RU2775367C2 - Device with cooling and heating function and vehicle - Google Patents

Abstract

FIELD: car industry.

SUBSTANCE: invention relates to devices for heating and cooling a vehicle. The device includes a cavity, at least a section of a wall of which is provided in the form of a vacuum adiabatic case, an engine room located from side and outside of the cavity, a compressor located in the engine room for compressing a refrigerant, the first heat exchange module located in the engine room for providing heat exchange of the refrigerant, the second heat exchange module located in the cavity for providing heat exchange of the refrigerant, and a cover of the engine room, which closes the engine room to separate a flow path, so that an inner airflow and an outer airflow have directions opposite to each other.

EFFECT: increase in the volume of refrigerator, and increase in the energy efficiency.

45 cl, 22 dwg

Description

The field of technology to which the invention belongs

The present invention relates to a refrigeration or heating device and a vehicle.

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.

In addition, there is an example 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.

In this example, because the structure forming 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.

The essence of the invention

Technical problem

Embodiments provide a refrigeration or heating device, to which the driver has direct access during the use of the refrigeration cycle, and the vehicle.

Embodiments also provide a refrigeration or heating device that is configured to expand the volume of the refrigerator, and a vehicle.

Embodiments provide a refrigeration or heating device that is configured to improve energy efficiency and a vehicle.

Technical solution

In one embodiment, to provide direct access to the driver when using the refrigeration cycle, the refrigeration or heating device includes: a cavity, at least a portion of the wall of which is provided in the form of a vacuum adiabatic housing; engine room located on the side and outside of the cavity; a compressor located in the engine room for compressing the refrigerant; the first heat exchange module located in the engine room to provide heat exchange of the refrigerant; and a second heat exchange module disposed in the cavity for heat exchange of the refrigerant.

In order to increase the volume of the refrigerator and realize a high degree of integration of the engine room, the refrigeration or heating device may further include an engine room cover that closes the engine room to separate the flow path so that the internal airflow and the external airflow have opposite directions to each other.

To improve energy efficiency and heat dissipation efficiency, the refrigeration or heating device may further include a flow guide for directing air from the outlet side of the internal air flow in a direction opposite to the cavity.

The refrigeration or heating apparatus may further include a connection passage further provided at the outlet end of the flow guide to prevent hot air from being recirculated, further improving heat dissipation efficiency.

Air from the inlet side of the external airflow can enter the cavity to further prevent hot air recirculation.

In order to improve energy efficiency and realize a high degree of integration of the engine room, the width of the external air flow can be gradually reduced as the air flow advances.

To ensure sufficient efficiency of heat dissipation, the cover of the engine room may have at least two stepped parts. A controller can be installed on the stepped part.

In order to increase the degree of integration, a compressor control circuit and a refrigeration or heating device control circuit may be provided in the controller.

In another embodiment, in order to provide a vehicle on which a refrigeration or heating device having a fast temperature adjustment function is installed, the vehicle includes: a console; a suction port and an exhaust port, which are provided on the left and right sides of the console; cavity and engine room, which are horizontally spaced in the interior of the console; a compressor and a first heat exchange module, which are provided in the engine room; and a second heat exchange module located in the cavity.

In order to ensure sufficient volume of the refrigerator and realize a high degree of integration, the external air flow outside the engine room cover covering the engine room and the internal air flow inside the engine room cover may have opposite directions to each other.

In order to improve energy efficiency and ensure sufficient heat dissipation efficiency, the vehicle may further include a flow guide provided in the bottom frame of the refrigerator to direct the flow of air discharged outside the engine room to the outlet.

In order to prevent recirculation of air exhausted from the flow guide, the vehicle may further include a connecting passage between the inlet end of the outlet port and the outlet end of the flow guide. The vehicle may further include a barrier wall sealing the gap between the lower portion of the interior of the console and the outlet end of the flow guide.

To improve energy efficiency and ensure sufficient heat dissipation efficiency, the flow guide can be vertically aligned with the compressor.

In another embodiment, in order to reliably control the refrigeration or heating device, the refrigeration or heating device includes: a cavity and an engine room that are horizontally aligned with each other; compressor located in the engine room; and an engine room cover that closes the engine room to separate the flow path and outside of which the controller is located.

To realize a highly integrated refrigeration or heating device, the controller may include a compressor control circuit for controlling the compressor.

To ensure the efficiency of controller cooling, air heated during controller cooling can be supplied to the engine room.

In order to achieve a high degree of integration of the engine room and the refrigeration or heating device, along with the efficiency of heat removal, the air passing through the controller and the air passing through the engine room may have opposite directions to each other.

Useful effects of the invention

A refrigeration or heating device may be provided, including: a cavity, at least a wall section of which is provided in the form of a vacuum adiabatic housing; engine room located on the side and outside of the cavity; a compressor located in the engine room for compressing the refrigerant; the first heat exchange module located in the engine room to provide heat exchange of the refrigerant; and a second heat exchange module located in the refrigerant heat exchange cavity, wherein a refrigeration or heating device may be located near the driver.

The refrigeration or heating device further includes an engine room cover that closes the engine room to separate the flow path so that the internal airflow and the external airflow have opposite directions to each other. In this way, the air flow in the engine room can be accurately divided to reduce the engine room, which allows the volume of the cavity to be increased.

