced, which leads to a decrease in the amount of cargo that can be loaded into the trunk.

US Pat. No. 4,545,211 is a typical example of the configuration described above. The technology described in the document has the following limitations.

First of all, there is a limitation related to the reduction of the internal volume of the refrigerator for the vehicle due to the large volume of the engine room. In addition, there is a limitation that the driver cannot use the refrigerator for the vehicle while driving when the driver is driving the vehicle, since the refrigerator is installed in the rear seat, and also because the door opens in the direction it may be inconvenient for the driver to get food in front. Since the cooling in the refrigerator is by direct cooling, that is, by natural convection, the cooling of the product takes a long time. Since the engine room is directly open, there is a high possibility of foreign objects entering the inside of the engine room, which may cause damage. There is also a limitation related to the intake air admixture, since the intake air is not separated from the exhaust air, which reduces the thermal efficiency. In addition, there is a limitation related to the discomfort experienced by the user due to the noise of the engine room due to the use of the compressor.

The essence of the invention

Technical problem

Embodiments provide a refrigeration or heating device, which is configured to increase the volume of the refrigerator, and a vacuum adiabatic housing.

Embodiments also provide a refrigeration or heating device that is capable of overcoming the limitation associated with slow cooling of products placed in the refrigerator and a vacuum adiabatic housing.

Embodiments provide a refrigeration or heating device that is designed to improve energy efficiency and a vacuum adiabatic housing.

Embodiments provide a refrigeration or heating device that is configured to prevent discomfort due to noise and a vacuum adiabatic housing.

Technical solution

In one embodiment, to increase the internal volume of the refrigerator, the vacuum adiabatic housing includes: a first plate element and a second plate element, which form a third space in a vacuum state; and a heat exchange module in contact with the inner surface of the cavity formed by the first plate element and the second plate element.

To solve the problem of slow cooling of the product placed in the refrigerator, the heat exchange module may include: an evaporator evaporating the refrigerant; and a first compartment housing an evaporator fan on the evaporator to suck in air passing through the evaporator and exhaust air into the cavity.

To accurately determine the temperature in the cavity, the heat exchange module may include: an evaporator; and a third compartment, which is separated from the first compartment, in which the evaporator fan is located, to accommodate the temperature sensor.

To illuminate the cavity, the vacuum adiabatic housing may further include a second compartment, which is separated from the first compartment and the third compartment to accommodate the lamp,

To improve the accuracy of temperature detection by the temperature sensor, the second compartment may be located between the first compartment and the third compartment. In addition, the third compartment may be located in the corner of one side of the heat exchange module.

To apply the refrigeration cycle and provide user access, the third compartment may be located in one direction relative to the first compartment, and the passage for the pipeline through which the refrigerant pipeline passes, may be located in the other direction.

To further increase the internal volume of the refrigerator, the evaporator fan may include a centrifugal fan and may draw in air from the rear to discharge air in a downward direction.

In another embodiment, in order to improve energy efficiency, the refrigeration or heating device includes: a bottom frame of the refrigerator, on which a cavity and an engine room are mounted in parallel; a second heat exchange module located in the cavity on one surface of the cavity to provide heat exchange of the refrigerant; and a temperature sensor provided in the second heat exchange module for measuring the temperature in the cavity.

To improve the accuracy of determining the temperature in the cavity, the temperature sensor can be located in the corner of the upper section of the second heat exchange module. The temperature sensor may be in communication with the interior of the cavity.

To prevent discomfort due to noise and to increase the internal volume of the refrigerator, the second heat exchange module may include an evaporator located on the bottom side and a first compartment in which a Sirocco type fan is provided is located on the top side of the evaporator. To further increase the internal volume of the refrigerator, the Scirocco fan can draw in air from the rear side and exhaust air from the bottom side.

To improve the accuracy of determining the temperature by the temperature sensor, another compartment can be located between the first compartment and the third compartment, in which the temperature sensor is located.

In another embodiment, in order to provide sufficient internal volume of the refrigerator, the refrigeration or heating device includes: a bottom frame of the refrigerator, on which a cavity and an engine room are mounted; a second heat exchange module located in the cavity on one surface of the cavity to provide heat exchange of the refrigerant; a cover forming the interior of the second heat exchange module; and a fan located in the second heat exchange module for blowing air.

For uniform cooling of food in the refrigerator, the cover may include: a back cover; and a front cover having a cold air intake hole in the lower portion corresponding to the back cover, and a cold air outlet hole located approximately at the center of the height.

To improve the efficiency of cold air circulation, the cold air outlet may be located at a distance between one second of the height and two thirds of the height from the bottom of the cavity.

In order to uniformly cool the container, the cold air outlet may be centrally located in the transverse direction of the cold air outlet cavity which is supplied from the bottom side towards the front.

To adjust the direction of cold air, the cover may include a ventilation plate.

To ensure the convenience of using the refrigerator, the ventilation plate may move with the container holder holding the container, or the ventilation plate may include a vertical ventilation plate and an inclined ventilation plate.

Useful effects of the invention

According to the invention, the vacuum adiabatic body includes: a first plate element and a second plate element forming a third space which is in a vacuum state; and a heat exchange module in contact with the inner surface of the cavity formed by the first plate member and the second plate member, the vacuum adiabatic case can be installed in a narrow space, and the food storage space can be enlarged, which makes the refrigerator convenient to use.

The heat exchange module may include: an evaporator evaporating a refrigerant; and a first compartment housing an evaporator fan on the evaporator to suck in air passing through the evaporator and exhaust air into the cavity. Thus, the refrigerator can be used more effectively in a narrow space.

The heat exchange module may include a third compartment, which is separated from the first compartment, in which the evaporator and evaporator fan are located, to accommodate a temperature sensor in order to more accurately determine the temperature in the cavity using a temperature sensor.

Additionally, a second compartment can be provided that is separated from the first compartment and the third lamp housing compartment to prevent heat transfer between the compartments and illuminate the inside of the refrigerator.

The second compartment may be located between the first compartment and the third compartment, and the third compartment may be located in the corner of one side of the heat exchange module. In this way, the temperature sensor can accurately detect the cavity temperature independently of other external components and their operation.

The third compartment may be located in one direction relative to the first compartment, and the passage for the pipeline through which the refrigerant pipeline passes, may be located in the other direction. Thus, the internal volume of the refrigerator, which is served by the circulating refrigerant, can be greatly increased, and thus it is convenient for the user to take out the storage container.

The evaporator fan may include a centrifugal fan and may draw in air from the rear to discharge air in a downward direction to reduce the mechanism that generates airflow and reduce noise.

The refrigeration or heating device includes: a lower frame of the refrigerator, on which a cavity and an engine room are installed in parallel; a second heat exchange module located in the cavity on one surface of the cavity to provide heat exchange of the refrigerant; and a temperature sensor provided in the second heat exchange module for measuring the temperature in the cavity. Thus, since the cavity temperature is accurately measured and controlled, excessive power consumption can be prevented and the interior volume of the refrigerator can be increased.

The temperature sensor may be located in the corner of the upper portion of the second heat exchange module. A temperature sensor may be in communication with the interior of the cavity to accurately measure the interior temperature of the cavity.

The second heat exchange module may include an evaporator located on the bottom side, and a first compartment in which a Sirocco type fan is provided is located on the upper side of the evaporator. Thus, user satisfaction can be ensured by reducing noise and increasing the internal volume of the refrigerator.

The Scirocco type fan can draw in air from the rear side and exhaust air from the bottom side to further increase the internal volume of the refrigerator.

Between the first compartment and the third compartment may be located another compartment in which the temperature sensor is located. Thus, the temperature in the cavity can be measured more accurately.

Refrigeration or heating device includes: the bottom frame of the refrigerator, on which the cavity and the engine room are installed; a second heat exchange module located in the cavity on one surface of the cavity to provide heat exchange of the refrigerant; a cover forming the interior of the second heat exchange module; and a fan located in the second heat exchange module for blowing air. Thus, a sufficient internal volume of the refrigerator can be ensured, and the temperature of the refrigerator storage container can be uniformly controlled.

The cover may include: a back cover; and a front cover having a cold air intake hole in the lower portion corresponding to the back cover, and a cold air outlet hole located approximately at the center of the height. In this way, the temperature of the product in the refrigerator can be evenly adjusted.

The cold air outlet may be located between one second of the height and two thirds of the height from the bottom of the cavity. Thus, cold air can circulate more uniformly in the cavity.

The cold air outlet may be centrally located in the transverse direction of the cold air outlet which is supplied from the lower side towards the front. Thus, the temperature in the cavity can be uniformly controlled.

