DEFROSTING DEVICE AND REFRIGERATOR HAVING THE SAME

TECHNICAL FIELD

The present disclosure relates to a defrosting device for removing frost formed on an evaporator provided in a refrigeration cycle, and a refrigerator having the same.

BACKGROUND ART

An evaporator provided in a refrigeration cycle decreases ambient temperature using cool air generated by the circulation of coolant flowing through a cooling tube. During the process, when there occurs a temperature difference from ambient air, a phenomenon of condensing and freezing moisture in the air on a surface of the cooling tube occurs.

A defrosting method using an electric heater has been used for a defrosting process for removing frost formed on an evaporator in the related art.

In recent years, a defrosting device using a heat pipe has been developed and contrived, and the related technologies include Korean Patent Registration No. 10-0469322, entitled “Evaporator.”

A heat pipe type defrosting device in the aforementioned patent “Evaporator” has a configuration in which a heater is vertically disposed in the top-down direction of the evaporator, and working fluid is filled only into a bottom portion of the heater. The defrosting device with the foregoing structure may increase the evaporation speed due to rapid heating but has a danger of overheating the heater.

Furthermore, it has a structure in which the heater is accommodated into the heat pipe, and thus high-temperature heat may be concentrated on an inside of the heat pipe, thereby reducing the lifespan of the heater as well as causing the sealing problem of the heater.

DISCLOSURE OF THE INVENTION

An aspect of the present disclosure is to provide a defrosting device with a new structure that can be fabricated at lower cost capable of reducing power consumption during defrosting, and facilitating maintenance.

Another aspect of the present disclosure is to provide a defrosting device capable of enhancing the heat transfer performance of a heater as well as preventing the overheating of the heater to enhance reliability.

Still another aspect of the present disclosure is to provide a defrosting device capable of preventing working fluid from being brought into contact with a heater.

Yet still another aspect of the present disclosure is to provide a defrosting device capable of efficiently circulating working fluid.

Still yet another aspect of the present disclosure is to provide a structure of efficiently carrying out defrosting for a lower cooling tube of an evaporator in a defrosting device in which a heating unit is vertically disposed along the top-down direction of the evaporator.

In order to accomplish the foregoing tasks of the present disclosure, a defrosting device according to the present disclosure may include a heating unit provided in an evaporator; and a heat pipe, both end portions of which are connected to an inlet and an outlet of the heating unit, respectively, and at least part of which is disposed adjacent to a cooling tube to dissipate heat to the cooling tube of the evaporator due to high-temperature working fluid heated and transferred by the heating unit, wherein the heating unit includes a heater case provided with a vacant space therein, and provided with the inlet and the outlet at positions separated from each other, respectively, along a length direction; and a heater attached to an outer surface of the heater case to heat working fluid within the heater case.

The heater may be a plate-shaped heater having a plate shape.

The heater may include a base plate formed of a ceramic material, and attached to an outer surface of the heater case; a hot wire formed on the base plate, and configured to dissipate heat during the application of power; and a terminal provided on the base plate to electrically connect the hot wire to the power.

The heater case may be divided into an active heating part corresponding to a portion on which the hot wire is disposed and a passive heating part corresponding to a portion on which the hot wire is not disposed, and the inlet may be formed on the passive heating part to prevent working fluid being moved through the heat pipe and then returned through the inlet from being reheated to flow backward.

The hot wire may be extended and formed from one point between the inlet and the outlet toward the outlet.

The present disclosure discloses a first through a fourth embodiment of a defrosting device based on the structure.

First Embodiment

The heater may be attached to a bottom surface of the heater case.

A first and a second extension fin extended and formed downward from a bottom surface and configured to cover both lateral surfaces of the heater attached to the bottom surface may be provided at both sides of the heater case, respectively.

A sealing member may be filled to cover the heater on a rear surface of the heater and a recessed space formed by the first and the second extension fin.

An insulating material may be interposed between the rear surface of the heater and the sealing member.

A thermal conductive adhesive may be interposed between the heater case and the heater.

The heater case may include a main case provided with a vacant space therein, both end portions of which have an open shape, and to a bottom surface of which the heater is adhered; and a first cover and a second cover mounted to cover both open end portions of the main case, respectively.

At least one of the first and the second cover may be extended and formed downward from a bottom surface of the main case, and configured to surround the heater along with the first and the second extension fins.

When the heat pipe is configured with a first heat pipe and a second heat pipe disposed to form two rows on a front portion and a rear portion of the evaporator, respectively, the outlet may include a first outlet and a second outlet connected to an end portion of the first and the second heat pipe, respectively, and the inlet may include a first inlet and a second inlet connected to the other end portion of the first and the second heat pipe, respectively.

The first and the second outlet may be formed at both sides of the main case, respectively, or formed in parallel to each other to the first cover.

The first and the second inlet may be formed at both sides of the main case, respectively, or folioed in parallel to each other to the second cover.

On the other hand, an outer fin may be protruded and formed on another outer surface of the heater case to which the heater is not adhered.

The heater may be attached to a bottom surface of the heater case, and the outer fin may be formed on an upper surface of the heater case.

A plurality of outer fins may be provided thereon, and extended and formed along a length direction or width direction of the heater case with a predetermined separation distance from each other. The separation distance may be set to be the same as or larger than a width of the outer fin.

Alternatively, the plurality of outer fins may be provided thereon, and disposed with a predetermined separation distance from each other along a length direction and a width direction of the heater case to form a matrix.

In a structure in which the first and the second outlet are formed on both lateral surfaces, respectively, adjacent to one end portion of the main case, and the first and the second inlet are formed on both lateral surfaces, respectively, adjacent to the other end portion of the main case, the outer fin may be protruded and formed on both outer surfaces of the main case, respectively, but extended and fanned between the first inlet and the first outlet and the second inlet and the second outlet in an elongated manner.

The outer fin may be also protruded and formed on an outer surface of at least one of the first and the second cover.

On the other hand, an inner fin may be protruded and formed on an inner surface at an inner side of the outer surface to which the heater is adhered.

The heater may be attached to an outer bottom surface of the heater case, and the inner fin may be protruded and formed from an inner bottom surface of the heater case.

The inner fin may be protruded and formed with a length less than ½ compared to an inner height of the heater case.

A plurality of inner fins may be provided thereon, and extended and formed along a length direction of the heater case with a predetermined separation distance from each other.

A distance from an inner wall of the heater case to the inner fin adjacent to the inner wall may be formed to be greater than one time but less than two times compared to a width of the inner fin.

A separation distance between each other of the plurality of inner fins may be formed to be greater than one time but less than two times compared to the width of the inner fin.

In a structure in which the first and the second outlet are formed on both lateral surfaces, respectively, adjacent to one end portion of the main case, and the first and the second inlet are formed on both lateral surfaces, respectively, adjacent to the other end portion of the main case, the inner fin may be extended and formed between the first inlet and the first outlet and the second inlet and the second outlet in an elongated manner.

On the other hand, it is configured such that the lead wire is extended outward from one end portion of the heater adjacent to an outer side of the evaporator.

In a structure in which the heating unit is disposed at a left bottom portion of the evaporator, it is configured such that the lead wire is extended outward from a left end portion of the heater adjacent to the left side of the evaporator.

In this case, the terminal connected to the lead wire may be located at a left end portion of the heater.

In a structure in which the heating unit is disposed at a right bottom portion of the evaporator, it is configured such that the lead wire is extended outward from a right end portion of the heater adjacent to the right side of the evaporator.

In this case, a right end portion of the heater may be disposed between the inlet and the outlet of the heater case, and the terminal connected to the lead wire may be located between the inlet and the outlet adjacent to the inlet of the heater case.

On the other hand, the outlet may be formed at a position separated backward from a front end of the heater case with a predetermined distance in such a manner that to part of working fluid remains at a front end portion of the heater case to be brought into contact with the heater.

Furthermore, an inner diameter of a return portion of the heat pipe connected to the inlet of the heater case may be formed to be greater than 5 mm but less than 7 mm.

On the other hand, the heater case may be disposed such that an end portion of the inlet side has an angle range greater than −90° but less than 2° with respect to an end portion of the outlet side.

Moreover, in consideration of a flow direction of working fluid and a rising characteristic of heated working fluid, the return portion may be disposed in parallel to the heater case or extended and formed in a downward direction of the heater case, and an entrance portion of the heat pipe connected to an outlet of the heater case may be disposed in parallel to the heater case or extended and formed in an upward direction of the heater case.

Second Embodiment

It is configured such that the heater case is vertically disposed along a top-down direction at an outer side of a support fixture provided at one side of the evaporator, and the heater is located lower than a water level of working fluid filled into the heater case when the working fluid is all in a liquid phase.

The heater may be attached to an opposite surface to one surface of the heater case facing the support fixture.

Third Embodiment

It is configured such that the heat pipe is repeatedly bent in a zigzag shape to form a plurality of columns, and a distance between each column disposed at a lower portion of the heat pipe is smaller than that between each column disposed at an upper portion thereof.

A distance between each column disposed at a lower portion of the first heat pipe at a front side of the evaporator may be formed to be smaller than that between each column disposed at an upper portion thereof, and a distance between each column disposed at an upper portion of the second heat pipe at a rear side of the evaporator may be formed to be smaller than that between each column disposed at a lower portion thereof.

Alternatively, a distance between each column disposed at a lower portion of the first heat pipe at a front side of the evaporator may be formed to be larger than that between each column disposed at an upper portion thereof, and a distance between each column disposed at an upper portion of the second heat pipe at a rear side of the evaporator may be formed to be larger than that between each column disposed at a lower portion thereof.