A flow guide may be provided to direct air from the outlet side of the internal air flow in a direction opposite to the cavity. Thus, hot air does not enter the cavity, which reduces the thermal load.

Since the width of the air stream decreases as the external air stream advances, sufficient space can be provided for cooling each of the components provided inside and outside the engine room and for dissipating heat from the components.

The controller may be installed on the stepped portion of the engine room cover, and a compressor control circuit for controlling the compressor and a refrigeration or heating device control circuit may be provided in the controller to further improve the degree of integration of the refrigeration or heating device and improve the operation reliability of the refrigeration or heating device.

A vehicle may be provided, including: a console; a suction port and an exhaust port, which are provided on the left and right sides of the console; cavity and engine room, which are horizontally spaced in the interior of the console; a compressor and a first heat exchange module, which are provided in the engine room; and a second heat exchange module located in the cavity. Thus, the user of the vehicle can quickly place the products at the desired temperature conditions.

The external air flow outside the engine room cover covering the engine room and the internal air flow inside the engine room cover may have opposite directions to each other. Thus, the refrigeration cycle can be placed in a narrow space.

The flow guide for directing the flow of air discharged to the outside of the engine room towards the outlet can prevent high temperature air from affecting the cavity.

The flow guide can be vertically aligned with the compressor to quickly exhaust air and realize a high degree of engine room integration.

A refrigeration or heating device may be provided, including: a cavity and an engine room that are horizontally aligned with each other; compressor located in the engine room; and an engine room cover that closes the engine room to separate the flow path and outside of which the controller is located. Thus, the controller can be prevented from being damaged in a narrow space to control the refrigeration or heating device stably.

A compressor control circuit for controlling the compressor may be provided in the controller to further reduce the interior space of the engine room.

The air passing through the controller can be supplied to the engine room to meet the conditions of heat dissipation from the controller.

Since the air passing through the controller and the air passing through the engine room have opposite directions, the inside and outside of the narrow engine room can be properly used to perform cooling.

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 for explaining the air flow outside the engine room of the vehicle refrigerator.

Fig. 5 is a bottom perspective view of the engine room cover.

Fig. 6 is a view illustrating the interior of the engine room with the engine room cover partially removed.

Fig. 7 is a front perspective view of the engine room cover.

Fig. 8 is a perspective view of the controller.

Fig. 9 is an exploded perspective view of the controller.

Fig. 10 is a diagram of a control board.

Fig. 11 is a block diagram for explaining the control of a refrigerator for a vehicle.

12 is a front view of a refrigerator for a vehicle.

13 is a left side view of a refrigerator for a vehicle.

14-18 are illustrations of simulation results to explain various flow guide designs.

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

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

Fig. 21 is a graph illustrating the results obtained by observing the time and pressure during evacuation of the interior of the vacuum adiabatic body using the reference assembly.

Fig.22 is a graph obtained by comparing vacuum pressure and gas thermal conductivity.

The 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 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 may be rigidly attached to 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.

Specifically, air enters (first flow) into the space between engine room cover 700 and console cover 300, and then enters (second flow) into engine room cover 700. In addition, the first flow and the second flow have opposite directions. Thus, the cooling efficiency in a narrow space can be maximized.

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 at the above-described location, the vehicle refrigerator 7 can operate smoothly in a proper temperature range in a narrow space inside 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 cover not only 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 mounted on the console cover 300 to allow a user to close an opening through which products can be removed from the cavity 100.

The door 800 may 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 allow the user to conveniently operate the door 800 because 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 rear 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 housing 101. Each of the surfaces of cavity 100 may be thermally insulated by a separate vacuum adiabatic housing or at least one or more vacuum adiabatic housings connected to each other. The cavity 100 may be provided by the vacuum adiabatic housing 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 housing 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.

A detailed description of the vacuum adiabatic housing 101 will be given later.

In the cavity 100, provided in the form of a vacuum adiabatic case 101, an evaporative module 400 can be installed. The evaporative module 400 can force the evaporation heat of the refrigerant that enters the cavity 100 through the refrigerant conduit 600 into the cavity 100. The evaporative module can be located at the rear sides in cavity 100.

Fig. 4 is a view for explaining the air flow outside the engine room of the vehicle refrigerator.

4, 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 inner 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 shape.

Specifically, in the rearward direction from the front surface, the first stepped portion 732, the second stepped portion 733, and the third stepped portion 735 may be provided sequentially. On the second stepped portion 733, a controller accommodating portion 734 having the same height as the third stepped portion is provided. According to this configuration, the controller 900 can be placed in parallel with the third step 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 along the flow path. Although the air may be slightly warm during controller cooling, the degree of temperature increase is negligible.

The air moving towards the rear side of the engine room cover 700 turns downward. A large open suction port can be provided in the rear surface of the engine room cover 700 (see reference numeral 751 in FIG. 5). 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 .

Next, the flow in the engine room 200 will be described with reference to the bottom perspective view of the engine room cover shown in FIG. 5 and the engine room view with the engine room cover partially removed shown in FIG.