The lid may include a vent plate, and the vent plate may move with the container holder holding the container. In addition, the ventilation plate may include a vertical ventilation plate and an inclined ventilation plate. Thus, uniform temperature adjustment by the ventilation plate and fast temperature adjustment of the container selected by the user can be performed simultaneously.

Description of drawings

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

2 is an enlarged perspective view illustrating a vehicle console.

Fig. 3 is a schematic perspective view illustrating the interior of a refrigerator for a vehicle.

Fig. 4 is a view illustrating the relative position of the engine room and the cavity.

Fig. 5 is an exploded perspective view of the evaporator module.

Fig. 6 is a view for explaining the airflow outside the engine room of the vehicle refrigerator.

7 is a perspective view of the adiabatic member for the hinge portion.

8-11 are a plan view, a front view, a bottom view, and a left view of the adiabatic member for the hinge portion.

Fig. 12 is an exploded perspective view illustrating the relative positions of the evaporator module and the adiabatic member for the hinge portion.

13 is a sectional view of the evaporator module.

Fig. 14 is a schematic front view illustrating the inside of the cavity for explaining the position of the cold air outlet.

Fig. 15 is a view illustrating the cold air outlet direction through the cold air outlet.

Fig.16-18 are graphs for explaining the results of the experiments shown in Fig.15.

Fig. 19 is a view illustrating the execution of uniform cooling according to the embodiment.

Fig. 20 is a view illustrating the execution of rapid cooling according to the embodiment.

Fig. 21 is a view illustrating a configuration example of a cold air exhaust vent plate.

22 and 23 are views illustrating another example of a cold air exhaust vent plate.

24 is a view illustrating the internal configuration of a vacuum adiabatic body according to various embodiments.

25 is a view of the heat transfer inhibiting sheet and a peripheral portion of the heat transfer inhibiting sheet.

Fig.26 is a graph illustrating the results obtained by monitoring the time and pressure in the process of evacuating the interior of the vacuum adiabatic body when using the reference node.

Fig.27 is a graph obtained by comparing the pressure of the vacuum and the thermal conductivity of the gas.

Best way to carry out the invention

In the following description according to the embodiments with reference to the drawings, the same reference numerals are indicated in different drawings in the case of the same components.

In addition, a description of each drawing will be made with reference to the direction that is indicated when looking at the vehicle from the front of the vehicle, and not from the driver's side, in the direction of travel of the vehicle. For example, the driver sits on the right and the passenger sits on the left.

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

According to figure 1, in the vehicle 1 is provided with a seat 2 to accommodate the user. Seat 2 may be provided with a pair of seats horizontally spaced from it. A console is disposed between the seats 2 and the driver can place in the console elements necessary for driving or components necessary for operating the vehicle. As an example of the seats 2, the front seats for driver and passenger can be described.

It should be understood that a vehicle includes various components necessary to propel the vehicle, such as a movement device, such as a wheel, a drive device, such as a motor, and a steering device, such as a steering wheel.

The refrigerator for the vehicle according to the embodiment can preferably be located in the console. However, the embodiment of the present invention is not limited to this. For example, a refrigerator for a vehicle may be installed in different locations. For example, a vehicle refrigerator may be installed in the space between the rear seats, in the door, glove box, and center console. One of the key aspects of installing a refrigerator for a vehicle according to an embodiment is power supply and minimum space. However, the main advantage of the embodiment is that the refrigerator can be installed in the console between the seats in a limited space due to the design of the vehicle.

2 is an enlarged perspective view illustrating a vehicle console.

According to Figure 2, the console 3 may be provided as a separate component made of a material such as a polymer. A steel frame 98 may be additionally provided below the console 3 to provide strength to the vehicle, and a sensitive component 99, such as a sensor, may be located in the space between the console 3 and the steel frame 98. The sensing component 99 may be a component necessary for accurately detecting an external signal and measuring the signal at the driver's position. For example, an airbag sensor may be installed that is directly related to driver safety.

The console 3 may have an interior console space 4 and the console space 4 can be covered by a console cover 300 . The console cover 300 can be rigidly mounted on the console 3. Thus, external foreign objects cannot enter the console through the console cover 300. In the console space 4, a refrigerator 7 for the vehicle is installed.

In the right surface of the console 3, a suction port 5 can be provided to supply air from the interior of the vehicle to the space 4 of the console. The suction port 5 may face the driver. An outlet 6 may be provided in the left surface of the console 3 to discharge the air heated during operation of the vehicle refrigerator from the console space 4 . The outlet 6 may face the passenger. A grille can be provided on each of the suction port 5 and the outlet port 6, which prevents the user's hand from accidentally entering and thereby ensures safety, prevents objects falling from above from entering, and directs the discharged air downward rather than toward the person.

Fig. 3 is a schematic perspective view illustrating the interior of a refrigerator for a vehicle.

3, the vehicle refrigerator 7 includes a refrigerator bottom frame 8 supporting components, an engine room 200 provided on the left side of the refrigerator bottom frame 8, and a cavity 100 provided on the right side of the refrigerator bottom frame 8. The engine room 200 may be covered with an engine room cover 700 and the top side of the cavity 100 may be covered with a console cover 300 and a door 800.

The engine room cover 700 can not only guide the flow path of the cooling air, but also can prevent foreign objects from entering the engine room 200.

A controller 900 may be disposed on the cover 700 of the engine room to control the operation of the refrigerator 7 for the vehicle. Since the controller 900 is installed in an appropriate position, the vehicle refrigerator 7 can operate smoothly in a proper temperature range in a narrow space within the console space 4.

That is, the controller 900 can be cooled by air passing through the gap between the engine room cover 700 and the console cover 300, and is separated from the interior of the engine room 200 by the engine room cover 700. Thus, the controller 900 is not exposed to heat from the engine room 200.

The console cover 300 may not only cover the open upper portion of the console space 4, but may also cover the upper edge of the cavity 100. A door 800 may be additionally installed on the console cover 300 to allow a user to close an opening through which products can be removed from the cavity 100. Door 800 can be opened using the rear portions of the console cover 300 and cavity 100 as hinge points.

Here, the opening in the console cover 300, door 800, and cavity 100 provide the user with convenient control of the door 800, since the console cover 300, door 800, and cavity 100 are positioned horizontally as viewed from the user's side and are also positioned at the back of the console.

In the engine room 200, a condensing unit 500, a dryer 630, and a compressor 201 may be installed in series in the cooling air flow direction. The section of the pipeline 600 of the refrigerant may continue into the cavity 100 to supply the refrigerant. The refrigerant conduit 600 may extend outside the cavity 100 through an upper opening designed to remove products from the cavity 100.

Cavity 100 has an open top surface and five surfaces covered by vacuum adiabatic casing 101. Cavity 100 may be thermally insulated by a separate vacuum adiabatic casing or at least one or more vacuum adiabatic casings connected to each other. The cavity 100 may be provided with a vacuum adiabatic casing 101. In addition, a cavity 100 may be provided to allow products to be withdrawn through one of the surfaces not covered by the vacuum adiabatic casing 101.

The vacuum adiabatic body 101 may include a first plate element 10 providing a boundary of the low temperature interior of the cavity 100, a second plate element 20 providing a boundary of the high temperature outer space, and a heat transfer inhibiting sheet 60 preventing heat transfer between the plate elements 10 and 20. Since for To achieve maximum adiabatic efficiency, the vacuum adiabatic body 101 has a small thickness of the adiabatic layer, a cavity 100 having a large volume can be provided.

A vacuum and getter hole may be provided on one surface to create a vacuum in the interior of the vacuum adiabatic housing 101 and to install a getter that maintains the vacuum state. The vacuum and getter hole 40 can provide vacuum and getter at the same time, which helps to reduce the size of the refrigerator 7 for the vehicle.

An evaporative module 400 may be installed in the cavity 100. The evaporative module 400 may force the evaporation heat of the refrigerant that enters the cavity 100 through the refrigerant conduit 600 into the cavity 100. the space inside the cavity, which is used by the user, can be further increased.

Fig. 4 is a view illustrating the relative position of the engine room and the cavity.

4, an evaporator module 400 is located in the cavity 100. That is, the evaporator module 400 is located in the interior of the cavity 100 having the vacuum adiabatic housing 101 as an outer wall. Thus, the space utilization efficiency of the engine room can be improved, and the interior space of the cavity 100 can be enlarged. This is because the vacuum adiabatic vessel provides high adiabatic efficiency even if the vacuum adiabatic vessel is thin.