Fourth Embodiment

The heat pipe may include an evaporation unit connected to an outlet of the heating unit, and disposed to correspond to the cooling tube to transfer heat to the cooling tube; and a condensing unit extended from the evaporator and disposed lower than the lowest column of the cooling tube, and connected to an inlet of the heating unit.

According to the foregoing structure, a lower end of the heating unit may be disposed adjacent to the lowest column of the cooling tube.

Alternatively, at least part of the heating unit may be disposed lower than the lowest column of the cooling tube.

According to present disclosure, it is configured such that the heater is attached to an outer surface of the heater case to heat working fluid within the heater case, thereby facilitating maintenance during the failure of the heater compared to a structure in which the heater is accommodated into the heater case. Furthermore, when a plate-shaped ceramic heater is applied to the heater, it may be possible to implement a defrosting device with a high efficiency at a lower cost.

When an outer fin is formed on an outer surface of the heater case in the defrosting device, an outer area of the heater case may increase, thereby enhancing heat exchange efficiency between ambient low-temperature air and the heater case.

Moreover, when an inner fin is formed at an inner portion of the heater case in the defrosting device, a contact area to working fluid filled into the heater case may increase, thereby increasing a heat transfer rate of being transferred from the heater to working fluid. Furthermore, the entire volume of the heater case may increase to increase heat capacity capable of receiving heat from the heater case, thereby receiving more heat generated from the heater. As a result, it may be possible to enhance defrosting performance.

When outer fins and/or inner fins are formed as described above, a large amount of heat generated from the heater may be transferred to the heater case at a front side of the heater to prevent the overheating of the heater, and the temperature of a rear portion of the heater may decrease to enhance the reliability and lifespan of the heater.

Furthermore, according to the defrosting device, the sealing structure of the heater may be implemented by a structure in which the heater is attached to a bottom surface of the heater case, and a first and a second extension fin at both sides of the heater case are respectively extended and formed downward from the bottom surface, and a sealing member is filled into a recessed space formed by a rear surface of the heater and the first and the second extension fin.

Moreover, a return portion connected to the inlet of the heating unit may have an inner diameter greater than 5 mm but less than 7 mm. In this case, working fluid being returned may be efficiently introduced into the heater case, thereby preventing reheated working fluid from flowing backward.

Furthermore, a structure capable of efficiently forming the flowing of working fluid reheated by the heater and discharged in a gas phase with a rising force while preventing reheated working fluid from flowing backward through a connection structure between the heating unit and the heat pipe for facilitating the flowing of working fluid in consideration of a rising characteristic of heated working fluid.

In addition, when at least two or more columns of low-temperature condensing units of the heat pipe are further disposed lower than the lowest column of the cooling tube of the evaporator in a defrosting device in which the heating unit is vertically disposed along a top-down direction of the evaporator, only a high-temperature evaporation unit may be used for the defrosting of the evaporator, thereby efficiently carrying out defrosting for a lower cooling tube.

According to the foregoing structure, at least part of the heating unit may be disposed lower than the evaporator, and a lower end of the heating unit may be preferably located adjacent to the lowest column of a horizontal pipe of the heating unit. In this case, a filling amount of working fluid may decrease, thereby increasing the temperature of the lowest column of the horizontal pipe of the heating unit up to a defrostable level.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a longitudinal cross-sectional view schematically illustrating the configuration of a refrigerator according to an embodiment of the present disclosure.

FIGS. 2 and 3 are a front view and a perspective view illustrating a first embodiment of a defrosting device applied to the refrigerator in FIG. 1.

FIG. 4 is an exploded perspective view illustrating an example of a heating unit illustrated in FIG. 3.

FIG. 5 is a cross-sectional view in which the heating unit illustrated in FIG. 4 is taken along a length direction.

FIG. 6 is a conceptual view illustrating the heater illustrated in FIG. 4.

FIGS. 7 through 9 are exploded perspective views illustrating examples in which the formation positions of an outlet and an inlet are modified in the heating unit illustrated in FIG. 4

FIGS. 10 and 11 are conceptual views for explaining the circulation of working fluid in a state prior to or subsequent to the operation of the heater

FIG. 12 is a cross-sectional view in which another example of the heating unit illustrated in FIG. 3 is taken along a width direction

FIGS. 13 and 14 are conceptual views illustrating examples in which the shape of outer fins is modified in the heating unit illustrated in FIG. 12

FIGS. 15 and 16 are cross-sectional views in which still another example of the heating unit illustrated in FIG. 3 is taken along a width and a length direction

FIG. 17 is a cross-sectional view illustrating an example in which the formation positions of inner fins are modified in the heating unit illustrated in FIG. 16

FIG. 18 is a cross-sectional view illustrating yet still another example of the heating unit illustrated in FIG. 3

FIGS. 19 and 20 are conceptual views for explaining the connection structure of a lead wire according to the position of the heating unit

FIGS. 21A through 21C are graphs illustrating a temperature change of the heater for an inner diameter of a return portion illustrated in FIG. 4 in a freezing condition

FIG. 22 is a view conceptually illustrating the flow of fluid at the return portion in the condition of FIG. 21C

FIG. 23 is graphs illustrating a temperature change of each column of the heater case and heat pipe according to an angle at which an inlet-side end portion of the heater case is inclined with respect to an outlet-side end portion thereof

FIGS. 24 through 26 are longitudinal cross-sectional views illustrating a modified example of a connection structure between a heating unit and a heat pipe in the heating unit applied to FIGS. 19 and 20

FIGS. 27 and 28 are a front view and a perspective view illustrating a second embodiment of a defrosting device applied to the refrigerator in FIG. 1

FIG. 29 is a conceptual view illustrating a third embodiment in which a width between upper columns and lower columns of the heat pipe is differently &limed in a defrosting device applied to the refrigerator in FIG. 1

FIGS. 30 and 31 are conceptual views illustrating a modified example of the defrosting device illustrated in FIG. 29

FIGS. 32 and 33 are a front view and a perspective view illustrating a fourth embodiment of a defrosting device applied to the refrigerator in FIG. 1 and

FIGS. 34 and 35 are a front view and a perspective view illustrating an example in which the formation position of the heating unit is modified in the defrosting device illustrated in FIGS. 32 and 33.

MODES FOR CARRYING OUT THE PREFERRED EMBODIMENTS

Hereinafter, a defrosting device and a refrigerator having the same associated with the present disclosure will be described in more detail with reference to the accompanying drawings.

According to the present specification, the same or similar elements are designated with the same numeral references even in different embodiments and their redundant description will be omitted.

Furthermore, a structure applied to any one embodiment may be also applied in the same manner to another embodiment if they do not structurally or functionally contradict each other even in different embodiments.

A singular representation may include a plural representation as far as it represents a definitely different meaning from the context.

In describing the embodiments disclosed herein, moreover, the detailed description will be omitted when a specific description for publicly known technologies to which the invention pertains is judged to obscure the gist of the present invention.

The accompanying drawings are used to help easily understand various technical features and it should be understood that the embodiments presented herein are not limited by the accompanying drawings. As such, the present disclosure should be construed to extend to any alterations, equivalents and substitutes in addition to those which are particularly set out in the accompanying drawings.

FIG. 1 is a longitudinal cross-sectional view schematically illustrating the configuration of a refrigerator 100 according to an embodiment of the present disclosure.

The refrigerator 100 is a device for storing foods kept therein at low temperatures using cooling air generated by a less in which the processes of compression-condensation-expansion-evaporation are sequentially carried out.

As illustrated in the drawing, a refrigerator body 110 may include a storage space for storing foods therein. The storage space may be separated by a partition wall 111, and divided into a refrigerating chamber 112 and a freezing chamber 113 according to the set temperature.

According to the embodiment, a top mount type refrigerator in which the freezing chamber 113 is disposed on the refrigerating chamber 112, but the present disclosure may not be necessarily limited to this. The present disclosure may be applicable to a side by side type refrigerator in which the refrigerating chamber and freezing chamber are horizontally disposed, a bottom freezer type refrigerator in which the refrigerating chamber is provided at the top and the freezing chamber is provided at the bottom, and the like.

A door is connected to the refrigerator body 110 to open or close a front opening portion of the refrigerator body 110. According to the present drawing, it is illustrated that a refrigerating chamber door 114 and a freezing chamber door 115 are configured to open or close a front portion of the refrigerating chamber 112 and freezing chamber 113, respectively. The door may be configured in various ways, such as a rotation type door in which a door is rotatably connected to the refrigerator body 110, a drawer type door in which a door is slidably connected to the refrigerator body 110, and the like.

The refrigerator body 110 may include at least one of accommodation units 180 (for example, a shelf 181, a tray 182, a basket 183, etc.) for effectively using an internal storage space. For example, the shelf 181 and tray 182 may be installed within the refrigerator body 110, and the basket 183 may be installed at an inside of the door 114 connected to the refrigerator body 110.

On the other hand, a cooling chamber 116 provided with an evaporator 130 and a blower fan 140 is provided at a rear side of the freezing chamber 113. A refrigerating chamber return duct 111a and a freezing chamber return duct 111b for inhaling and returning the air of the refrigerating chamber 112 and freezing chamber 113 to the side of the cooling chamber 116 are formed on the partition wall 111. Furthermore, a cool air duct 150 communicating with the freezing chamber 113 and having a plurality of cool air discharge ports 150a on a front portion thereof is installed at a rear side of the refrigerating chamber 112.