4-6, in the rear surface 750 of the cover 700 of the engine room, a suction port 751 in the cover is provided. Air is sucked forward from the rear of the engine room through suction port 751 in the cover.

The air entering through the suction port 751 in the cover passes through the condensing unit 500 to carry out the condensation of the refrigerant, which causes it to heat up. In this way, heat exchange takes place between the dryer and the expansion valve. The refrigerant then cools the compressor 201 and is discharged through the underside of the engine room 200.

The refrigerant discharged from the engine room 200 moves to the left through an opening formed in the engine room bottom frame 210 provided under the compressor and the flow guide 81 of the bottom frame 8 of the refrigerator. The flow guide 81 is aligned with the console outlet 6 and the heated air is discharged towards the passenger side. In order to prevent discomfort to the passenger, the outlet grille 6 is provided with downward inclination, and hot air can be discharged under the passenger's seat.

The air flow will be re-described with reference to the flow direction.

First of all, air is usually drawn in from the driver's side and exhausted from the passenger's side, i.e. in the direction to the left.

In particular, a path is provided in which the air sucked from the right side through the suction port 5 moves from the cavity 100 to the engine room, a path in which the air moves from the engine room area to the outside of the engine room, a path in which the air moves down from the top side of the engine room, a path in which air moves forward from the interior of the engine room, a path in which air moves down from the front section of the engine room, and a path in which air moves from the engine room to the left and then discharged through the outlet 6.

The above-described paths have a configuration that satisfies spatial integration for ideal operation of the refrigerator for a vehicle when installing the refrigeration system in a narrow space.

The power to draw in the air flow may be provided by the condenser fan 501 provided in the condensing unit 500. Thus, in terms of the air flow path, the air drawn into the condenser fan 501 may be outside the engine room. Exhaust air can be supplied to the interior of the engine room relative to the condenser fan 501.

The air exhausted from the condenser fan 501 can only exit through the flow guide 81.

This is due to the need to prevent the recirculation of hot air discharged outside the engine room cover 700 to the suction side of the condenser fan 501. To this end, the interior of the engine room surrounded by the engine room cover 700 is not in communication with the other sides except for the flow guide 81 .

As can be seen, the air discharged from the interior of the engine room 200 cannot go outside the console space 4, but enters the interior of the engine room 200 again, having a significant effect on reducing the efficiency of the refrigeration system.

In order to prevent this influence, the air from the engine room can only be discharged through the flow guide 81 and not discharged to other parts, and the air discharged through the flow guide 81 can be smoothly guided to the outlet. If the air discharged through the flow guide stagnates in the console space 4 without exiting through the outlet 6, some of the air may eventually enter the engine room 200. This leads to a significant reduction in cooling efficiency.

By increasing the speed of the condenser fan 501, the efficiency of the system can be maintained even if air is recirculated. However, when the speed of the condenser fan is increased, a loud noise is generated that causes discomfort to the driver. The vehicle cooler according to the embodiment is located next to the driver since the vehicle cooler is installed in the console. In this regard, the problem of noise becomes more significant. Because of these considerations, the maximum speed of the condenser fan 501 is preferably limited to about 2000 rpm.

Fig. 7 is a front perspective view of the engine room cover.

7, the engine room cover 700 has a front surface 710, a top surface 730, and a left surface 700 as described above. An air inlet hole may be formed in the rear surface.

The interior of the engine room 100 may be formed by the engine room cover 700, and the right and bottom surfaces of the engine room cover 700 can be provided as open spaces. The left surface of the engine room 100 becomes the right surface of the cavity, and the bottom surface of the engine room 100 may be the bottom of the engine room. According to the above-described configuration, the interior of the engine room can be formed.

Upper surface 730 is provided with stepped portions 732, 733, and 735 to smooth airflow and prevent placement problems for internal components located inside the engine room and external components located outside the engine room.

A controller accommodating portion 734 is provided protruding upward from the upper surface of the second stepped portion 733. The upper surface of the controller accommodating portion 734 and the lower surface of the third stepped portion 375 may be at the same height. Thus, the controller 900 can be placed in a horizontal position.

Between the controller accommodating portion 734 and the bottom surface of the third stepped portion 735, a recessed portion 733 may be provided at the same height as the upper surface of the second stepped portion 733. The recessed portion 733 may provide a space through which air passes under the controller 900, and outside air can enter or exit this space. Thus, the cooling of the controller 900 can be carried out through its upper section and lower section. Thus, the cooling of the controller 900 can be performed more evenly, and the proper operating temperature of the controller can be ensured in the narrow space of the console 3.

The engine room cover may be fixed to the outer wall of the vacuum adiabatic body 101 forming the cavity 100. To this end, a cavity attachment portion 742 may be provided on the right side of the engine room cover 700, and the engine room cover 700 and the cavity 100 may be formed as one. frame.

Since the engine room cover 700 completely seals the left side of the cavity, air from the engine room does not leak out. Thus, air recirculation can be prevented to improve cooling efficiency.

A controller 900 is installed in the interior space between the second step portion 733 and the third step portion 735. The controller 900 is connected and attached to the engine room cover 700, and controller attachment portions 737 and 738 are provided.