The refrigerant conduit 600, which directs the refrigerant to the evaporator module 400, enters the evaporator module 400 through the top surface of the cavity 100.

The refrigerant conduit 600 may be considered to pass through the vacuum adiabatic housing 101 to reduce its volume. However, since the vehicle is subject to vibrations and the inside of the vacuum adiabatic case 101 is kept in a vacuum state, the seal of the contact area between the refrigerant pipe 600 and the vacuum adiabatic case 101 may be damaged. Thus, it is undesirable for the refrigerant line 600 to pass through the vacuum adiabatic case 101. For example, air leakage may occur due to vehicle vibration. When air leaks from the vacuum adiabatic housing, the adiabatic efficiency can deteriorate significantly.

The evaporation module 400 may preferably be mounted in contact with the hinge point of the door within the cavity 100, i. e. back surface of the cavity 100. This is because the path of the refrigerant conduit 600 to the evaporator module 400 should be as short as possible to ensure sufficient internal volume of the cavity 100. In addition, the internal volume of the cavity can be maximized.

More preferably, the refrigerant conduit 600 passing over the vacuum adiabatic housing 101 passes through the hinge point of the door. If the evaporative module 400 does not pass through the hinge point of the door, due to the length of the refrigerant conduit 600 and the adiabatic characteristics of the refrigerant conduit 600, loss of cavity volume and low temperature energy may occur.

The condensation module 500 can be attached to the bottom frame 210 of the engine room using the rear attachment assembly. The air drawn in through the condenser module 500 may cool the compressor 201 and then discharge downward from the compressor 201.

The engine room cover 700 may be attached to the left side of the cavity 100 to cover the engine room 200. From the top side of the engine room cover 700, airflow for cooling may occur, and the controller 900 may be provided in the cooling path for proper cooling.

11 is an exploded perspective view of the evaporator module.

5, the evaporator module 400 includes a back cover 430 located on the rear side for accommodating components, and a front cover 450 located on the front side of the back cover 430 and facing the cavity 100. Between the front cover 450 and the back cover 430 in the evaporator module 400, space may be provided to accommodate the components.

In the space formed by the front cover 450 and the rear cover 430, an evaporator 410 is located on the lower side, and an evaporator fan 420 is located on the upper side. The evaporator fan 420 may be a centrifugal fan designed to be installed in a narrow space. In particular, as the narrow space evaporator fan 420, a Sirocco type fan including a fan inlet 422 having a large air intake area and a fan outlet 421 blowing air at a high speed in a predetermined blowing direction can be used.

Since the Scirocco fan can operate with low noise, the Scirocco fan can also be used in low noise environments.

The air passing through the evaporator 410 is sucked into the fan inlet 422, and the air exhausted from the fan outlet 421 is forced into the cavity 100. To this end, a predetermined space can be provided between the evaporator fan 420 and the back cover 430.

The back cover 430 may be provided with a plurality of compartments for receiving components. In particular, the evaporator 410 and the evaporator fan 420 are located in the first compartment 431 to direct the flow of cold air. In the second compartment, a lamp 440 may be provided to illuminate the inside of the cavity 100 so that the user can look inside the cavity 100. In the fourth compartment 434, a temperature sensor 441 is located to measure the internal temperature of the cavity 100 and control the refrigerator for the vehicle accordingly.

By placing the temperature sensor 441 in the fourth compartment 434 for measuring the temperature in the cavity 100, the flow in the cavity does not directly affect the temperature sensor 441. That is, the cold air from the evaporator 410 does not directly affect the third compartment 433.

Although there is no third compartment 433 in some cases, the third compartment 433 may be provided to prevent an error in determining the internal temperature of the cavity 100 due to heat conduction.

The fourth compartment 434 and the temperature sensor 441 are located at the upper left end, i. e. in the corner of the evaporator module 400 which is furthest away from the evaporator 410. This is to prevent the cold air from the evaporator 410 from being influenced directly. be isolated from the first compartment 431 by other compartments 432 and 433.

Next, the internal structure of the first compartment 431 will be described in detail.

On the upper side of the first compartment 431, a fan case 435 having a circular shape is provided to receive the evaporator fan 420, and on the lower side of the first compartment 431, an evaporator housing portion 437 is provided on which the evaporator 410 is located.

A pipeline passage 436 is provided on the left side of the fan housing 435. The conduit passage 436 may be a portion through which the refrigerant conduit 600 passing through the vacuum adiabatic housing 101 is led to the evaporator module 400, and which is provided in the left corner portion of the evaporator module 400. The refrigerant conduit 600 may include two conduits that surrounded by an adiabatic element so that the two conduits passing through the evaporator module 400 can exchange heat with each other. Thus, the conduit passage 436 may have a predetermined volume. The piping passage 436 may extend vertically from the left side of the evaporator module 400 to increase the filling density of the space within the evaporator module 400.

As described above, an evaporator 410 and an evaporator fan 420 are provided in the back cover 430 to perform cooling of the air inside the cavity and circulating the air inside the cavity.

Like the back cover 430, the front cover 450 has a substantially rectangular shape. In the lower portion of the front cover 450, a cold air inlet 451 is formed to direct air to the underside of the evaporator 410, and a cold air outlet 452 is aligned with the fan outlet 421. The cold air outlet 452 may have a shape whose inner surface gently curves to discharge air discharged downward from the evaporator fan 420 in a forward direction.

The front cover 450, aligned with the second compartment 432, may be opened, or a window may be provided in the portion of the front cover 450 to allow light from the lamp 440 to enter the cavity 100.

The front cover 450 is provided with a vent 454 aligned with the fourth compartment 434. The air exhausted from the cold air outlet 452 circulates in the cavity 100 and then enters the vent 454. Thus, the internal temperature of the cavity 100 can be detected from more high precision. For example, an erroneous measurement of the internal temperature of the cavity 100 due to a large amount of cold air discharged from the cold air outlet 452 can be prevented. Here, the cold air can have a direct effect on the temperature inside the cavity without being influenced by the cold air blown out of the evaporator fan 420. To do this, the fourth compartment 434 may be located in the upper right corner of the rear surface of the cavity.

Fig. 6 is a view for explaining the airflow outside the engine room of the vehicle refrigerator.

6, the air entering the suction port 5 moves to the left side of the vehicle refrigerator through the space between the vacuum adiabatic case 101 forming the front wall of the cavity 100 and the front surface of the console space 4. Since there is no heating source on the right side of the vehicle cooler, the intake air can maintain its original temperature.

The air moving towards the left side of the vehicle refrigerator can change its direction and move towards the rear side along the top surface of the engine room cover 700 outside the engine room 200.

To smoothly guide air flow, the height of the engine room cover 700 may gradually increase rearward from the front surface 710. In addition, to provide space for the controller 900 and prevent components in the engine room from colliding with each other, the top surface of the engine room cover 700 may be stepped form.

Specifically, a first step portion 732, a second step portion 733, and a third step portion 735 may be provided in a rearward direction from the front surface. On the second step portion 733, a controller accommodating portion 734 having the same height as the third step portion is provided. Due to this structure, the controller 900 can be placed parallel to the third stepped portion 735 and the controller accommodating portion 734.

Air moving along the top surface of the engine room cover 700 may cool the controller 900. As the controller cools, the air may become slightly warm.

The air moving towards the rear side of the engine room cover 700 turns downward. A large open suction port is formed in the rear surface of the engine room cover. To this end, a predetermined space can be provided between the rear surface of the engine room cover 700 and the rear surface of the console space 4 .

Thereafter, the air cooling the inside of the engine room cover 700 is discharged to the outside through the bottom of the engine room.

As described above, an evaporator module 400 is disposed on the rear side of the cavity 100, and a refrigerant conduit 600 extends above the cavity 100 to supply refrigerant to the evaporator module 400. In addition, the door hinge 800 and the evaporator module 400 are located on the rear side of the cavity such that the rear the area of the cavity is not protected from heat.

To overcome this limitation, an adiabatic element is provided for the hinge portion. The adiabatic member 470 for the hinge portion thermally insulates the upper portion of the evaporator module 400, the space between the evaporator module 400 and the back wall of the cavity 100, and the area of contact between the regenerative adiabatic element 651 inserted into the cavity and the interior of the cavity. The rear surface and side surface of the evaporator module 400 may be thermally insulated by the cavity. The cavity may be isolated by a third space provided in a vacuum state.

As described above, a cantilever cover 300 is additionally provided above the adiabatic hinge member 470 for complete thermal insulation.

7 is a perspective view of the adiabatic member for the hinge portion.