A machine room 117 is provided at a rear lower side of the refrigerator body 110, and a compressor 160, a condenser (not shown) and the like are provided within the machine room 117.

On the other hand, the process of inhaling the air of the refrigerating chamber 112 and freezing chamber 113 to the cooling chamber 116 through the refrigerating chamber return duct 111a and freezing chamber return duct 111b of the partition wall 111 by the blower fan 140 of the cooling chamber 116 to perform heat exchange with the evaporator 130, and discharging it to the refrigerating chamber 112 and freezing chamber 113 through the cool air discharge ports 150a of the cool air duct 150 again is repeatedly carried out. At this time, frost is formed on a surface of the evaporator 130 due to a temperature difference from circulation air reintroduced through the refrigerating chamber return duct 111a and the freezing chamber return duct 111b.

A defrosting device 170 is provided in the evaporator 130 to remove such frost, and water removed by the defrosting device 170, namely, defrost water, is collected to a lower defrost water tray (not shown) of the refrigerator body 110 through a defrost water discharge pipe 118.

Hereinafter, a new type of defrosting device 170 capable of reducing power consumption and enhancing heat exchange efficiency during defrost will be described.

FIGS. 2 and 3 are a front view and a perspective view illustrating a first embodiment of a defrosting device 170 applied to the refrigerator 100 in FIG. 1.

Referring to FIGS. 2 and 3, the evaporator 130 may include a cooling tube 131 (cooling pipe), a plurality of cooling fins 132, and support fixtures 133 at both sides.

The cooling tube 131 is repeatedly bent in a zigzag shape to constitute a plurality of columns, and refrigerant is filled therein. The cooling tube 131 may be formed in an aluminum material.

The cooling tube 131 may be configured in combination with horizontal pipe portions and bending pipe portions. The horizontal pipe portions are horizontally disposed to each other in a vertical direction, and configured to pass through the cooling fins 132, and the bending pipe portions connect an end portion of an upper horizontal pipe portion to an end portion of a lower horizontal pipe portion to communicate their inner portions with each other.

The cooling tube 131 is supported through the support fixture 133 provided at both sides of the evaporator 130. Here, the bending pipe portion of the cooling tube 131 is configured to connect an end portion of an upper horizontal pipe portion to an end portion of a lower horizontal pipe portion at an outer side of the support fixture 133.

Referring to FIG. 3, according to the present embodiment, it is seen that the cooling tube 131 is configured with a first cooling tube 131′ and a second cooling tube 131″ formed at a front portion and a rear portion of the evaporator 130, respectively, to constitute two columns For reference, the first cooling tube 131′ at a front side thereof and the second cooling tube 131″ at a rear side thereof are formed with the same shape, and thus the second cooling tube 131″ is hidden by the first cooling tube 131′ in FIG. 2.

However, the present disclosure may not be necessarily limited to this. The first cooling tube 131′ at a front side thereof and the second cooling tube 131″ at a rear side thereof may be formed in different shapes. On another hand, the cooling tube 131 may be formed to constitute a single column.

For the cooling tube 131, a plurality of cooling fins 132 are disposed to be separated at predetermined intervals along an extension direction of the cooling tube 131. The cooling fin 132 may be formed with a flat body made of an aluminum material, and the cooling tube 131 may be flared in the state of being inserted into an insertion hole of the cooling fin 132, and securely inserted into the insertion hole.

A plurality of support fixtures 133 may be provided at both sides of the evaporator 130, respectively, and each of which is configured to support the cooling tube 131 vertically extended and passed through along a vertical direction. An insertion groove or insertion hole to which a heat pipe 172 which will be described later can be inserted and fixed is formed on the support fixture 133.

The defrosting device 170 is provided in the evaporator 130 to remove frost generated from the evaporator 130. The defrosting device 170 may include a heating unit 171 and a heat pipe 172 (heat transfer tube).

The heating unit 171 is provided below the evaporator 130, electrically connected to the controller (not shown), and formed to generate heat upon receiving a drive signal from the controller. For example, the controller may be configured to apply a drive signal to the heating unit 171 for each predetermined time interval or apply a drive signal to the heating unit 171 when the sensed temperature of the cooling chamber 116 is less than a predetermined temperature.

The heat pipe 172 is connected to the heating unit 171 to form a closed loop shaped passage through which working fluid (F) can circulate along with the heating unit 171. The heat pipe 172 is formed of an aluminum material.

The heat pipe 172 may include a first heat pipe 172′ and a second heat pipe 172″ disposed to constitute two columns at a front and a rear portion of the evaporator 130. According to the present example, it is seen a structure in which the first heat pipe 172′ is disposed at a front side of the first cooling tube 131′, and the second heat pipe 172″ is disposed at a rear side of the second cooling tube 131″ to constitute two columns.

For the working fluid (F), refrigerant (for example, R-134a, R-600a, etc.) that exists in the liquid phase in a freezing condition of the refrigerator 100, but is phase-changed into the gas phase to perform the role of transferring heat when heated may be used.

FIG. 4 is an exploded perspective view illustrating an example of the heating unit 171 illustrated in FIG. 3, and FIG. 5 is a cross-sectional view in which the heating unit 171 illustrated in FIG. 4 is taken along a length direction, and FIG. 6 is a conceptual view illustrating the heater 171b illustrated in FIG. 4.

Referring to the present drawings along with the foregoing drawings, the heating unit 171 may include a heater case 171a and a heater 171b.

The heater case 171a has a hollow shape therein, and is connected to both end portions of the heat pipe 172, respectively, to form a closed loop shaped passage through which working fluid (F) can circulate along with the heat pipe 172. The heater case 171a may have a rectangular pillar shape, and formed of an aluminum material.

The heater case 171a may be disposed at one side of the evaporator 130 at which the accumulator 134 is located, the other side opposite the one side, or at any point between the one side and the other side.

The heater case 171a may be disposed adjacent to the lowest column of the cooling tube 131. For example, the heater case 171a may be disposed at the same height as the lowest column of the cooling tube 131 or disposed at a position lower than the lowest column of the cooling tube 131.

According to the present embodiment, it is shown that the heater case 171a is disposed in a horizontal direction of the evaporator 130 in parallel to the cooling tube 131 at a position lower than the lowest column of the cooling tube 131 at one side of the evaporator 130 at which the accumulator 134 is located.

The outlet 171c′, 171c″ and the inlet 171d′, 171d″ connected to both end portions of the heat pipe 172, respectively, are formed at both sides of the heater case 171a, respectively, in a length direction.

Specifically, the outlet 171c′, 171c″ communicated with one end portion of the heat pipe 172 is formed at one side of the heater case 171a (for example, an outer circumferential surface adjacent to a front end portion of the heater case 171a). The outlet 171c′, 171c″ denotes an opening through which working fluid (F) heated by the heater 171b is discharged to the heat pipe 172.

The inlet 171d′, 171d″ communicated with the other end portion of the heat pipe 172 is formed at the other side of the heater case 171a (for example, an outer circumferential surface adjacent to a rear end portion of the heater case 171a). The inlet 171d′, 171d″ denotes an opening through which condensed working fluid (F) is collected to the heater case 171a while passing through the heat pipe 172.

The heater 171b is attached to an outer surface of the heater case 171a, and configured to generate heat upon receiving a drive signal from the controller. Working fluid (F) within the heater case 171a receives heat due to the heater 171b to be heated at high temperatures.

The heater 171b is extended and formed along one direction, and has a shape of being attached to an outer surface of the heater case 171a and extended along a length direction of the heater case 171a. A plate-shaped heater (for example, a plate-shaped ceramic heater) having a plate shape is used for the heater 171b.

According the present embodiment, the heater case 171a is formed in a rectangular pipe shape in which a vacant space therein has a rectangular cross-sectional shape, and it is shown that a plate-shaped heater 171b is attached to a bottom surface of the heater case 171a. In this manner, the structure in which the heater 171b is attached to a bottom surface of the heater case 171a may be beneficial in generating a driving force in an upward direction on the heated working fluid (F), and defrost water generated due to the defrost operation may not directly fall onto the heater 171b, thereby preventing a short circuit.

A hot wire 171b2 (refer to FIG. 6) is formed on the heater 171b, and configured to generate heat while supplying power. As illustrated in FIG. 6, the heater case 171a is divided into an active heating part (AHP) corresponding to a portion on which the hot wire 171b2 is disposed and a passive heating part (PHP) corresponding to a portion on which the hot wire 171b2 is not disposed. The active heating part (AHP) and passive heating part (PHP) will be described later.

The heat pipe 172 and heater case 171a may be formed of the same type material (for example, aluminum material), and in this case, the heat pipe 172 may be directly connected to the outlet 171c′, 171c″ and the inlet 171d′, 171d″ of the heater case 171a.

For reference, when the heater 171b is configured with a cartridge type and mounted within the heater case 171a, the heater case 171a with a copper material other than an aluminum material will be used to bond and seal between the heater 171b and the heater case 171a.

In this manner, when the heat pipe 172 and the heater case 171a are formed of different types of materials (as described above, when the heat pipe 172 is formed of an aluminum material, and the heater case 171a is formed of a copper material), it is difficult to directly connect the heat pipe 172 to the outlet 171c′, 171c″ and the inlet 171d′, 171d″ of the heater case 171a. Accordingly, for the connection between them, an outlet tube is extended and fanned to the outlet 171c′, 171c″ of the heater case 171a, and a return tube is extended and formed to the inlet 171d′, 171d″ to connect the heat pipe 172 to the outlet tube and the return tube, and thus the bonding and sealing process is required for the procedure.