On the right side of the engine room cover 700, a through hole 741 is formed to guide the refrigerant pipe 600, which supplies refrigerant to the cavity through the upper opening of the cavity. The refrigerant line 600 passing through the through hole 741 may correspond to a regenerative adiabatic element for the line. The regenerative adiabatic piping element may be an element for thermally insulating a regenerative piping system that exchanges heat from a first refrigerant pipe entering the evaporator module 400 and heat from a second refrigerant pipe exiting the evaporator module.

The regenerative piping system may form a refrigerant piping section 600.

Fig. 8 is a perspective view of the controller, and Fig. 9 is an exploded perspective view of the controller.

8 and 9, the controller includes a bottom case 910 and a top cover 920 that form an interior space.

On the lower body 910, cover attachment portions 941 and 942 are provided, aligned with engine room cover 700 controller attachment portions 737 and 738, which are horizontally mounted on the upper surface of the engine room cover 700. On one side of the lower housing 910, a connection terminal 943 may be provided for electrical connection to the power supply and the sensor.

All electrical connection terminals provided in the vehicle refrigerator may be double-locked connection terminals to prevent the connection from loosening due to vehicle movement and vibration.

In the inner space formed by the bottom case 910 and the top cover 920, the control board 950 is disposed.

The control board 950 has a plurality of heat sources. Among them, a compressor control circuit for controlling the compressor 201, which includes a switching circuit, and because a relatively large current passes through the compressor, a large amount of heat is generated.

The compressor control circuit is usually attached to the side of the compressor. However, in the case of the embodiment, since the interior of the engine room in the vehicle refrigerator is narrow and the compressor is located just before the engine room outlet, the airflow temperature is high. Thus, it is not practical to install the compressor control circuit in the vicinity of the compressor.

As a solution to this problem, the compressor control circuit can be provided together with the control board 950 that controls the operation of the vehicle refrigerator, and the space of the vehicle refrigerator can be more compact. However, it is preferable that a heat dissipation structure having a high cooling efficiency be provided, because due to the mounting of a plurality of components on the narrow control board 950, the amount of heat generated is further increased, which may adversely affect the operation of the components.

To solve this problem, a heat sink 930 is provided that contacts a heat-generating portion of the control board 950 to promote heat radiation of the control board 950. The top cover 920 is provided with an opening 921 open on the top surface. Through an opening 921 in the lid, the heat sink 930 exits.

The exposed heat sink is cooled by air passing through the space between the engine room cover 700 and the console cover 300. Relatively cold air flows in the space between the engine room cover 700 and the console cover 300, and the air entering the console space 4 does not cool the other components. Therefore, cooling of the heat sink 930 can be performed evenly. In addition, the control board 950 can be uniformly cooled to improve operational reliability.

Next, the configuration of the controller 900 will be described in more detail.

Fig. 10 is a diagram of a control board.

10, the control board 950 includes a refrigerator control circuit 956 for controlling the operation of the vehicle refrigerator and a compressor control circuit 951 for controlling the operation of the compressor 201.

The refrigerator control circuit 956 can perform functions such as opening/closing a door, controlling a fan, storing data, determining states, and issuing commands. The compressor control circuit 951 is configured to control the rotation of the compressor motor and has a high heat dissipation value due to the execution of the switching operation and current supply.

The high temperature heat generated in the compressor control circuit 951 affects the other circuits of the control board 950 and creates the possibility of ignition. Thus, in the vicinity of the compressor control circuit 951, a temperature sensor 952 is provided to stop the compressor 201 when the sensor 952 detects a temperature equal to or above a threshold. In this regard, it is important that the value of the temperature sensor 952 does not rise above the threshold value.

Other high heat generating circuits on the control board are DC/DC converter 953 and diode 954 to boost the voltage from about 12 volts to about 40 volts. Although these components are different from the compressor control circuit 951, they have a significant effect on temperature rise, and if such components do not work properly, it may cause a malfunction of the refrigerator for the vehicle.

The area including the compressor control circuit 951 and the temperature sensor 952, as well as including the DC/DC converter 953 and the diode 954, is called a heat sink section 955, and the heat sink 930 may contact the heat sink section 955 directly or indirectly.

As described above, since the installation site of the heat sink 930 is a place where relatively cold air flows, such as the outer space of the engine room cover 700, the cooling operation through the heat sink 930 can be performed evenly. Thus, the cooling of the fuel components can be uniformly performed.

Fig. 11 is a block diagram for explaining the control of a refrigerator for a vehicle.

11, the vehicle refrigerator can be divided into a cavity 100, an engine room 200, a door 800, and a control board 950 to control the cavity, the engine room, and the door according to control functions.

The cavity 100 is provided with a temperature sensor 181 for measuring the temperature in the cavity, an evaporator fan 182 included in the evaporator module 400 to circulate cold air in the cavity, and a light source 183 that illuminates the interior of the cavity. Each of the components is controlled by the control unit 961 of the control board 950.

In the engine room 200, a condenser fan 281 is provided that draws air flow from the engine room and a compressor 282 that draws a refrigerant flow from the refrigeration system. The condenser fan 281 and the compressor 282 are controlled by the control unit 961.

A magnet 891 may be mounted on the door 800 and the controller 961 may perform the appropriate operation when the sensor 964 detects access to the magnet 891.