7, the adiabatic member 470 for the hinge portion includes an inner support 473 covering the regenerative adiabatic member 651 and being inserted into the inner bearing portion 373, an outer bearing being inserted into the outer bearing portion 372, and a connecting bar 471 connecting the bearings 472 and 473 with each other and a thermally insulating upper section of the evaporator module 400.

Since the supports 472 and 473 are inserted into the support portions 372 and 373, the adiabatic member for the hinge portion and the console cover 300 can be connected to each other. In addition, since the cover of the console 300 is rigidly mounted, the adiabatic member 470 for the hinge portion can be fixed relative to the cavity 100. That is, the supports 472 and 473 provide intimate contact of the components in the rear space within the cavity 100, while supporting the evaporative module 400. Thus, components can be in close contact with each other, preventing cold air from escaping. In addition, the turning function of the door 800 becomes more reliable.

The supports 472 and 473 may each be of a structure whose cross-sectional area gradually decreases towards its end so that the supports 472 and 473 can be inserted into the support portions 372 and 373.

The thickness of the inner support 473 may be greater than the thickness of the outer support 472. This is due to the fact that heat losses may occur due to the regenerative adiabatic element 651. It is understood that due to the regenerative adiabatic element 651 passing through the vacuum adiabatic element, cold air leakage may occur with a high probability.

On the inner surface of the inner support 473, a regenerative adiabatic element receiving portion 476 is provided, the shape of which closely matches the appearance of the regenerative adiabatic element 651. Thus, the regenerative adiabatic element can be bent into a smooth arc shape. The lower end surface of the regenerative adiabatic element receiving part 476 can be located at the upper end of the vacuum adiabatic body 101. Thus, the mutual vertical positioning of the adiabatic element 470 for the hinge part and the cavity 100 can be more accurate, and no gap is formed between the components.

An inner mounting portion 477 may be further provided extending downward from the rear portion of the portion 476 to receive the regenerative adiabatic element. The inner mounting portion 477 can correspond to the inner surface of the vacuum adiabatic body 101, and thus the relative position of the adiabatic member 470 for the hinge portion in the longitudinal direction can be more reliably maintained. An outer mounting portion 478 corresponding to the inner mounting portion 477 may also be provided on the outer support 472.

On the connecting bar 471, a portion for mounting the evaporator module 400 may be provided. Specifically, a portion for mounting a cover 488, a portion for mounting a fan case 474, and a portion for mounting a second compartment 475 may be provided. The relative positioning of the adiabatic member 470 for the hinge part and the cavity in the transverse direction can be provided by the cover setting part 488, whereby each of the fan casing setting part 474 and the second compartment setting part 475 is formed according to the shape of the top surface of the evaporator module 400 to prevent cold leakage. air through the contact area between the evaporator module and the adiabatic element for the hinged part.

According to the above-described configuration, outside air can be prevented from leaking through the contact area of various components with the adiabatic member for the hinge portion to improve the adiabatic efficiency with respect to a portion that is not protected from heat leakage.

8-11 are a plan view, a front view, a bottom view, and a left view of the adiabatic member for the hinge portion.

Referring to Figs. 8-11, the configuration of the adiabatic member for the hinge part and the function of each component will become more clear.

Within the supports 472 and 473, an outer mounting slot 480 and an inner mounting slot 479 are provided, respectively. They are configured to receive a support portion of the console cover that becomes thicker to receive the hinge pin of the door in the support portions 372 and 373 provided on the console cover 300.

The second compartment fitting portion 475 may be of a recessed design and provide an area through which a structure such as a wire that exits the evaporator module 400 is exposed to the outside.

Skirt 478 further extends downward into portion 476 to receive the regenerative adiabatic element. The skirt 478 may be a portion that further extends downward and facilitates the insertion of the regenerative adiabatic element 651 into the cavity 100.

Fig. 12 is an exploded perspective view illustrating the relative positions of the evaporator module and the adiabatic member for the hinge portion.

12, on the adiabatic element 470 for the hinge part, there is an internal support 473 covering the regenerative adiabatic element 51 and a conduit passage 436 to improve the adiabatic efficiency.

On the adiabatic element 470 for the hinge part is an external support 472, which closes the compartment and is insulated from the outside.

A connection bar 471 is also provided connecting the supports 472 and 473 to each other and thermally insulating the top portion of the evaporator module 400.

The adiabatic hinge member 470 can keep the components in close contact in the back space within the cavity while supporting the evaporator module 400. Thus, the components can be in close contact with each other, preventing cold air from escaping. In addition, the support portions 372 and 373 and the supports 472 and 473 may be nested within each other to more securely support the door 800.

The thickness of the inner support 473 may be greater than the thickness of the outer support 472. As described above, this is necessary to prevent heat loss that may occur due to the regenerative adiabatic element 651.

For this, the mutual vertical positioning of the adiabatic element 470 for the hinge part and the cavity 100 can be more accurate, and no gap is formed between the components to further reduce heat loss due to the regenerative adiabatic element receiving portion 476 provided on the inner surface of the inner support 473.

To further reduce cold air leakage from the cavity, an inner mounting portion 477 and an outer mounting portion 478 may be provided.

Installation of the upper ends of the vacuum adiabatic case 101 and the evaporator module 400, which form the cavity 100, can be performed more accurately by the lid mounting portion 488, the fan case mounting portion 474, and the second compartment mounting portion 475.

Between the upper ends of the adiabatic member 470 for the hinge portion and the evaporative module, a wire may be passed to supply power to the sensor and light source provided in the evaporative module. Therefore, the operation of the evaporator module can be ensured.

13 is a sectional view of the evaporative module, where the left and right sides correspond to the back and front sides.

Referring to Fig. 13, the arrows show the airflow within the evaporator module 400.

In particular, the flow of cold air will be described. The air entering through the cold air inlet 451 from the bottom side of the front cover is cooled while passing through the evaporator 410. The cooled air moves to the rear side of the evaporator fan 420, passes through the fan inlet 422 on the back surface of the evaporator fan 420, and is discharged downward in the direction release 421 fan under the action of centrifugal force. The evaporator fan can be a Sirocco type fan, and the shape of the fan housing and the position of the fan can be adjusted to direct the outlet down.

The air discharged through the fan outlet 421 changes direction and moves towards the front side through the cold air outlet 452, and then is discharged into the cavity 100. In the cold air outlet 452, a cold air outlet guide 456 having a smooth curve can be provided. shape so that the air discharged downwards is smoothly curved forward and discharged.

Preferably, the interior of the cavity can be uniformly cooled.

For example, if the containers on one side and the other are cooled to different temperatures, several people will not be able to enjoy cold drinks at the same time. From this point of view, it is important to determine exactly where the cold air outlet 452 should be formed on the front cover 450, as well as the direction of the cold air outlet.

Fig. 14 is a schematic front view illustrating the inside of the cavity for explaining the position of the cold air outlet.

As shown in FIG. 14, the cold air outlet 452 extends transversely at a substantially center height of the cavity.

That is, when the interior of the cavity is divided into three parts, the cold air outlet 452 is located in the central third. As a result, the air discharged from the middle section passes through the internal obstacles and then moves down into the evaporator module 400. In addition, the cold air outlet 452 can extend horizontally and therefore has a considerable width in the transverse direction, so that the air is uniformly is released into the cavity 100.

More preferably, the cold air outlet 452 may be located at a distance from one second of the height to two thirds of the height from the bottom of the cavity 100.

This is because the cold air discharged from the cold air outlet 452 collides with the storage container located in the cavity. Here, since the upper portion of the storage container 498 is smaller than the body, cold air can enter the front of the cavity 100. In contrast, since a small gap is provided between the bodies of the storage containers 498, and therefore there is a high flow cold air into the front of cavity 100 is difficult.

That is, since the cold air outlet 452 is located at a distance of one second of the height to two thirds of the height from the bottom of the cavity 100, a cold air flow to the front of the cavity 100 through the opening of the storage container and a cold air flow can be simultaneously provided. air remaining in the back of cavity 100 due to collision with the body of the storage container. Thus, simultaneous cooling of the front and back of the cavity 100 is ensured, and thus all products in the cavity 100 are cooled evenly.

If the products are not in contact with each other, the cold air outlet 452 may be located at a distance of one second of the height in the transverse direction. Thus, the cold air passing through the storage container 498, ie. cold air passing between the storage containers 498 and cold air that cannot pass between them can be separated from each other. Two rows can be placed in the cavity, i.e. two rows of containers for drinks. In this case, the size of the beverage container must be taken into account and the number of beverage containers placed in the narrow space of the console must be taken into account.