However, according to a structure in which the heater 171b is attached to an outer surface of the heater case 171a, the heater case 171a may be formed of the same material as that of the heat pipe 172, and the heat pipe 172 may be directly connected to the outlet 171c′, 171c″ and the inlet 171d′, 171d″ of the heater case 171a.

On the other hand, as working fluid (F) filled into the heater case 171a is heated to high temperatures by the heater 171b, the working fluid (F) flows due to a pressure difference to move the heat pipe 172. Specifically, the working fluid (F) at high temperatures heated by the heater 171b and discharged to the outlet 171c′, 171c″ transfers heat to the cooling tube 131 of the evaporator 130 while moving through the heat pipe 172. The working fluid (F) is gradually cooled while passing through the heat exchange process and introduced into the inlet 171d′, 171d″. The cooled working fluid (F) is reheated by the heater 171b and then discharged to the outlet 171c′, 171c″ again to repeatedly perform the foregoing processes. The defrosting of the cooling tube 131 is carried out due to such a circulation method.

Referring to FIGS. 2 and 3, at least part of the heat pipe 172 is disposed adjacent to the cooling tube 131 of the evaporator 130, and configured to transfer heat to the cooling tube 131 of the evaporator 130 due to high-temperature working fluid (F) heated and transferred by the heating unit 171 to remove frost.

The heat pipe 172 may have a shape of being repeatedly bent (a zigzag shape) similarly to the cooling tube 131. To this end, the heat pipe 172 may include an extension portion 172a and a heat emitting part 172b.

The extension portion 172a faults a passage for transferring working fluid (F) heated by the heating unit 171 in an upward direction of the evaporator 130. The extension portion 172a is connected to an outlet 171c′, 171c″ of the heater case 171a provided below the evaporator 130 and the heat emitting part 172b provided on the evaporator 130.

The extension portion 172a may include a vertical extension portion extended in an upward direction of the evaporator 130. The vertical extension portion is extended up to an upper portion of the evaporator 130 in the state of being disposed to be separated from the support fixture 133 at an outer side of the support fixture 133 provided at one side of the evaporator 130.

On the other hand, the extension portion 172a may further include a horizontal extension portion according to the installation position of the heating unit 171. For an example, when the heating unit 171 is provided at a position separated from the vertical extension portion (refer to FIG. 20), a horizontal extension portion for connecting the heating unit 171 to the vertical extension portion may be additionally provided.

When the horizontal extension portion is connected to the heating unit 171 and extended in an elongated manner, high-temperature working fluid (F) may pass through a lower portion of the evaporator 130, thereby having an advantage of efficiently implementing a defrost operation on the cooling tube 131 at a lower side of the evaporator 130.

The heat emitting part 172b is connected to the extension portion 172a extended to an upper portion of the evaporator 130, and extended in a zigzag shape along the cooling tube 131 of the evaporator 130. The heat emitting part 172b is configured in combination with a plurality of horizontal tubes 172b′ constituting columns and a connecting tube 172b″ formed in a bent U-shaped tube to connect them in a zigzag shape.

The extension portion 172a or heat emitting part 172b may be extended up to a position adjacent to an accumulator 134 to remove frost formed on the accumulator 134.

As illustrated in the drawing, when the vertical extension portion is disposed at one side of the evaporator 130 at which the accumulator 134 is located, the vertical extension portion may be extended upward to a position adjacent to the accumulator 134, and then bent and extended downward toward the cooling tube 131 to be connected to the heat emitting part 172b.

On the contrary, when the vertical extension portion is disposed at the other side opposite to the one side, the heat emitting part 172b may be connected to the vertical extension portion and extended in a horizontal direction, and then extended upward toward the accumulator 134, and then extended downward again to correspond to the cooling tube 131.

For the heat pipe 172, a portion connected to the outlet 171c′, 171c″ of the heater case 171a constitutes an entrance portion 172c′, 172c″ for introducing high-temperature working fluid (F), and a portion connected to the inlet 171d′, 171d″ of the heater case 171a constitutes a return portion 172d′, 172d″ for returning the cooled working fluid (F).

According to the present embodiment, working fluid (F) heated by the heater 171b forms a circulation loop in which the working fluid (F) is discharged to the entrance portion 172c′, 172c″ and transferred to an upper portion of the evaporator 130 through the extension portion 172a, and then heat is transferred to the cooling tube 131 while flowing along the heat emitting part 172b to perform a defrost operation, and then the working fluid (F) is returned through the return portion 172d′, 172d″, and reheated by the heater 171b again to flow the heat pipe 172.

According to a structure in which the heat pipe 172 is configured with the first and the second heat pipe 172′, 172″, the first and the second heat pipe 172′, 172″ are connected to the inlet 171d′, 171d″ and the outlet 171c′, 171c″ of the heating unit 171, respectively.

Specifically, the outlet 171c′, 171c″ of the heating unit 171 is configured with a first outlet 171c′ and a second outlet 171c″, and one end portion of the first and the second heat pipe 172′, 172″, respectively, is connected to the first and the second outlet 171c′, 171c″, respectively. Due to the foregoing connection structure, working fluid (F) in the gas phase heated by the heating unit 171 is discharged to the first and the second heat pipe 172′, 172″, respectively, through the first and the second outlet 171c′, 171c″.

The first and the second outlet 171c′, 171c″ may be formed at both sides of an outer circumference of the heater case 171a, respectively, and formed in parallel at a front portion of the heater case 171a.

It may be understood that one end portion of the first and the second heat pipe 172′, 172″ connected to the first and the second outlet 171c′, 171c″, respectively, is the first and the second entrance portions 172c′, 172c″ (a portion to which working fluid (F) at high temperatures heated by the heater 171b is introduced) due to the function.

Furthermore, the inlet 171d′, 171d″ of the heating unit 171 is configured with a first inlet 171d′ and a second inlet 171d″, and the other end of the first and the second heat pipe 172′, 172″, respectively, is connected to the inlet 171d′, 171d″, respectively. Due to the connection structure, working fluid (F) in the liquid phase cooled while moving the heat pipes 172, respectively, is introduced into the heater case 171a through the first and the second inlet 171d′, 171d″.

The first and the second inlet 171d′, 171d″ may be formed at both sides of an outer circumference of the heater case 171a, respectively, and Ruined in parallel at a rear portion of the heater case 171a.

It may be understood that the other end portion of the first and the second heat pipe 172′, 172″ connected to the inlet 171d′, 171d″, respectively, is the first and the second return portions 172d′, 172d″ (a portion to which working fluid (F) in the liquid phase cooled while moving through the heat pipes 172, respectively, is collected) due to the function.

On the other hand, referring to FIGS. 4 and 5, the outlet 171c′, 171c″ of the heater case 171a may be formed at a position separated by a predetermined distance from a front end of the heater case 171a in a backward direction. In other words, it may be understood that the front end portion of the heater case 171a is protruded and formed in a forward direction from the outlet 171c′, 171c″.

The hot wire 171b2 of the heater 171b may be extended and formed from one point between the inlet 171d′, 171d″ and the outlet 171c′, 171c″ to a position passed through the outlet 171c′, 171c″. According to this, the outlet 171c′, 171c″ of the heater case 171a is located within the active heating part (AHP).

Due to the foregoing structure, part of working fluid (F) stays at a front end portion (a space between an inner front end and the outlet 171c′, 171c″ of the heater case 171a) to prevent the overheating of the heater 171b.

Specifically, working fluid (F) heated by the active heating part (AHP) moves in a direction through which the working fluid (F) circulates, namely, toward a front end portion of the heater case 171a, and during this process, part of the working fluid (F) is discharged to the branched outlet 171c′, 171c″, but the remaining working fluid passes through the outlet 171c′, 171c″ and stays while forming a vortex at a front end portion of the heater case 171a.

In this manner, the whole of the heated working fluid (F) is not immediately discharged to the outlet 171c′, 171c″, but part thereof stays within the heater case 171a without being immediately discharged to the outlet 171c′, 171c″, thereby further preventing the overheating of the heater 171b.

On the other hand, the heat pipe 172 may be accommodated between a plurality of cooling fins 132 fixed to each column of the cooling tube 131. According to the foregoing structure, the heat pipe 172 is disposed between each column of the cooling tube 131. Here, the heat pipe 172 may be configured to make contact with the cooling fin 132.

However, the present disclosure may not be necessarily limited to this. For an example, the heat pipe 172 may be provided to pass through a plurality of cooling fins 132. In other words, the heat pipe 172 may be flared in the state of being inserted into an insertion hole of the cooling fin 132, and securely inserted into the insertion hole. According to the foregoing structure, the heat pipe 172 is disposed to correspond to the cooling tube 131.

As described above, the heater 171b applied to the heating unit 171 of the present disclosure may be formed in a plate shape, and a plate-shaped ceramic heater 171b may be typically used.

As illustrated in FIG. 6, the heater 171b may include a base plate 171b1, a hot wire 171b2 and a terminal 171b3.

The base plate 171b1 is formed of a ceramic material, and formed in a plate shape extended in an elongated manner along one direction. The base plate 171b1 is attached to an outer surface of the heater case 171a, and disposed along a length direction of the heater case 171a.

The hot wire 171b2 is formed on the base plate 171b1, and the hot wire 171b2 is configured to emit heat during the application of power. In a state that the base plate 171b1 is attached to an outer surface of the heater case 171a, the hot wire 171b2 has a shape of being extended from one point between the inlet 171d′, 171d″ and the outlet 171c′, 171c″ toward the outlet 171c′, 171c″.