The relay switch 966 is controlled by the control unit 961, and the voltage regulators 965 and 967 control the operation of the fans 182 and 281.

A UART port for data input may be provided on the control board 950. The data required for the operation of the UART port can be saved.

A power switch 963 is provided on the control board 950 for turning off the power supplied from the 12-volt power supply.

The control unit 961 may be provided with a refrigerator control unit and a compressor control unit on the same chip.

When the control unit 961 is provided as one physical chip, the compressor control circuit for switching the compressor 282 and supplying high voltage to the compressor 282 is provided as a plurality of chips on a panel between the compressor 282 and the controller 961. The compressor control circuit 951 may be operated under the control of commands from the block 961 control to supply power to the compressor 282.

Next, the operation of each component will be described in turn.

When the refrigerator for transport is operating in normal mode, i.e. in state I, when the door is not open, the compressor 282, the condenser fan 281, and the evaporator fan 2 can operate according to the cavity temperature. Of course, intermittent operation may be performed depending on the operating state, such as the supercooling state. Periodic operation is monitored by the temperature sensor 181 and adjusted accordingly. On/off of compressor 282, condenser fan 281 and evaporator fan 2 cannot be performed at the same time, and the on/off state may differ depending on the refrigerant flow and the current temperature.

When the door 800 is opened while the vehicle refrigerator is operating, the sensor 964 detects a change in the magnetic field due to the trip or proximity of the magnet, which can be determined as the opening of the door 800. Thereafter, the compressor 282 may be turned off, or the fans 182 and 281 may be stopped. When door 800 is detected as open, evaporator fan 182 may be turned off at all times. This is necessary to prevent cold air loss.

Next, a detailed description will be given of the flow path of the air discharged through the flow guide and the method for preventing recirculation of the exhaust air from the engine room.

12 is a front view of a refrigerator for a vehicle.

12, the refrigerator for the vehicle is installed in the space 4 of the console. The air inside the engine room, which passes through the above-described path, is directed to the outlet 6 through the flow guide 81.

The flow guide 81 is recessed into the bottom frame of the refrigerator and at least a portion of it is inclined towards the outlet 6.

In the path between the flow guide 81 and the outlet 6, a connection channel 65 may be provided. The connection channel 65 is a member connecting the flow guide 81 provided in the bottom frame 8 of the refrigerator to the inlet end of the outlet 6.

According to the connecting channel 65, the laminar flow flowing through the flow guide 81 can be continuous. Thus, the air flow can be stably guided. However, it is not necessary to ensure that the connection port 81 is in contact with the inlet end of the outlet 6. The recirculation of exhaust air from the engine room can be greatly reduced by placing the outlet of the connection port 81 near the inlet end of the outlet 6. This has a significant effect on improving thermal efficiency.

The height H2 of the outlet 6 is greater than the height H1 of the outlet end of the flow guide 81 . This is to reduce the discomfort caused to the passenger by the hot air discharged from the outlet 6 and to prevent the exhaust air from being recirculated. Accordingly, the air discharged from the flow guide 81 is dispersed and the flow rate is slowed down so that direct contact with the occupant is prevented.

13 is a left side view of a refrigerator for a vehicle.

13, the outlet width W2 is larger than the width of the flow guide 81 . Accordingly, the air discharged from the flow guide 81 is dispersed and the flow rate is slowed down so that direct contact with the occupant is prevented. In addition, a uniform flow is ensured and recirculation of exhaust air is prevented.

When comparing the height of the center of the outlet with the height of the outlet end of the flow guide 81, the center of the outlet is located at a relatively lower height than the centers of the elements. This is because the air discharged from the flow guide 81 is directed downward, so that the natural airflow of the air is maximized.

Fig.14-18 are illustrations of simulation results to explain the various designs of the flow guide

Referring to FIG. 14, the flow guide 81 according to the embodiment may have an inclined portion that gradually descends towards the left to direct the flow. The flow guide 81 is provided, for example, by notching and pulling the plate bottom frame 8 of the refrigerator, and has a size and structure similar to the area of the notched plate.

In this embodiment, it can be seen that the exhaust air from the engine room 200 is redirected to the console space through the gap between the bottom frame 8 of the refrigerator and the console space 4. The recirculated air may again enter the engine room 200, resulting in a reduction in the efficiency of the refrigeration system.

In the drawing, dark blue shows an area without flow, and the thicker the red, the faster the flow. This also applies to other drawings.

Referring to FIG. 15, the flow guide 81 in this example has an inclined portion that descends in the left direction to guide the flow, and is provided, for example, by cutting and pulling the refrigerator plate bottom frame 8 to provide a similar size and structure to the area of the notched plate. In addition, a barrier wall 66 is provided extending downward from the lower end of the outlet end of the flow guide.

The gap between the bottom frame 8 of the refrigerator and the console space 4 is closed by the closing wall 66, and exhaust air does not pass between them. Thus, hot air can be prevented from entering the engine room 200, i. e. to the inlet side of the condensation module 500.

The barrier wall 66 is preferably a means of preventing exhaust air from being recirculated to the engine room.