Fig. 15 is a view illustrating the cold air outlet direction through the cold air outlet, and Figs. 16 to 18 are graphs for explaining the results of the experiments shown in Fig. 15. Here the horizontal axis shows the cooling time and the vertical axis shows the temperature.

In FIG. 15, ① denotes a case where the cold air outlet 452 is formed approximately at the center when viewed from the top, bottom, left, and right sides of the back surface of the cavity, to discharge cold air to the right with respect to FIG. 15, ② denotes a case where the cold air outlet 452 is formed approximately in the center, when viewed from the top, bottom, left and right sides of the back surface of the cavity, to discharge the cold air straight up with respect to Fig. 15, and ③ indicates the case where the cold air outlet 452 is formed from the top side, when viewed from the top and bottom sides of the back surface of the cavity, and from the right side, when viewed from the left and right sides of the back surface of the cavity, to discharge cold air to the left with respect to Fig.15.

In addition, the cavity 100 accommodates four storage containers 498, designated by different reference numerals depending on their position.

According to Fig. 16, it can be seen that the container ① at the front and right is cooled quickly, and it takes about 22 minutes to cool the container by about 10 degrees. Thus, it can be seen that the cooling slows down in the following order ②, ③ and ④.

In this case, it can be seen that the deviation between the cooling rates of the containers ① ②, ③ and ④ is excessively large.

17, it can be seen that the front and left container ③ cools quickly, and it takes about 24 minutes to cool the container by about 10 degrees. Thus, it can be seen that the cooling slows down in the following order ④, ① and ②. It has been found that although the cooling rate of the storage container that cools the fastest slows down compared to the case shown in FIG. 16, the deviation between the cooling rates of the storage containers decreases.

In this case, the storage containers ③ and ④ are considered to cool faster due to the properties of the evaporator fan 420 provided as a centrifugal fan. In the case shown in FIG. 17, the current position is close to the position of the driver, and the comfort level of the driver is improved.

18, it can be seen that the front and right container ④ cools quickly, and it takes about 28 minutes to cool the container by about 10 degrees. Thus, it can be seen that the cooling slows down in the following order ②, ③ and ①. It has been found that the cooling rate of the storage container which cools the fastest slows down compared to the case shown in FIG. 17, and the deviation between the cooling rates of the storage containers is further reduced.

Considering each experiment described above, it has been found that it is possible to provide uniform cooling of the cavity 100 and at the same time provide rapid cooling in a particular position. Most preferred is a direct air outlet towards the front side of the cavity 100 along with the vertical and horizontal positions of the cold air outlet 452 shown in FIG.

It is also important to ensure that a particular storage container is quickly cooled and that the entire interior of cavity 100 is cooled evenly. For example, it is important that a driver be able to quickly cool one storage container when he is driving the vehicle.

An embodiment for realizing uniform cavity cooling along with rapid cooling of a particular storage container is described below.

Fig. 19 is a view illustrating the execution of uniform cooling according to the embodiment, and Fig. 20 is a view illustrating the execution of rapid cooling according to the embodiment.

19 and 20, the container holder 460 for holding the storage container is rotatably mounted on at least one of the rear cover 430 and the front cover 450 on the periphery of the cold air outlet 452.

The container holder 460 is provided with an extension 463 that is supported by and extends from the sides of the lids 430 and 450, a container holding portion 462 that folds away from the end of the extension 463 and allows the user to grip the storage container 498, and a holder handle 461 that the user grasps. can rotate or pull out the container holder 460.

In the cold air outlet 452, a cold air outlet vent plate 457 is provided, and the cold air outlet vent plate 457 is rotatable when the container holder 460 is rotated.

For example, in the case where the container holder 460 is directed to the evaporator module 400 (see FIG. 19), the ventilation plate 457 may be positioned so that the cold air passing through the cold air outlet 452 is directed straight. In the case where the container holder 460 is directed away from the evaporator module 400 (see FIG. 20), the ventilation plate 457 can be rotated so that cold air passing through the cold air outlet 452 enters the storage container 498.

The cold air outlet vent plate 457 may be positioned inside the cold air outlet guide 456.

Next, the connecting structure between the container holder 460 and the cold air outlet vent plate 457 will be described with reference to the configuration view of the cold air outlet vent plate illustrated in FIG.

As shown in FIG. 21, the container holder 460 can be rotated by the support axis 466 of the holder at one point of the lids 430 and 450.

In addition, the cold air outlet vent plate 457 can be rotated by the vent plate bearing shaft 468 at another point of the covers 430 and 450. A plurality of cold air outlet plates 457 are connected to each other by a parallel linkage mechanism 465 on the side opposite to the bearing shaft placement side. 468 ventilation plate. Thus, when one vent plate 457 is rotated to discharge cold air, the other vent plate 457 to discharge cold air is also rotated by the parallel link mechanism 465.

A slot 467 is provided in the container holder 460, and a pin 469 extending from the ventilation plate 457 can be inserted into the slot 467.

According to the above configuration, the holder functions as follows.

The user holds the handle 461 of the container holder 460 and rotates the handle 461 of the holder. User means extraction. As the container holder 460 rotates about the support axis 466 of the holder, the pin 469 moves along the slot 467. Since the pin 469 is integrally provided with the vent plate 457, the vent plate 457 rotates about the vent plate support axis 468. Turning one vent plate 457 rotates all vent plates 457 connected by a parallel linkage 465.

Because the rotation of the container holder 460 and the rotation of the vent plate 457 are interrelated, when the vent plate 457 is tilted, the slope of the vent plate 457 can be directed towards accommodating the storage container 498 in the container holder 460. That is, the inclination may be directed toward the placement of the container holding portion 462.

Thus, the vent plate 457 can be directed towards the storage container 498 so that cool air enters the storage container 498. Thus, the storage container held in the container holder 460 can be quickly cooled since cold air is blown directly onto it.

In the case of having multiple directions of inertia and vibration, as in a vehicle, cooling can be performed in a state where the position of the storage container is supported by the support of the container holder 460.

Based on the above, the rotation of the container holder 460 and the rotation of the ventilation plate 467 are interrelated. However, the size and angle of each component shown in FIG. 21 may vary according to the size and rotation angle of the container, and the drawings are given as examples only.

Rapid cooling at a particular position within the cavity is not limited to the above example. 22 and 23 are views illustrating another example of a cold air exhaust vent plate.

22 and 23, at the outlet end of the cold air exhaust guide 456, a guide mechanism 470 having a predetermined space is provided, and a slider 475 guided by the guide mechanism 470 can be provided. which is directed towards the front of the cavity, and an inclined ventilation plate 472 which is inclined in a certain direction. The inclined ventilation plates 472 can be directed towards the driver. For example, they may be directed toward the posterior right side of the cavity.

As the slider 475 moves, uniform cooling of the cavity can be performed by aligning the vertical ventilation plate 470 with the outlet end of the cold air outlet guide 465, as illustrated in FIG. In this case, cold air can be discharged in the vertical direction, i.e. in front of the cavity, due to the vertical ventilation plate 470.

On the other hand, rapid cooling of the cavity can be performed by aligning the inclined ventilation plate 472 with the outlet end of the cold air outlet guide 465, as illustrated in FIG. In this case, cold air can be discharged at an angle, i.e. to the back of the cavity, due to the inclined ventilation plate 472. In this case, a particular storage container can be quickly cooled.

The above configuration has two modes: a uniform cooling mode when a plurality of storage containers, such as a plurality of passengers, needs to be cooled, and a fast cooling mode when a plurality of storage containers, such as a driver only, needs to be cooled.

Next, the structure and function of the vacuum adiabatic body 101 will be described in more detail.

24 is a view illustrating the internal configuration of a vacuum adiabatic body according to various embodiments.

First of all, as shown in FIG. 24a, the vacuum space portion 50 is provided in a third space having a pressure different from the first and second spaces, preferably in a vacuum state, resulting in a reduction in adiabatic loss. The third space may have a temperature that is between the temperature of the first space and the temperature of the second space. A component that prevents heat transfer between the first space and the second space may be referred to as a heat resistant assembly. Further, various configurations can be applied together or separately. In a narrow sense, a component that impedes heat transfer between plate elements may be referred to as a heat resistant assembly.

The third space is provided as a space in a vacuum state. Thus, the first and second plate elements 10 and 20 are subjected to a force that compresses them in the direction of approach to each other due to the force corresponding to the pressure difference between the first and second spaces. Therefore, the vacuum space portion 50 may be deformed in the direction of its reduction. In this case, adiabatic losses may occur due to the increase in thermal radiation due to the compression of the part 50 with the vacuum space, and the increase in heat transfer due to the contact between the plate elements 10 and 20.