The hot wire 171b2 may be formed by patterning a resistor *for example, powder mixed with ruthenium and platinum, tungsten, etc.) on the base plate 171b1 with a specific pattern. The hot wire 171b2 may be extended and formed along a length direction of the base plate 171b1.

A terminal 171b3 configured to electrically connect the hot wire 171b2 to power is provided at one side of the base plate 171b1, and a lead wire 173 electrically connected to the power is connected to the terminal 171b3.

On the other hand, the heater case 171a is divided into an active heating part (AHP) corresponding to a portion on which the hot wire 171b2 is disposed and a passive heating part (PHP) corresponding to a portion on which the hot wire 171b2 is not disposed.

The active heating part (AHP) is a portion directly heated by the hot wire 171b2, and working fluid (F) at the liquid phase is heated by the active heating part (AHP) and phase-changed into the gas phase at high temperatures.

The outlet 171c′, 171c″ of the heater case 171a may be located within the active heating part (AHP) or located at a front side than the active heating part (AHP). In FIG. 6, it is illustrated that a portion formed with the hot wire 171b2 of the heater 171b is extended and formed in a forward direction through a lower portion of the outlet 171c′, 171c″ formed on an outer circumference of the heater case 171a. In other words, according to the present embodiment, the outlet 171c′, 171c″ of the heater case 171a is located within the active heating part (AHP).

The passive heating part (PHP) is formed at a rear side of the active heating part (AHP). The passive heating part (PHP) indirectly receives heat to be heated to a predetermined temperature level though it is not a portion directly heated by the hot wire 171b2 like the active heating part (AHP). Here, the passive heating part causes a predetermined temperature increase to the working fluid (F) in the liquid phase, but does not have high temperatures to the extent of phase-changing the working fluid (F) to the gas phase.

In other words, in the aspect of temperature, the active heating part (AHP) forms a relatively high-temperature portion and the passive heating part forms a relatively low-temperature portion.

If working fluid (F) is configured to directly return to a side of the active heating part (AHP) at high temperatures, then it may occur a case where the collected working fluid (F) is reheated and flowed backward without being efficiently returned into the heater case 171a. It may be an obstacle to the circulation flow of the working fluid (F) within the heat pipe 172, thereby causing a problem of overheating the heater 171b.

In order to solve the foregoing problem, it is configured such that the inlet 171d′, 171d″ of the heating unit 171 is formed to correspond to the passive heating part (PHP) not to allow working fluid (F) that has moved through the heat pipe 172 and then returned to be immediately introduced into the active heating part (AHP).

According to the present embodiment, it is configured that the inlet 171d′, 171d″ of the heating unit 171 is located within the passive heating part (PHP) to allow working fluid (F) that has moved through the heat pipe 172 and then returned to be introduced into the passive heating part (PHP). In other words, the inlet 171d′, 171d″ of the heating unit 171 is formed at a portion on which the hot wire 171b2 is not disposed on the heater case 171a.

As described above, the passive heating part (PHP) is associated with the formation location of the hot wire 171b2. Accordingly, if the hot wire 171b2 is not extended and formed up to the inlet 171d′, 171d″ of the heating unit 171, then the base plate 171b 1 of the heater 171b may be extended and formed up to a portion corresponding to the inlet 171d′, 171d″. In other words, the base plate 171b1 may be disposed to cover the most bottom surface of the heater case 171a, and the hot wire 171b2 may be formed at a position out of the inlet 171d′, 171d″, thereby preventing working fluid (F) returned through the inlet 171d′, 171d″ from flowing backward.

Hereinafter, the detailed structure of the heater case 171a and the coupling structure between the heater case 171a and the heater 171b will be described in more detail.

The heater case 171a may include a main case 171a1, a first cover 171a2 and a second cover 171a3 coupled to both sides of the main case 171a1, respectively.

The main case 171a1 is provided with a vacant space therein, and has a shape in which both end portions thereof are open. The main case 171a1 may be formed of an aluminum material. In FIG. 5, it is illustrated the main case 171a1 in a rectangular pillar shape in which a vacant space therein having a rectangular cross-sectional shape is extended and formed in an elongated manner along one direction.

The first and the second cover 171a2, 171a3 are mounted at both sides of the main case 171a1 to cover both end portions of the main case 171a1 that are open. The first and the second cover 171a2, 171a3 may be formed of an aluminum material like the main case 171a1.

According to the present embodiment, it is shown a structure in which the outlet 171c′, 171c″ and the inlet 171d′, 171d″ are provided at positions separated from each other along a length direction of the main case 171a1, respectively, and the both end portions (the entrance portion 172c′, 172c″ connected to the outlet 171c′, 171c″ and the return portion 172d′, 172d″ connected to the inlet 171d′, 171d″) of the heat pipe 172 are connected to the outlet 171c′, 171c″ and the inlet 171d′, 171d″.

More specifically, the first outlet 171c′ and the first inlet 171d′ are formed at positions separated from each other along a length direction on one lateral surface of the main case 171a1, and the second outlet 171c″ and the second inlet 171d″ are formed at positions separated from each other along a length direction on the other lateral surface facing the one surface. Here, the first outlet 171c′ and the second outlet 171c″ may be disposed to face each other, and the first inlet 171d′ and the second inlet 171d″ may be disposed to face each other.

However, the present disclosure may not be necessarily limited to this. At least one of the inlet 171d′, 171d″ and the outlet 171c′, 171c″ may be formed on a first and/or a second cover 171a2, 171a3. A structure associated therewith will be described in more detail later.

On the other hand, the heating unit 171 is provided below the evaporator 130, and thus defrost water generated due to defrosting in the aspect of the structure may flow down to the heating unit 171. The heater 171b provided in the heating unit 171 is an electronic component, and thus when defrost water is brought into contact with the heater 171b, it may cause a short circuit. As described above, the heating unit 171 of the present disclosure may include the following sealing structure to prevent moisture including defrost water from infiltrating into the heater 171b.

First, the heater 171b is attached to a bottom surface of the main case 171a1, and a first and a second extension pin 171a1a, 171a1b extended and formed in a downward direction from the bottom surface to cover a lateral surface of the heater 171b attached to the bottom surface are configured at both sides of the main case 171a1. Due to the structure, even when defrost water generated due to defrosting falls onto the main case 171a1 and flows down along an outer surface of the main case 171a1, the defrost water does not infiltrate into the heater 171b accommodated at an inner side of the first and the second extension pin 171a1a, 171a1b.

Furthermore, a sealing member 171e may be filled into a recessed space 171a1′ formed by a rear surface of the heater 171b and the first and the second extension pin 171a1a, 171a1b as described above. Silicon, urethane, epoxy or the like may be used for the sealing member 171e. For example, epoxy in the liquid phase may be filled into the recessed space 171a1′ and then subject to the curing process to complete the sealing structure of the heater 171b. Here, the first and the second extension pin 171a1a, 171a1b may function as a sidewall limiting the recessed space 171a1′ into which the sealing member 171e is filled.

An insulating material 171f may be interposed between a rear surface of the heater 171b and the sealing member 171e. A mica sheet with a mica material may be used for the insulating material 171f. The insulating material 171f may be disposed on a rear surface of the heater 171b, thereby limiting heat from being transferred to a side of the rear surface of the heater 171b when the hot wire 171b2 emits heat according to the application of power.

Moreover, a thermally conductive adhesive 171g may be interposed between the main case 171a1 and the heater 171b. The thermally conductive adhesive 171g may attach the heater 171b to the main case 171a1 to perform the role of transferring heat generated from the heater 171b to the main case 171a1. A heat-resistant silicone capable of enduring high temperatures may be used for the thermally conductive adhesive 171g.

On the other hand, at least one of the first and the second cover 171a2, 171a3 may be extended and formed from the bottom of the main case 171a1 in a downward direction to surround the heater 171b along with the first and the second extension pin 171a1a, 171a1b. Due to the structure, the filling of the sealing member 171e may be more easily carried out.

However, considering a structure in which the lead wire 173 connected to the terminal 171b3 of the heater 171b is extended from one side of the heater case 171a to an outside, a cover corresponding to one side of the heater case 171a on the first and the second cover 171a2, 171a3 may not be extended and formed in a downward direction or may be provided with a groove or hole allowing the lead wire 173 to pass therethrough even when extended and formed in a downward direction.

According to the present embodiment, it is shown that the second cover 171a3 is extended and formed from the bottom surface of the main case 171a1 in a downward direction, and the lead wire 173 is extended and formed to a side of the first cover 171a2.

FIGS. 7 through 9 are exploded perspective views illustrating examples in which the formation positions of an outlet 171c′, 171c″ and an inlet 171d′, 171d″ are modified in the heating unit 171 illustrated in FIG. 4. The modified example is merely different from the foregoing embodiment in only the formation positions of the outlet 171c′, 171c″ and/or inlet 171d′, 171d″, and the configurations of the foregoing embodiment may be applied in a similar manner to other configurations.

First, referring to FIG. 7, an inlet and an outlet of a heating unit 271 may be formed on a first and a second cover 271a2, 271a3, respectively. Specifically, a first and a second outlet of the heating unit 271 may be formed together on the first cover 271a2, and a first and a second entrance portion 272c′, 272c″ connected to the first and the second outlet, respectively, may be disposed in parallel. Furthermore, the first and the second inlet of the heating unit 271 may be formed together on the second cover 271a3, and a first and a second return portion 272d′, 272d″ connected to the first and the second inlet, respectively, may be disposed in parallel.