Referring to FIG. 16, the flow guide 81 in this example has an inclined portion that descends in the left direction to direct the flow, and is provided, for example, by notching and pulling the lamellar bottom frame 8 of the refrigerator to provide a similar size and structure to the area of the notched plate. In addition, a connection channel 65 is provided further extending from the outlet end of the flow guide 81 to the outlet 6.

The connection channel 65 extends almost to the inlet end of the outlet 6, but does not contact the outlet 6. This is because the exhaust air from the connection channel 65 is directly discharged through the outlet 6, which prevents a large flow rate and user discomfort. In addition, such a structure can prevent exhaust air from being recirculated to the engine room.

The size of the outlet side of the connecting channel 65 may be larger than the size of the inlet side of the connecting channel 65. In this case, the connecting channel 65 itself can serve as a diffuser. The outlet end of the connection channel 65 may match the size of the outlet 6, and the outlet end of the connection channel 65 may contact the inlet end of the outlet 6 in the case of a diffuser. In this case, the passenger does not experience discomfort.

Referring to FIG. 17, the flow guide 81 in this example does not have a sloping portion that descends towards the left, and is provided, for example, by notching and pulling the refrigerator plate bottom frame 8 to provide a similar size and structure to the area of the notched plate.

In this embodiment, the turbulence inside the flow guide 81 increases, and the turbulence inside the flow guide 81 propagates outward. Thus, the flow reaches the gap between the lower frame 8 of the refrigerator and the console space 4, and the exhaust air is recirculated to the engine room.

As described above, the recirculation of exhaust air to the engine room adversely affects the heat exchange efficiency, the efficiency of the refrigerator is reduced, and the internal temperature of the cavity is increased.

Referring to FIG. 18, the flow guide 81 according to the embodiment may have an inclined portion that gradually descends towards the left to direct the flow. In addition, the flow guide 81 is provided, for example, by cutting and pulling the plate bottom frame 8 of the refrigerator to provide a size and structure similar to the area of the notched plate. In addition, the flow guide 81 is further inclined downward to provide a height and vertical width equal to the outlet 8.

At the outlet portion of the flow guide 81, a turbulence region A is generated due to the size of the additional flow guide, and the influence of the turbulence region A occurs between the bottom frame 8 of the refrigerator and the console space 4, so that the flow reaches the gap therebetween. As a result, it can be seen that the exhaust air is recirculated.

As a result of the above experiment, it has been found that the use of a barrier wall 66 and a connecting passage 65 is the preferred means of preventing the air discharged from the outlet end of the flow guide 81 from being recirculated to the engine room.

Next, the construction and operation of the vacuum adiabatic vessel will be described in more detail.

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

First of all, as shown in FIG. 19a, 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 lower 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.

The component that prevents heat transfer between the first space and the second space may be referred to as a heat transfer preventing assembly. The following various configurations can be applied together or separately.

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. In this regard, the radiation obstruction sheet 32 may be plate-shaped over a large portion of the area of the vacuum space portion 50 to help reduce radiation heat transferred between the first and second plate elements 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.

19b, 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.

19c, 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.

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

According to Fig.20a, 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 . Accordingly, 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 thermal insulation. 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 radiant heat transfer ④ is smaller than the heat transfer amount by conduction heat transfer of a solid body, but is 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/AΔT. Here, Q stands for heating value (W) and can be obtained using the heating value of the heater. A indicates the cross-sectional area (m ² ) 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 (ΔT) between the inlet and outlet of the heat inhibition sheet 60, the cross-sectional area (A) of the heat inhibition sheet, the length (L) of the heat inhibition sheet, and the thermal conductivity ( k) the heat transfer inhibiting sheet (the thermal conductivity of the heat transfer inhibiting sheet is a property of the material and can be determined in advance). For heat transferred by thermal conduction of the support, the heating value can be obtained based on the temperature difference (ΔT) between the inlet and outlet of the support node 30, the cross-sectional area (A) of the support node, the length (L) of the support node, and the thermal conductivity (k) of the support node. 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 inhibiting 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 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 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/m ² ) of a certain level can be used.

Referring to Fig. 20b, this shown configuration is similar to that shown in Fig. 20a, 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 are described in detail. components.

The ends of the plate members 10 and 20 may be bent toward the second high temperature space to form a flange portion 65. A welded portion 61 may be provided on the upper surface of the flange portion 65 to connect the heat transfer inhibiting sheet 60 to the flange portion 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. 20a, due to the narrow space in the vacuum space portion 50, for example, in the refrigerator 7 for a vehicle.

Fig. 21 is a graph illustrating the results obtained by observing the time and pressure during evacuation of the interior of the vacuum adiabatic body using the reference assembly.

As shown in FIG. 21, 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 (Δt1). 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 (Δt2). 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 activation of the getter 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.22 is a graph obtained by comparing vacuum pressure and gas thermal conductivity.

22, 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 a point corresponding to a typical effective heat transfer coefficient of 0.0196 W/m⋅K, which is provided by an adiabatic material formed by foaming polyurethane, is small, the vacuum pressure is 2.65×10 ^-1 Torr, even when the gap size is 2.76mm. 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 about 4.5×10 ^-3 Torr. A vacuum pressure of 4.5 x 10 ^-3 Torr can be defined as the point at which the decrease in the adiabatic effect due to the heat transferred by the thermal conduction 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.