To reduce deformation of the vacuum space portion 50, a support assembly 30 may be provided. second plate elements 10 and 20. At least one end of the rod 31 may be provided with a base plate 35. The base plate 35 connects at least two rods 31 to each other and may extend in a horizontal direction relative to the first and second plate elements 10 and 20 .

The support plate 35 may be in the form of a plate, or may be provided in the form of a grid, so that the area of contact with the first or second plate member 10 or 20 is reduced, resulting in reduced heat transfer. The rods 31 and the base plate 35 are connected to each other at at least one insertion site between the first and second plate elements 10 and 20. The base plate 35 contacts at least one of the first and second plate elements 10 and 20, which prevents deformation of the first and second plate members 10 and 20. In addition, based on the extension direction of the bars 31, the total cross-sectional area of the base plate 35 can be larger than the cross-sectional area of the bars 31, so that the heat transferred through the bars 31 can be dissipated through the base plate. 35.

The material of the support assembly 30 may include a polymer selected from the group consisting of polycarbonate (PC), fiberglass-based polycarbonate, low outgassing polycarbonate, polyphenylene sulfide (PPS), and liquid crystal polymer (LCP) to provide high compressive strength, low outgassing and water absorption, low thermal conductivity, high compressive strength at high temperature and excellent machinability.

Next, the radiation preventing sheet 32 for reducing heat radiation between the first and second plate members 10 and 20 through the vacuum space portion 50 will be described. The first and second plate elements 10 and 20 may be made of stainless material to prevent corrosion and provide sufficient strength. The stainless material has a relatively high emissivity of 0.16, and therefore can transmit a large amount of radiant heat. In addition, the support assembly 30 made of resin has a lower emissivity than the plate members and does not completely cover the inner surfaces of the first and second plate members 10 and 20. Therefore, the support assembly 30 does not have much effect on the radiation heat. Therefore, the radiation inhibiting sheet 32 may be formed into a plate over most of the area of the vacuum space portion 50 to help reduce the radiation heat transferred between the first and second plate members 10 and 20.

As the material of the radiation-blocking sheet 32, a product having a low emissivity can preferably be used. In an embodiment, aluminum foil having an emissivity of 0.02 may be used as the radiation-blocking sheet 32. In addition, at least one sheet can be provided at a certain distance from the radiation-obstructing sheet 32 without the possibility of contact with it. At least one radiation barrier sheet may be provided at a position where it contacts the inner surface of the first or second plate member 10 or 20. When the vacuum space portion 50 has a low height, one sheet of the radiation barrier sheet may be provided. In the case of a refrigerator 7 for a vehicle, one sheet of a radiation-impeding sheet may be provided to reduce the thickness of the vacuum adiabatic case 101 and increase the internal volume of the cavity 100.

24b, the distance between the plate elements is maintained by the support assembly 30, and the vacuum space portion 50 can be filled with a porous material 33. The porous material 33 may have a higher emissivity than the stainless material of the first and second plate elements 10 and 20. However, Since the vacuum space portion 50 is filled with a porous material 33, the porous material 33 has a high efficiency in preventing radiation heat transfer.

In this embodiment, the vacuum adiabatic housing can be made without the use of a radiation-impeding sheet 32.

24c, the support assembly 30 supporting the vacuum space portion 50 is not provided. Instead of the support assembly 30, a porous material 33 surrounded by a film 34 may be provided. In this case, the porous material 33 may be provided in a compressed state to maintain a gap within the vacuum space portion 50. The film 34 is made of polyethylene, for example, and may be provided with holes.

In this embodiment, the vacuum adiabatic housing can be made without the use of support assembly 30. In other words, porous material 33 can simultaneously serve as a radiation-impeding sheet 32 and support assembly 30.

25 is a view of the heat transfer inhibiting sheet and a peripheral portion of the heat transfer inhibiting sheet.

According to Fig.25a, the first and second plate elements 10 and 20 must be sealed to maintain a vacuum inside the vacuum adiabatic housing. In this case, since the two plate members have temperatures different from each other, heat transfer can occur between the two plate members. A heat transfer inhibiting sheet 60 may be provided to prevent heat transfer between two different kinds of plate members.

The heat transfer inhibition sheet 60 may be provided with sealing portions 61 on which both ends of the heat transfer inhibition sheet 60 are sealed to form at least one wall portion of the third space and maintain a vacuum state. The heat transfer inhibiting sheet 60 may be in the form of a thin foil, on the order of a few micrometers, to reduce the amount of heat transferred along the wall of the third space. The sealing parts 61 may be in the form of welded parts. That is, the heat transfer inhibiting sheet 60 and the plate members 10 and 20 can be welded to each other. For welding of the heat transfer inhibiting sheet 60 and the plate members 10 and 20, the heat inhibition sheet 60 and the plate members 10 and 20 may be made of the same material, and a stainless material may be used as such material. The sealing parts 61 are not limited to the welded parts, and can be obtained by a process such as embossing. The heat transfer inhibiting sheet 60 may have a curved shape. Thus, the heat transfer distance along the heat transfer inhibiting sheet 60 can be larger than the linear distance of each plate member, so that heat transfer can be further reduced.

A change in temperature occurs along the heat transfer inhibiting sheet 60 . Therefore, in order to prevent heat transfer to the outside of the heat transfer inhibition sheet 60, a protective portion 62 can be provided on the outside of the heat transmission inhibition sheet 60, which serves as a heat insulator. In other words, in the vehicle refrigerator 7, the second plate member 20 has a high temperature and the first plate member 10 has a low temperature. In addition, in the heat transfer inhibition sheet 60, a transition from high temperature to low temperature occurs, and therefore the temperature of the heat transfer inhibition sheet 60 changes abruptly. Therefore, when the heat transfer inhibiting sheet 60 is opened, significant heat transfer can occur through the open area.

To reduce heat loss outside the heat transfer inhibition sheet 60, a protective portion 62 is provided. .

The protective portion 62 may be formed as a porous material in contact with the outer surface of the heat transfer inhibiting sheet 60, may be in the form of an adiabatic structure, such as a separate gasket, which is located outside the heat transfer inhibiting sheet 60, or may be in the form of a console cover 300 facing the heat transfer inhibiting sheet 60.

Next, the heat transfer path between the first and second plate members 10 and 20 will be described. sheet 60, heat conduction transfer of the support ② that is transferred through the support assembly 30 provided inside the vacuum adiabatic case, heat transfer of the gas heat conduction ③ that is transferred through the internal gas to the vacuum space part, and heat transfer ④ due to the radiation that is transmitted through the part with the vacuum space.

The heat transfer may vary depending on the different design dimensions. For example, the support assembly can be changed so that the first and second plate members 10 and 20 can withstand vacuum pressure without deformation, the vacuum pressure can be changed, the distance between the plate members can be changed, and the length of the heat transfer inhibiting sheet can be changed. The heat transfer may vary depending on the temperature difference between the spaces (first and second spaces) respectively formed by the plate elements. In an embodiment, the preferred configuration of the vacuum adiabatic vessel is determined on the basis that the overall heat transfer is less than that of a typical polyurethane foamed adiabatic design. In a conventional refrigerator including an adiabatic structure formed by foaming polyurethane, the effective heat transfer coefficient may be about 19.6 mW/m·K.

By performing a relative analysis of the heat conduction values of the vacuum adiabatic body according to the embodiment, the heat transfer amount by the heat ③ transferred by the heat conduction of the gas can be minimized. For example, the heat transfer amount by gas conduction heat ③ can be adjusted to a value equal to or less than 4% of the total heat transfer amount. The amount of heat transfer by conduction heat transfer of a solid, defined as the sum of surface conduction heat ① and support conduction heat ②, is the largest. For example, the amount of heat transfer by means of heat transferred by thermal conduction of a solid can be up to 75% of the total amount of heat transfer. The heat transfer amount by radiative heat transfer ④ is smaller than the heat transfer amount by conduction heat transfer of a solid body, but larger than the heat transfer amount by gas conduction heat transfer ③. For example, the heat transfer amount by radiative heat ④ may be about 20% of the total heat transfer amount.

According to this heat transfer distribution, the effective heat transfer coefficients (eK: effective K) (W/m K) of heat ① transferred by surface conduction, heat ② transferred by heat conduction of the support, heat ③ transferred by gas conduction, and heat ④ transferred by radiation can have a mathematical representation of 1.