As described above, the outlet and inlet of the heating unit 271 may be formed on both lateral surfaces of a main case 271a1, and formed on the first and the second cover 271a2, 271a3. In addition, a combination of the foregoing structures is also possible.

For an example, as illustrated in FIG. 8, an outlet of a heating unit 371 may be formed on a main case 371a1, and an inlet of the heating unit 371 may be formed on a second cover 371a1. Specifically, a first and a second outlet of the heating unit 371 may be formed on both lateral surfaces of the main case 371a1 to face each other. Furthermore, a first and a second inlet of the heating unit 371 may be formed together, and a first and a second return portion 372d′, 372d″connected to the first and the second inlet, respectively, may be disposed in parallel.

For another example, as illustrated in FIG. 9, an outlet of a heating unit 471 may be formed on a main case 471a1. Specifically, a first and a second inlet of the heating unit 471 may be formed together on a second cover 471a3, and a first and a second entrance portion 472c′, 472″ connected to the first and the second outlet, respectively, may be disposed in parallel. Furthermore, a first and a second outlet of the heating unit 471 may be formed on both lateral surfaces of the main case 471a1 to face each other.

FIGS. 10 and 11 are conceptual views for explaining the circulation of working fluid (F) in a state prior to or subsequent to the operation of the heater 171b.

First, referring to FIG. 10, prior to the operation of the heater 171b, working fluid (F) is present in a liquid phase, and filled up to a preset column of the top based on the lowest column of the heat pipe 172. For an example, the working fluid (F) in this state may be filled up to the lower two columns of the heat pipe 172.

When the heater 171b is operated, working fluid (F) within the heater case 171a is heated by the heater 171b. Referring to FIG. 11, working fluid heated in a high-temperature gas phase (F1) is introduced into the entrance portion 172c′, 172c″ of the heat pipe 172 to dissipate heat to the cooling tube 131 while flowing through the heat pipe 172. The working fluid (F) flows in a phase (F2) that liquid and gas coexist while losing heat during the heat dissipation process, and is finally introduced into the heating unit 171 through the return portion 172d′, 172d″ of the heat pipe 172 in a liquid phase (F3). The working fluid (F) introduced into the heating unit 171 is heated again by the heater 171b to repeat (circulate) the foregoing flow, and transfer heat to the evaporator 130 during the process, thereby removing frost formed on the evaporator 130.

As described above, working fluid (F) flows by a pressure difference generated by the heating unit 171 to quickly circulate the heat pipe 172, and thus the entire section of the heat pipe 172 may reach a stable operating temperature within a short period of time, thereby quickly carrying out defrosting.

On the other hand, working fluid (F) introduced into the entrance portion 172c′, 172c″ is in a high-temperature gas phase (F1) and has the highest temperature during the circulation process of the heat pipe 172. Accordingly, the convection of heat due to working fluid (F) in such a high-temperature gas phase (F1) may be used to more efficiently remove frost formed on the evaporator 130.

For an example, the entrance portion 172c′, 172c″ may be disposed at a relatively lower position than that of the lowest column of the cooling tube 131 provided in the evaporator 130 or at the same position as that of the lowest column. Accordingly, high-temperature working fluid (F) introduced through the entrance portion 172c′, 172c″ may transfer heat in the vicinity of the lowest column of the cooling tube 131 as well as such heat is increased and transferred to the cooling tube 131 adjacent to the lowest column.

On the other hand, in order to allow working fluid (F) to circulate the heat pipe 172 while carrying out such a phase change, an appropriate amount of the working fluid (F) should be filled into the heat pipe 172.

As a result of experiment, it is seen that the temperature of the heating unit 171 rapidly increases according to the passage of time when working fluid (F) less than 30% compared to the entire internal volume of the heat pipe 172 and heater case 171a is filled. It denotes that working fluid (F) is insufficient compared to the entire internal volume of the heat pipe 172 and heater case 171a.

Furthermore, it is seen that the temperature of partial heat of the heat pipe 172 does not reach a stable operating temperature (less than 50° (freezing condition)) when working fluid (F) greater than 40% compared to the entire internal volume of the heat pipe 172 and heater case 171a is filled. Such a temperature decrease will be apparent as the heat pipe 172 is located closer to the return portion 172d′, 172d″. It denotes that working fluid (F) compared to the entire internal volume of the heat pipe 172 and heater case 171a is excessive to increase a section in which working fluid (F) flows in a liquid phase.

It is seen that the temperature of the heating unit 171 and the temperature of each column of the heat pipe 172 reaches a stable operating temperature according to the passage of time when working fluid (F) greater than 30% but less than 40% compared to the entire internal volume of the heat pipe 172 and heater case 171a is filled.

Here, it is shown that the temperature of each column of the heat pipe 172 exhibits higher temperature as closer to the entrance portion 172c′, 172c″, and exhibits lower temperature as closer to the return portion 172d′, 172d″. As an amount of filled working fluid (F) decreases, a difference between the temperature (maximum temperature) on the entrance portion 172c′, 172c″ and the temperature (minimum temperature) on the return portion 172d′, 172d″ decreases.

Accordingly, working fluid (F) greater than 30% but less than 40% compared to the entire internal volume of the heat pipe 172 and heater case 171a may be filled, but an optimized filling amount of working fluid (F) may be chosen for each defrosting device 170.

On the other hand, according to the structure in which the heater 171b is attached to an outer surface of the heater case 171a, a structure of enhancing the heat transfer performance of the heater 171b to the heater case 171a as well as preventing the overheating of the heater 171b may preferably taken into consideration. Hereinafter, the heating unit 171 in consideration of such items will be described.

FIG. 12 is a cross-sectional view in which another example 571 of the heating unit 171 illustrated in FIG. 3 is taken along a width direction.

Referring to FIG. 12, an outer fin 571a1c for the heat dissipation of the heater case is protruded and formed on an outer surface of the heater case. The outer fin 571a1c may be integrally formed on the heater case as a protruded configuration during the fabrication of the heater case (for example, extrusion molding of aluminum) or attached to the heater case by welding, an adhesive or the like as an additional configuration.

When the outer fin 571a1c is formed on an outer surface of the heater case as described above, an outer area of the heater case increases compared to a structure in which the outer fin 571a1c is not formed. As a result, it may be possible to enhance heat exchange efficiency between ambient low-temperature air and the heater case.

According to the foregoing structure, a significant amount of heat generated from a heater 571b may be transferred to the heater case at a front side (in an upward direction of the present drawing) of the heater 571b [heat transfer to a rear side of the heater 571b relatively decreases), thereby preventing the overheating of the heater 571b. Furthermore, a rear temperature of the heater 571b is reduced to enhance the reliability and lifespan of the heater 571b. Moreover, heat transfer to a sealing member 571e provided at a rear side of the heater 571b decreases to prevent the melting of the sealing member 571e.

Hereinafter, the containment of the outer fin 571a1c will be described in more detail.

As illustrated in the drawing, the outer fin 571a1c may be formed on an upper surface of a main case 571a1. A plurality of outer fins 571a1c may be provided thereon, and extended and formed along a length or width direction of the main case 571a1 with a predetermined separation distance from each other. According to the present embodiment, it is seen that the outer fin 571a1c is extended and formed along a length direction of the main case 571a1.

A separation distance between the plurality of outer fins 571a1c may be formed to be the same as a width of the outer fin 571a1c or to be larger than the width of the outer fin 571a1c. It is because a heat dissipation effect due to the outer fin 571a1c is not so large compared to a structure in which the outer fin 571a1c is not formed when the separation distance between the plurality of outer fins 571a1c is smaller than the width of the outer fin 571a1c.

In a structure in which the heater 571b is attached to a bottom surface of the main case 571a1, a significant amount of heat generated from the heater 571b is transferred to the main case 571a1 at a front side of the heater 571b by the outer fin 571a1c formed at an upper portion of the main case 571a1. Due to such heat transfer, it may be possible to prevent the overheating of the heater 571b as well as transfer a larger amount of heat to working fluid (F) within the main case 571a1 during the heat transfer process. In other words, the enhancement of heat transfer efficiency is accomplished.

On the other hand, when working fluid (F) is all in a liquid phase, it is configured such that the working fluid (F) is completely filled into a vacant space within the main case 571a1 to transfer the maximum amount of heat to the working fluid (F). It may be satisfied as described above in case where the heater case is provided at a lower portion of the evaporator 130, and working fluid (F) greater than 30% but less than 40% compared to the entire internal volume of the heat pipe and heater case is filled.

FIGS. 13 and 14 are conceptual views illustrating examples in which the shape of outer fins 571a1c is modified in the heating unit 571 illustrated in FIG. 12.

First, referring to FIG. 13, an outer fin 671a1c may be formed on an upper surface of a main case 671a1 as well as another outer surface thereof.

For an example, the outer fin 671a1c may be protruded and formed on both outer surfaces of the main case 671a1, respectively. However, when an outlet 671c′, 671c″ and an inlet 671d′, 671d″ of a heating unit 671 are formed on both lateral surfaces of the main case 671a1, the outer fin 671a1c may be formed in an elongated manner between the outlet 671c′, 671c″ and the inlet 671d′, 671d″.