According to the present invention, user satisfaction can be improved because the vehicle allows the user to quickly obtain the food in the desired state.

Claims (121)

1. A device having a cooling and heating function, comprising: branch; an engine room provided on the side and outside of said room; a compressor provided in an engine room for compressing the refrigerant; the first heat exchange unit provided in the engine room to provide heat exchange of the refrigerant; a second heat exchange unit provided in said compartment to enable heat exchange of the refrigerant; and cover that closes the engine room, wherein a first air flow path is provided along which the first air moves downward from the top side of the engine room cover so that the first air is sucked into the engine room, and a second air flow path is provided along which the second air moves downward from the front of the engine room so that the second air is discharged from the engine room. 2. The device according to claim 1, in which the first heat exchange unit and the compressor are located in series in the engine room in accordance with the direction of the internal air flow. 3. The apparatus of claim 1, further comprising a flow guide provided below the compressor to discharge the internal air flow away from said compartment. 4. The device according to claim 1, in which the air from the inlet side of the external air flow runs parallel to the wall of said compartment. 5. The apparatus of claim 1, wherein the width of the external airflow gradually decreases as the airflow advances. 6. A device having a cooling and heating function, comprising: branch; an engine room provided on the side and outside of said room; a compressor provided in an engine room for compressing the refrigerant; the first heat exchange unit provided in the engine room to provide heat exchange of the refrigerant; a second heat exchange unit provided in said compartment to enable heat exchange of the refrigerant; and cover that closes the engine room, wherein the first airflow along the first surface of the lid and the second airflow along the second surface of the lid are separated by the lid, and the first air flow includes air movement from the inside of the cover, and the second air flow includes air movement from the outside of the cover. 7. A device having a cooling and heating function, comprising: compartment, at least a wall section of which is provided in the form of a vacuum adiabatic housing; an engine room provided on the side and outside of said room; a compressor provided in an engine room for compressing the refrigerant; the first heat exchange unit provided in the engine room to provide heat exchange of the refrigerant; a second heat exchange unit provided in said compartment to enable heat exchange of the refrigerant; and cover that closes the engine room, wherein the device includes a first air flow path, along which the air sucked from the suction hole moves in the first direction, and a second air flow path, along which the air moves in the second direction from the first part of the engine room to the outside of the engine room. 8. The apparatus of claim 7, wherein the first direction and the second direction are perpendicular to each other. 9. The apparatus of claim 7, wherein the apparatus includes a third air flow path in which air moves in a third direction from the rear of the engine room to the front of the engine room within the engine room. 10. The apparatus of claim 9, wherein the second direction and the third direction are opposite to each other. 11. The apparatus of claim 7, wherein the apparatus includes an air flow path in which air moves in a fourth direction down from the front of the engine room and an air flow path in which air moves in a fifth direction from the engine room to the outlet . 12. The apparatus of claim 11, wherein the fifth direction is the same as the first direction. 13. The device according to claim 7, wherein the first direction is defined as the direction from said compartment to the engine room. 14. The apparatus of claim 7, wherein an air flow path is provided in which air moves downward from the top side of the engine room cover so that air is drawn into the engine room. 15. The device according to claim 7, wherein the first heat exchange unit and the compressor are arranged in series within the engine room according to the direction of the internal air flow. 16. The apparatus of claim 7, wherein the second air flow path along the first surface of the cover and the third air flow path along the second surface of the cover are separated by the cover. 17. The apparatus of claim 9, wherein the first air flow path includes air moving from one side of the cover and the third air flow path includes air moving from the other side of the cover. 18. The apparatus of claim 9, wherein the first air flow path includes air moving from the inside of the lid and the third air flow path includes air moving from the outside of the lid. 19. A device having a cooling and heating function, comprising: compartment, at least a section of the wall of which is provided in the form of a vacuum adiabatic housing; an engine room provided on the side and outside of said room; a compressor provided in an engine room for compressing the refrigerant; the first heat exchange unit provided in the engine room to provide heat exchange of the refrigerant; a second heat exchange unit provided in said compartment to enable heat exchange of the refrigerant; and cover that closes the engine room, wherein the device includes an air flow path in which air moves in a water direction down from the front of the engine room, and an air flow path in which air moves in the other direction from the engine room to the outlet. 20. The apparatus of claim 19, wherein said one direction and said other direction are different. 21. A device having a cooling and heating function, comprising: compartment, at least a section of the wall of which is provided in the form of a vacuum adiabatic housing; an engine room provided on the side and outside of said room; a compressor provided in an engine room for compressing the refrigerant; the first heat exchange unit provided in the engine room to provide heat exchange of the refrigerant; a second heat exchange unit provided in said compartment to enable heat exchange of the refrigerant; and cover that closes the engine room, wherein an air flow path is provided in which air moves downward from the top side of the engine room so that air is sucked into the engine room, or an air flow path is provided in which air moves downward from the front of the engine room so that air is exhausted from the engine room, or an air flow path is provided along which air moves from the compartment to the engine room. 22. A device having a cooling and heating function, comprising: compartment, at least a section of the wall of which is provided in the form of a vacuum adiabatic housing; engine room; a compressor provided in an engine room for compressing the refrigerant; the first heat exchange unit provided in the engine room to provide heat exchange of the refrigerant; a second heat exchange unit provided in said compartment to enable heat exchange of the refrigerant; and cover that closes the engine room, wherein the flow path of the first air along the first surface of the cover and the flow path of the second air along the second surface of the cover are separated by the cover. 