Mathematical representation 1

eK heat transferred by thermal conduction of a solid > eK heat transferred by radiation > eK heat transferred by thermal conduction of a gas

Here, the effective heat transfer coefficient (eK) is a value that can be determined 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 total amount of heat transfer and the temperature of at least one area where heat is transferred. For example, the calorific value (W) is measured using a heat source that can be quantified in a refrigerator, the door temperature distribution (K) is measured using heat respectively transmitted through the main body and door edge of the refrigerator, and the heat transfer path is calculated as the value (m) conversion, thus an effective heat transfer coefficient can be obtained.

The effective heat transfer coefficient (eK) of the entire vacuum adiabatic vessel has a value given by the formula k=QL/A△T. Here, Q stands for heating value (W) and can be obtained using the heating value of the heater. A indicates the cross-sectional area (m2) of the vacuum adiabatic vessel, L indicates the thickness (m) of the vacuum adiabatic vessel, and △T indicates the temperature difference.

For heat transferred by surface conduction, the calorific value can be obtained based on the temperature difference (△T) between the inlet and outlet of the heat inhibition sheet 60 or 63, the cross-sectional area (A) of the heat inhibition sheet, the length (L) of the heat inhibition sheet and a thermal conductivity (k) of the heat transfer inhibiting sheet (the thermal conductivity of the heat inhibiting sheet is a material property and can be determined in advance). For heat transferred by thermal conduction of the support, the calorific value can be obtained based on the temperature difference (△T) between the inlet and outlet of the support assembly 30, the cross-sectional area (A) of the support assembly, the length (L) of the support assembly, and the thermal conductivity (k) base node. Here, the thermal conductivity of the reference node is a property of the material and can be determined in advance. The sum of heat transfer ③ by gas conduction and heat transfer ④ by radiation can be obtained by subtracting heat transfer by surface conduction and heat transfer by heat conduction of the support from the heat transfer value of the entire vacuum adiabatic body. The ratio of heat transferred by thermal conduction of gas ③ and heat transferred by radiation ④ can be obtained by determining the heat transferred by radiation, in the absence of heat transferred by thermal conduction of gas, due to a significant reduction in the vacuumization degree of part 50 with vacuum space.

When a porous material is provided inside the vacuum space portion 50, the thermal conduction heat ⑤ of the porous material may be the sum of the support conduction heat ② and the radiation heat ④. The heat ⑤ transferred by thermal conduction of the porous material may vary depending on various variables, including the kind, amount of porous material, and the like.

In the second plate element, the temperature difference between the average temperature of the second plate element and the temperature at the point where the heat transfer path through the heat transfer preventing sheet 60 reaches the second plate element 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 transfer path through the heat transfer inhibiting sheet reaches the second plate member is the lowest. Similarly, when the second space is a colder region than the first space, the temperature at the point where the heat transfer path through the heat transfer inhibiting sheet reaches the second plate member is the highest.

This means that the amount of heat transferred through other points, with the exception of the heat transferred by the thermal conductivity of the surface passing through the heat transfer inhibiting sheet, must be controlled, and the total amount of heat transfer corresponding to the vacuum adiabatic housing can only be achieved when the heat transferred due to the thermal conductivity of the surface, provides the greatest amount of heat transfer. To this end, the change in temperature of the heat transfer inhibiting sheet can be controlled so as to exceed the change in temperature of the plate element.

Next, the physical characteristics of the components forming the vacuum adiabatic case will be described. In a vacuum adiabatic housing, vacuum pressure acts on all components. In this regard, a material having a strength (N/m2) of a certain level can be used.

Referring to Fig. 25b, this configuration is similar to that shown in Fig. 24a, except for the portions where the first plate member 10 and the second plate member 20 are connected to the heat transfer inhibiting sheet 60. Thus, the description of the same components is omitted, and only the differences of the components are described in detail. .

The ends of the plate elements 10 and 20 can be bent towards the second high temperature space to form a flange part 65. A welded part 61 can be located on the upper surface of the flange part 65 to connect the heat transfer inhibiting sheet 60 to the flange part 65. In this embodiment, worker can only weld on one side. Thus, by not having to perform two operations, the process can be simplified.

This is more preferable in the case where welding inside and outside is difficult, as illustrated in FIG. 25a, due to the narrow space in the vacuum space portion 50, for example, in the refrigerator 7 for a vehicle.

Fig.26 is a graph illustrating the results obtained by monitoring the time and pressure in the process of evacuating the interior of the vacuum adiabatic body when using the reference node.

As shown in FIG. 26, in order to ensure the vacuum state of the vacuum space portion 50, the gas from the vacuum space portion 50 is pumped out by a vacuum pump while evaporating the latent gas remaining in the regions of the vacuum space portion 50 by heating. However, if the vacuum pressure reaches or exceeds a certain level, there is a point where the vacuum pressure level no longer increases (△t1). Thereafter, the getter is activated by detaching the vacuum space portion 50 from the vacuum pump and supplying heat to the vacuum space portion 50 (△t2). If the getter is activated, the pressure in the vacuum space portion 50 decreases for a certain period of time, but then normalizes to maintain the vacuum pressure at a certain level. The vacuum pressure maintained at a certain level after the getter is activated is approximately 1.8×10-6 Torr.

In an embodiment, the point at which the vacuum pressure is substantially no longer reduced, even when pumping out gas by driving the vacuum pump, is set as the lower limit of the vacuum pressure used in the vacuum adiabatic case, so that the minimum internal pressure of the part 50 with the vacuum space is 1.8×10-6 torr.

Fig.27 is a graph obtained by comparing the pressure of the vacuum and the thermal conductivity of the gas.

27, the thermal conductivity of the gas relative to vacuum pressures versus gap dimensions in the vacuum space portion 50 is plotted as effective heat transfer coefficients (eK). The effective heat transfer coefficients (eK) are determined for three gap sizes in the vacuum space portion 50, namely 2.76 mm, 6.5 mm and 12.5 mm. The clearance in the vacuum space portion 50 is defined as follows. When the radiation barrier sheet 32 is provided in the vacuum space portion 50, the gap is the distance between the radiation barrier sheet 32 and the plate member adjacent thereto. In the absence of the radiation-impeding sheet 32 in the vacuum space portion 50, the gap is the distance between the first and second plate members.

It can be seen that since the size of the gap at the point corresponding to the typical effective heat transfer coefficient of 0.0196 W/m K, which is provided by the adiabatic material formed by foaming the polyurethane, is small, the vacuum pressure is 2.65×10-1 Torr even when the size the gap is 2.76 mm. Here, it can be seen that the point at which the decrease in the adiabatic effect due to the heat transferred by thermal conduction of the gas is neutralized even if the vacuum pressure is reduced is the point at which the vacuum pressure is approximately 4.5 x 10-3 Torr. A vacuum pressure of 4.5×10-3 Torr can be defined as the point at which the decrease in the adiabatic effect due to the heat transferred due to the thermal conductivity of the gas is neutralized. In addition, when the effective heat transfer coefficient is 0.1 W/m·K, the vacuum pressure is 1.2×10 −2 Torr.

When the vacuum space portion 50 is not provided with a support assembly but is provided with a porous material, the size of the gap ranges from a few micrometers to several hundreds of micrometers. In this case, the amount of heat transfer due to radiation is small due to the porous material even when the vacuum pressure is relatively high, i. e. when the degree of vacuum is low. Therefore, an appropriate vacuum pump is used to regulate the vacuum pressure. The vacuum pressure suitable for a suitable vacuum pump is approximately 2.0 x 10-4 torr. In addition, the vacuum pressure at the point where the decrease in the adiabatic effect due to the heat transferred due to the thermal conduction of the gas is neutralized is approximately 4.7 × 10 -2 Torr. In addition, the pressure at which the reduction in adiabatic effect due to heat transferred by thermal conduction of the gas reaches a typical effective heat transfer coefficient of 0.0196 W/m·K is 730 Torr.

When the support assembly and the porous material are simultaneously provided in the vacuum space portion, a vacuum pressure that is an average between the vacuum pressure when using only the support assembly and the vacuum pressure when using only the porous material can be provided.

Next, another embodiment will be described.

In the above-described embodiment, a refrigerator mounted on a vehicle is generally described. However, the embodiment of the present invention is not limited to this. For example, the intent of the present invention can be applied to a heating device and a refrigeration or heating device. Of course, the embodiment of the present invention is not limited to a vehicle, and can be applied to any device that provides the desired product temperature. However, it is most preferred in the case of a refrigerator for a vehicle.