For another example, the outer fin 671a1c may be also protruded and formed on an outer surface of at least one of a first and a second cover 671a2, 671a3. However, when the outer fin 671a1c is formed on a cover corresponding to one of the outlet 671c′, 671c″ and inlet 671d′, 671d″ of the heating unit 671, the outer fin 671a1c may be protruded and formed on an outer surface of at least one cover on which the outlet 671c′, 671c″ and inlet 671d′, 671d″ are not formed between the first and the second cover 671a2, 671a3.

Next, an outer fin 771a1c may be protruded and formed in a protrusion shape on an outer surface of a heater case 771a.

For an example, as illustrated in FIG. 14, a plurality of outer fins 771a1c are provided, and disposed along a length and a width direction of a main case 771a1 with a predetermined separation distance from each other. Accordingly, the plurality of outer fins 771a1c may be disposed to form a matrix.

For another example, a plurality of outer fins 771a1c are provided to have a protruded shape on an outer surface of the main case 771a1.

According to the foregoing structure, an outer area of the heater case due to outer fins may be further increased. As a result, it may be possible to further enhance heat exchange efficiency between ambient low-temperature air and the heater case, and further enhance the reliability and lifespan of the heater due to the overheating prevention of the heater.

On the other hand, in the aspect of a configuration in which the foregoing first and second extension fins are also protruded and formed on the heater case, they may be understood as a type of outer fins. Accordingly, the above-mentioned effect may be also accomplished by the first and the second extension fins.

FIGS. 15 and 16 are cross-sectional views in which still another example 871 of the heating unit 171 illustrated in FIG. 3 is taken along a width and a length direction.

Referring to FIGS. 15 and 16, an inner fin 871af1 for enhancing the heat transfer performance of a heater 871b is protruded and formed within the heater case. The inner fin 871af1 may be integrally formed on the heater case as a protruded configuration during the fabrication of the heater case (for example, extrusion molding of aluminum) or attached to the heater case by welding, an adhesive or the like as an additional configuration.

When the inner fin 871af1 is formed within the heater case as described above, a contact area to working fluid (F) filled into the heater case may increase, thereby increasing a heat transfer rate of being transferred from the heater 871b to working fluid (F). Furthermore, the entire volume of the heater case may increase to increase heat capacity capable of receiving heat from the heater case, thereby receiving more heat generated from the heater 871b. As a result, it may be possible to enhance defrosting performance.

Moreover, a significant amount of heat generated from a heater 871b may be transferred to the heater case at a front side (in an upward direction of the present drawing) of the heater 871b [heat transfer to a rear side of the heater 871b relatively decreases), thereby preventing the overheating of the heater 871b. Furthermore, a rear temperature of the heater 871b is reduced to enhance the reliability and lifespan of the heater 871b. Moreover, heat transfer to a sealing member 871e provided at a rear side of the heater 871b decreases to prevent the melting of the sealing member 871e.

Hereinafter, the configuration of the inner fin 871af1 will be described in more detail.

As illustrated in the drawing, the inner fin 871af1 is protruded and formed on an inner surface at an inner side of an outer surface to which the heater 871b is attached on the main case 871a1. According to the present drawing, it is seen that the heater 871b is attached to an outer bottom surface of the main case 871a1, and the inner fin 871af1 is protruded and formed on an inner bottom surface of the main case 871a1.

The inner fin 871af1 is preferably protruded and formed at a length less than ½ compared to an inner height of the main case 871a1. When the inner fin 871af1 is protruded and formed at a length larger than ½ compared to an inner height of the main case 871a1, it may prevent working fluid (F) from efficiently flowing.

A plurality of inner fins 871af1 may be provided, and extended and formed along a length or width direction of the main case 871a1 with a predetermined separation distance from each other. According to the present embodiment, it is seen that the inner fin 871af1 is extended and formed along a length direction of the main case 871a1. In case of having a structure in which the inner fin 871af1 is integrally formed with the main case 871a1 by the extrusion molding of the main case 871a1, it has a structure in which the inner fin 871af1 is extended and formed along a length direction of the main case 871a1.

Here, a separation distance between each other of the plurality of inner fins 871af1 is preferably set to be above one time compared to a width of the inner fin 871af1 . It is because flowing between the plurality of inner fins 871af1 is significantly reduced when the separation distance between each other of the plurality of inner fins 871af1 is less than the width of the inner fin 871af1 . Furthermore, a separation distance between each other of the plurality of inner fins 871af1 may be preferably set to be less than two times compared to the width of the width of the inner fin 871af1 such that a lot of inner fins 871af1 are provided within the main case 871a1 to obtain an effect due to the formation of the inner fin 871af1 at a satisfactory level.

In this viewpoint, a distance from an inner wall of the main case 871a1 and the inner fin 871af1 adjacent to the inner wall may be also preferably set to be greater than one time but less than two times compared to the width of the inner fin 871af1 .

Hereinafter, a structure capable of obtaining the effect due to the inner fin at a satisfactory level as well as efficiently discharging working fluid from the heater case while introducing working fluid to the heater case will be described.

FIG. 17 is a cross-sectional view illustrating an example in which the formation positions of inner fins 971a1 are modified in the heating unit 971 illustrated in FIG. 16.

According to the foregoing embodiment, it is shown a structure in which the inner fin 871af1 is extended and formed along a length direction of the main case 871a1 from one end of the main case 871a1 up to the other end thereof. As illustrated in FIG. 16, in a structure in which an outlet 871c″ (an outlet at an opposite side is not shown) and an inlet 871d″ (an inlet at an opposite side is not shown) are formed at positions separated from each other, respectively, with a predetermined distance along a length direction of the main case 871a1 on both lateral surfaces of the main case 871a1, the inner fin 871af1 is protruded and formed up to a height at which the inlet 871d″ and outlet 871c″ are formed. Accordingly, as illustrated in FIG. 16, the inner fin 871af1 is disposed to cover part of the outlet 871c″ and inlet 871d″ with a separation distance along a width direction of the main case 871a1.

The structure does not have a large effect on working fluid (F) discharged from the outlet 871c″ and collected through the inlet 871d″ but have some effect thereon in actuality when the inner fin 871af1 is protruded and formed at a length less than ½ compared to an inner height of the main case 871a1, and a distance between an inner wall of the main case 871a1 and the inner fin 871af1 adjacent to the inner wall is formed to be greater than one time compared to a width of the inner fin 871af1.

In order to improve this, according to the present modified example, it is seen that an inner fin 971a1f protruded and formed from an inner bottom surface of a main case 971a1 is formed between an inlet 971d″ (an inlet at an opposite side is not shown) and an outlet 971c″ (an outlet at an opposite side is not shown). According to the above-mentioned structure, the inner fin 971a1 f does not cover the outlet 971c″ and inlet 971d″ of the main case 971a1 along a width direction of the main case 971a1. Accordingly, working fluid (F) may be efficiently collected through the inlet 971d″, and the collected working fluid (F) receive more heat due to the inner fin 971a1f when heated again by the heater 971b while flowing forward, and the reheated working fluid (F) may be efficiently discharged through the outlet 971c″.

FIG. 18 is a cross-sectional view illustrating yet still another example 1071 of the heating unit 171 illustrated in FIG. 3.

A structure illustrated in FIG. 18 may be understood in combination of structures associated with the foregoing outer fins and inner fins. In other words, an outer fin 1071a1c for the heat dissipation of a main case 1071a1 is protruded and formed on an outer surface of the main case 1071a1, and an inner fin 1071a1f for the heat transfer performance enhancement of a heater 1071b is protruded and formed within the main case 1071a1.

The structures of the foregoing embodiments may be all applicable to the structure of the present example. The redundant description thereof will be omitted.

On the other hand, when the heater 171b is driven, the removal of frost formed on the evaporator 130 is started. Specifically, working fluid (F) is heated by the heater 171b to flow through the heat pipe 172, and heat dissipation is carried out on the cooling tube 131 of the evaporator 130 during the process to melt frost or ice formed on the cooling tube 131. The frost or ice is converted into water, namely, defrost water, due to defrosting, and falls onto the bottom of the evaporator 130, and according to circumstances, defrost water may fall even on the heating unit 171 provided at a lower portion of the evaporator 130.

The hot wire 171b2 and terminal 171b3 of the heater 171b, and the lead wire 173 connected to the terminal 171b3 are configured to include a conductor, and thus there is a possibility of causing a short circuit when brought into contact with defrost water. As described above, it may be possible to prevent a contact between the heater 171b and defrost water at a predetermined level according to a structure in which the heater 171b is attached to a bottom surface of the heater case 171a, a structure in which the sealing member 171e is disposed to cover the heater 171b, and a structure in which the first and the second extension fin 171a1a, 171a1b are protruded and formed at both sides of the heater case 171a to accommodate the heater 171b.

However, the lead wire 173 has a shape of being exposed and extended to an outside of the heater case 171a. Due to such configuration characteristics, when defrost water flowed down to the lead wire 173 is cooled subsequent to defrosting and converted into frost or ice, the resultant weight increase may have an effect on contact with the terminal 171b3 or part of defrost water may flow to the side of the heater 171b or power along the lead wire 173 to cause a short circuit.

Hereinafter, a connection structure of the lead wire 173 according to the position of the heating unit 171 for preventing the foregoing problem will be described with reference to FIGS. 19 and 20.

The heating unit 171 is disposed in a shape of being extended along a left-right direction at a bottom portion of one side of the evaporator 130. The heating unit 171 may be disposed in a shape of being extended along a left-right direction of the evaporator 130 at the same height as that of the lowest column of the cooling tube 131 or a position lower than that of the lowest column of the cooling tube 131.