23. The apparatus of claim 22, wherein the first air flow path and the second air flow path are provided in opposite directions. 24. The apparatus of claim 22, wherein the first air flow path includes air moving from one side of the cover and the second air flow path includes air moving from the other side of the cover. 25. The apparatus of claim 22, wherein the first air flow path includes air moving from the inside of the lid and the second air flow path includes air moving outside the lid. 26. A device having a cooling and heating function, comprising: compartment, at least a section of the wall of which is provided in the form of a vacuum adiabatic housing; an engine room provided on the side and outside of said room; a compressor provided in an engine room for compressing the refrigerant; the first heat exchange unit provided in the engine room to provide heat exchange of the refrigerant; a second heat exchange unit provided in said compartment to enable heat exchange of the refrigerant; a cover that closes the engine room; and a flow guide provided for venting internal air from the inside of the cover. 27. The apparatus of claim 26, wherein the flow guide is vertically aligned with the compressor for quick release. 28. The apparatus of claim 26, wherein the flow guide directs the exhausted air outside the engine room towards the outlet so that high temperature is prevented from affecting the compartment and/or the flow guide is aligned with the outlet of the console. 29. The apparatus of claim 26, wherein the flow guide has a sloped portion to discharge the internal air away from the compartment, or the flow guide has a slope that slopes towards the outlet of the console. 30. The apparatus of claim 26, wherein the flow guide is provided such that it is recessed into the bottom frame of the refrigerator supporting the compartment. 31. The apparatus of claim 26, wherein the barrier wall is provided downstream of the end portion of the flow guide. 32. The device according to claim 26, wherein a barrier wall is provided in the interval between the bottom frame of the refrigerator supporting the compartment and the console space so that exhaust air does not pass through this interval, and/or a barrier wall is provided for closing the space between the lower part of the internal console space and the outlet end of the flow guide. 33. The apparatus of claim 26, wherein the flow guide is provided by cutting and pulling the lamellar bottom frame of the refrigerator. 34. A device having a cooling and heating function, comprising: compartment, at least a section of the wall of which is provided in the form of a vacuum adiabatic housing; an engine room provided on the side and outside of said room; a compressor provided in an engine room for compressing the refrigerant; the first heat exchange unit provided in the engine room to provide heat exchange of the refrigerant; a second heat exchange unit provided in said compartment to enable heat exchange of the refrigerant; a flow guide provided for discharging internal air from the inside of the cover; and console outlet. 35. The apparatus of claim 34, wherein the width of the outlet is larger than the width of the flow guide so that the discharged air is dispersed. 36. The apparatus of claim 34, wherein the height of the outlet is lower than the height of the flow guide so that the natural airflow of the air is increased. 37. A device having a cooling and heating function, comprising: compartment, at least a section of the wall of which is provided in the form of a vacuum adiabatic housing; an engine room provided on the side and outside of said room; a compressor provided in an engine room for compressing the refrigerant; the first heat exchange unit provided in the engine room to provide heat exchange of the refrigerant; a second heat exchange unit provided in said compartment to enable heat exchange of the refrigerant; an opening of the lower frame of the refrigerator surrounding the compartment, the air being discharged through the opening; and a shut-off wall provided in a gap between the bottom frame of the refrigerator and the console space so that exhaust air does not pass through the gap. 38. The apparatus of claim 37, wherein the barrier wall is provided for sealing off the space between the bottom of the console interior space and the outlet end of the flow guide to direct the discharged air. 39. A device having the function of cooling and heating, containing: compartment, at least a section of the wall of which is provided in the form of a vacuum adiabatic housing; an engine room provided on the side and outside of said room; a compressor provided in an engine room for compressing the refrigerant; the first heat exchange unit provided in the engine room to provide heat exchange of the refrigerant; a second heat exchange unit provided in said compartment to enable heat exchange of the refrigerant; and a connecting passage provided between the internal air outlet from the inside of the engine room and the outlet of the console. 40. The apparatus of claim 39, wherein the connection passage is an element for connecting a flow guide provided in the bottom frame of the refrigerator supporting the engine room to the inlet end of the outlet. 41. The device according to claim 39, wherein the outlet of the connecting channel is located near the inlet end of the outlet. 42. The apparatus of claim 39, wherein the connecting passage does not come into contact with the outlet. 43. The apparatus of claim 39, wherein the outlet of the connecting channel has a size larger than the size of the inlet of the connecting channel. 44. The apparatus of claim 39, wherein the outlet end of the connecting channel is aligned with the outlet. 45. A vehicle comprising the device of claim 39, wherein the vehicle comprises: a plurality of seats spaced apart from each other, a console provided between adjacent seats and including a console space; and a refrigerator bottom frame provided in the console space; wherein said device is placed inside the console space.

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