In particular, in the case of a heating device, the direction of the refrigerant may be opposite to the direction of the refrigerant in the refrigerator. In the case of a refrigeration or heating device, four walls may be provided in the flow path of the refrigerant, which change the direction of the refrigerant depending on whether the refrigerant is operating as a refrigerant of a refrigerator or a heating device.

The condensation module may be referred to as the first heat exchange module, and the evaporator module may be referred to as the second heat exchange module, regardless of switching between the refrigerator and the heating device. Here, the expressions "first" and "second" mean the separation of the heat exchange module and are interchangeable.

Industrial Applicability

According to the embodiments, a refrigerator for a vehicle that is externally powered and is an independent device can be efficiently implemented.

Claims (104)

1. Vacuum adiabatic housing, containing: a first plate having a first temperature, the first plate forming a cavity; a second plate having a second temperature different from the first temperature; a seal that seals the first plate and the second plate to provide a third space between the first plate and the second plate, which has a third temperature between the first temperature and the second temperature, and which is in a vacuum state; a support that supports the first and second plates and is provided in the third space; a heat insulating material that reduces heat transfer between the first plate and the second plate; a vacuum opening through which gas is released from the third space; and a heat exchange module, which is placed in the cavity, and the heat exchange module includes a heat exchanger and a fan configured to circulate air through the heat exchanger and the cavity. 2. The vacuum adiabatic vessel according to claim 1, wherein the heat exchanger is an evaporator and the heat exchange module further comprises a first compartment in which a fan and an evaporator are provided. 3. Vacuum adiabatic housing according to claim 2, in which the heat exchange module contains a second compartment, which is separated from the first compartment and is configured to accommodate a temperature sensor. 4. Vacuum adiabatic housing according to claim 3, further comprising a third compartment, which is separated from the first compartment and the second compartment and is configured to receive a lamp, and the third compartment is provided between the first compartment and the second compartment. 5. Vacuum adiabatic housing according to claim 3, wherein the second compartment is provided on the first side of the first compartment, and the conduit passage through which the refrigerant pipeline passes is provided on the second side opposite the first side. 6. The vacuum adiabatic casing of claim 2, wherein the fan includes a centrifugal fan and draws air from the back of the evaporator to discharge air downward into the cavity. 7. Vacuum adiabatic housing according to claim 3, wherein the second compartment is provided at the top of the first side of the heat exchange module. 8. Vacuum adiabatic housing according to claim 1, in which the heat exchange module is in contact with the cavity. 9. Vacuum adiabatic housing according to claim 1, in which the heat exchange module is located in the rear side of the cavity. 10. A device having a cooling and heating function and containing a vacuum adiabatic housing according to claim 1, while the device further comprises: an engine room provided on the first side of the cavity; the lower frame of the refrigerator, on which the cavity and the engine room are installed; a compressor provided in the engine room and configured to compress the refrigerant; the first heat exchange module provided in the engine room and configured to provide heat exchange of the refrigerant; a second heat exchange module located in the cavity and corresponding to at least one side wall of the cavity for providing heat exchange of the refrigerant; and a temperature sensor provided in the second heat exchange module and configured to measure the temperature of the cavity. 11. The apparatus of claim 10, wherein the second heat exchange module comprises a first compartment provided on the underside of the second heat exchange module and including an evaporator and a Sirocco fan provided above the evaporator. 12. The device according to claim 10, further comprising: a pipeline that connects the first heat exchange module to the second heat exchange module and through which the refrigerant flows, moreover, the first heat exchange module is located on the inner surface of the cavity, at least one side surface and the rear surface of the first heat exchange module are thermally insulated by the third space, which is in a vacuum state, and the upper surface of the first heat exchange module is thermally insulated by a separate adiabatic element. 13. The apparatus of claim 12, further comprising a lid that defines the interior of the first heat exchange module, the lid including: back cover and a front cover connected to the back cover and having a cold air intake hole at its lower portion and a cold air outlet hole at the center of the front cover. 14. The apparatus of claim 13, wherein the cold air outlet is provided at a position between one second of the height and two thirds of the height from the bottom of the cavity. 15. The device according to claim 13, further comprising: a fan provided in the interior of the first heat exchange module; and a ventilation plate supported by a cover and configured to direct the flow of cold air discharged from the fan. 16. The apparatus of claim 15, further including a container holder attached to the lid and rotatable, the orientation of the vent plate being adjusted as the container holder is rotated. 17. The apparatus of claim 15, wherein the vent plate includes a first plurality of vanes, each of the first plurality of vanes being perpendicular to a front surface of the front cover; and a second plurality of blades, each of the second plurality of blades being inclined at an angle of less than 90° relative to the front surface of the front cover. 18. Vacuum adiabatic housing, containing: a first plate having a first temperature, the first plate forming a cavity; a second plate having a second temperature different from the first temperature; a seal that seals the first plate and the second plate to provide a third space between the first plate and the second plate, which has a third temperature between the first temperature and the second temperature, and which is in a vacuum state; a support that supports the first and second plates and is provided in the third space; and heat exchange module while the rear surface and the front surface of the heat exchange module are thermally insulated by the third space, which is in a vacuum state, and the upper part of the heat exchange module is thermally insulated by the second adiabatic element. 19. Vacuum adiabatic housing according to claim 18, in which the second adiabatic element is fixed relative to the cavity. 20. Vacuum adiabatic housing, containing: a first plate having a first temperature, the first plate forming a cavity; a second plate having a second temperature different from the first temperature; a seal that seals the first plate and the second plate to provide a third space between the first plate and the second plate, which has a third temperature between the first temperature and the second temperature, and which is in a vacuum state; a support that supports the first and second plates and is provided in the third space; and heat exchange module wherein the heat exchange module includes an evaporator, a compartment in which the evaporator fan is placed, and another compartment that is separated from said compartment for accommodating a temperature sensor. 21. Vacuum adiabatic housing, containing: a first plate forming a cavity; second plate; a vacuum space portion provided between the first plate and the second plate; a heat exchange module located in the cavity, and a cover that forms the interior of the heat exchange module, while the lid contains: back cover and a front cover connected to the back cover and containing a cold air intake hole in its lower part and a cold air outlet hole in the central part of the front cover. 22. Vacuum adiabatic housing according to claim 21, in which the cold air outlet is located at a distance between one second of the height and two thirds of the height from the bottom of the cavity and/or in which the cold air outlet is located at the center in the transverse direction of the cold air outlet which is supplied from the lower side in the forward direction. 23. Vacuum adiabatic housing, containing: a first plate forming a cavity; second plate; a vacuum space portion provided between the first plate and the second plate; a heat exchange module located in the cavity, and a cover that forms the interior of the heat exchange module, while the lid contains: cold air outlet a ventilation plate located in the cold air outlet, and a container holder for holding the storage container rotatably held relative to the lid at the periphery of the cold air outlet, wherein the movement orientation of the ventilation plate associated with the container holder is adjusted by rotation of the container holder holding the storage container. 24. Vacuum adiabatic housing, containing: a first plate forming a cavity; second plate; a vacuum space portion provided between the first plate and the second plate; a heat exchange module located in the cavity; and a cover that forms the interior of the heat exchange module, while the lid contains: cold air outlet a guide mechanism having a predetermined space and provided at the outlet end of the cold air outlet, and a slider guided by a guide mechanism, the slider including a vertical ventilation plate that is directed towards the front of the cavity and an inclined ventilation plate that is inclined in a certain direction of the cavity. 25. Vacuum adiabatic housing, containing: a first plate forming a cavity; second plate; a vacuum space portion provided between the first plate and the second plate; and heat exchange module located in the cavity, wherein the heat exchange module comprises a first compartment in which an evaporator is provided and a second compartment that is separated from the first compartment and configured to accommodate a temperature sensor. 26. Vacuum adiabatic housing according to claim 25, further comprising a third compartment, which is separated from the first compartment and the second compartment and is configured to accommodate a lamp, wherein a third compartment is provided between the first compartment and the second compartment. 27. Vacuum adiabatic housing, containing: a first plate forming a cavity; second plate; a vacuum space portion provided between the first plate and the second plate; the first heat exchange module provided outside the cavity and configured to provide heat exchange of the refrigerant; and a second heat exchange module placed in the cavity and corresponding to at least one side wall of the cavity to provide heat exchange of the refrigerant. 28. Vacuum adiabatic housing, containing: a first plate forming a cavity; second plate; a vacuum space portion provided between the first plate and the second plate; and a heat exchange module that contacts the interior surface of the cavity, the heat exchange module comprising a heat exchanger.

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