In the layout state, the lead wire 173 connected between the heater 171b and the power is extended from one end portion of the heater 171b adjacent to an outer side of the evaporator 130 to an outer side. In other words, the lead wire 173 is extended to an outer side other than an inner side of the evaporator 130 and connected to the power. According to the structure, an area in which the lead wire 173 is disposed to a lower side of the evaporator 130 may be minimized, thereby minimizing defrost water from falling onto the lead wire 173.

Considering specific examples thereof, first, FIG. 19 illustrates a view in which the heating unit 171 is disposed at a left bottom portion of the evaporator 130. The lead wire 173 is extended from a left end portion of the heater 171b adjacent to the left side of the evaporator 130 to an outer side. To this end, the terminal 171b3 connected to the lead wire 173 may be preferably located at a left end portion of the heater 171b.

As an opposite case to FIG. 19, FIG. 20 illustrates a view in which the heating unit 171 is disposed at a right bottom portion of the evaporator 130. The lead wire 173 is extended from a right end portion of the heater 171b adjacent to the right side of the evaporator 130 to an outer side. To this end, the terminal 171b3 connected to the lead wire 173 may be preferably located between the inlet and the outlet adjacent to the inlet of the heater case 171a.

Here, the right end portion of the heater 171b may be preferably disposed between the inlet and the outlet of the heater case 171a to disallow working fluid (F) collected through the inlet located at the right end portion of the heater case 171a from being reheated to flow backward. According to the layout, the hot wire 171b2 is not disposed at the inlet of the heater case 171a, and thus the inlet is located within the passive heating part (PHP).

As illustrated in the drawing, when the return portion 172d′, 172d″ connected to the inlet of the heater case 171a is formed in a bent shape, the direction of the returned working fluid (F) is switched at least once just prior to being introduced into the heater case 171a. Here, a large flow resistance is formed at a bent portion, thereby preventing the returned working fluid (F) from being flowing backward.

For reference, the foregoing examples illustrate a case where the heater case 171a is disposed horizontally to the evaporator, but the present disclosure may not be necessarily limited to this. The heater case 171a may be disposed in such a manner that an inlet-side end portion is disposed within an angle range greater than −90° but less than 2° with respect to an outlet-side end portion. It will be described in detail later.

FIGS. 21A through 21C are graphs illustrating a temperature change of the heater 171b for an inner diameter of a return portion 172d′, 172d″ illustrated in FIG. 4 in a freezing condition, and FIG. 22 is a view conceptually illustrating the flow of fluid at the return portion 172d′, 172d″ in the condition of FIG. 21C.

FIG. 21A is a view illustrating a case where an inner diameter of the return portion 172d′, 172d″ is 4.75 mm, and FIG. 21B is a view illustrating a case where the inner diameter of the return portion 172d′, 172d″ is 6.35 mm, and FIG. 21C is a view illustrating a case where the inner diameter of the return portion 172d′, 172d″ is 7.92 mm. In the present experiment, an appropriate amount of working fluid (F) was set to 55 g, 60 g and 65 g, respectively, to measure a temperature change of the heater 171b for an inner diameter of the return portion 172d′, 172d″.

As illustrated in FIG. 21A, in case where the inner diameter of the return portion 172d′, 172d″ is 4.75 mm, the overheating of the heater 171b occurred when the amount of working fluid (F) is 55 g. It is regarded that an amount of working fluid (F) returned to the heater case 171a is reduced compared to an appropriate amount due to a small diameter of the return portion 172d′, 172d″, and not sufficiently brought into contact with the heater 171b for heating the working fluid (F). When the diameter of the return portion 172d′, 172d″ is less than 5 mm as described above, it may cause a problem of overheating the heater 171b.

As illustrated in FIG. 21C, in case where the inner diameter of the return portion 172d′, 172d″ is 7.92 mm, the overheating of the heater 171b occurred when the amount of working fluid (F) is 55 g, 65 g. As described above, when the diameter of the return portion 172d′, 172d″ is greater than 7 mm, it occurred a phenomenon in which the collected working fluid (Fa) is all filled into the return portion 172d′, 172d″, and not collected into the heater case 171a, and flowed to a space formed at an upper portion within the return portion 172d′, 172d″ and introduced into the heater case 171a.

Here, working fluid (Fa) introduced into the heater case 171a is heated again by the heater 171b to strongly flow within the heating unit 171, and part of the heated working fluid (Fb) is discharged to an upper space within the return portion 172d′, 172d″, and as a result, it occurs a phenomenon in which part of the heated working fluid (Fb) flows backward.

As described above, the foregoing phenomenon occurs as an inner diameter of the return portion 172d′, 172d″ varies. Accordingly, in order to prevent the overheating of the heater 171b and the backflow of working fluid (F), the inlet 171d′, 171d″ should be formed within the passive heating part (PHP) as well as the return portion 172d′, 172d″ should have an appropriate inner diameter.

As a result of experiment, as illustrated in FIG. 21B, it is seen that the overheating of the heating unit 171 does not occur when an inner diameter of the return portion 172d′, 172d″ is 6.35 mm. It denotes that working fluid (F) can be efficiently returned, reheated and circulated. For reference, an amount of working fluid (F) used for the experiment is 55 g, 60 g, and it is a filling amount corresponding to 30-35% of the entire volume of the heat pipe 172 and heater case 171a.

As described above, an inner diameter of the return portion 172d′, 172d″ may be formed to be greater than 5 mm but less than 7 mm. Preferably, a commercial tube having an inner diameter of 6.35 mm within the above range may be used for the return portion 172d′, 172d″.

For reference, the heater case 171a having a specification with a width direction cross-section of 8 mm (height)×13 mm (width) was used for the foregoing experiment. The specification of the heater case 171a may be slightly different from the specification used for the foregoing experiment, the return portion 172d′, 172d″ having the above inner diameter condition may be used in a similar manner for the return portion 172d′, 172d″.

On the other hand, as described above, working fluid (F) heated and evaporated by the heater 171b within the heater case 171a is introduced into the entrance portion 172c′, 172c″ of the heat pipe 172, and working fluid (F) cooled while flowing through the heat pipe 172 is collected into the heater case 171a through the return portion 172d′, 172d″ of the heat pipe 172. During such a series of flow processes, an installation angle for the heater case 171a with respect to the heat pipe 172 performs a key role on whether or not working fluid (F) circulates. Hereinafter, it will be described in detail.

FIG. 23 is graphs illustrating a temperature change of each column of the heater case 171a and heat pipe 172 according to an angle at which an inlet 171d′, 171d″ side end portion of the heater case 171a is inclined with respect to an outlet 171c′, 171c″ side end portion thereof.

For reference, TH indicates a temperature of the heater case 171a, and TL indicates a temperature of the lowest column of the heat emitting part 172b of the heat pipe 172. Since working fluid (F) is heated by the heater 171b and circulated through the heat pipe 172, and then returned to the heater case 171a, the temperature (TH) of the heater case 171a is the highest, but the temperature (TL) of the lowest column of the heat emitting part 172b is the lowest. Accordingly, it is understood that the temperature of the remaining columns of the heat pipe 172 is between TH and TL. In FIG. 23, for the sake of convenience of explanation, only temperature curves corresponding to TH and TL are shown with indication lines.

Referring to the drawing, whether or not working fluid (F) efficiently circulates may vary according to an angle at which an inlet 171d′, 171d″ side end portion of the heater case 171a is inclined with respect to an outlet 171c′, 171c″ side end portion thereof. In case of a structure in which the heater case 171a is extended and formed in one direction, and the inlet 171d′, 171d″ and outlet 171c′, 171c″ are formed at both sides thereof, respectively, it relates to an angle at which an inlet 171d′, 171d″ side end portion of the heater case 171a is inclined with respect to an outlet 171c′, 171c″ side end portion thereof.

The angle 0° denotes a configuration in which the heater case 171a is disposed horizontally to the evaporator 130, and a positive (+) angle denotes a configuration in which an inlet 171d′, 171d″ side end portion of the heater case 171a is inclined upward with respect to an outlet 171c′, 171c″ side end portion thereof, and a negative (−) angle denotes a configuration in which an inlet 171d′, 171d″ side end portion of the heater case 171a is inclined downward with respect to an outlet 171c′, 171c″ side end portion thereof

As illustrated in FIG. 23A through 23C, when the heater case 171a is disposed horizontally to the evaporator 130 or an inlet 171d′, 171d″ side end portion of the heater case 171a is inclined downward with respect to an outlet 171c′, 171c″ side end portion thereof (when the outlet 171c′, 171c″ side is formed at the same height as that of the inlet 171d′, 171d″ side or the outlet 171c′, 171c″ side is formed at a higher height than that of the inlet 171d′, 171d″ side), the temperature of each column of the heat pipe 172 similarly increases according to the passage of time, and reaches a stable operating temperature subsequent to the passage of a predetermined period of time. It denotes that the circulation of working fluid (F) is efficiently carried out.

As a result of experiment, when an end portion of the inlet 171d′, 171d″ of the heater case 171a is disposed within a range between 0° and −90° with respect to an outlet 171c′, 171c″ side end portion thereof, it is seen that a temperature curve according to the passage of time has no problem in circulating working fluid (F) through the heat pipe 172.

On the contrary, referring to FIGS. 23D and 23F, when an inlet 171d′, 171d″ side end portion of the heater case 171a is inclined upward with respect to an outlet 171c′, 171c″ side end portion thereof (when the outlet 171c′, 171c″ side is formed at a lower position than that of the inlet 171d′, 171d″ side), it is shown that the temperature of each column of the heater case 171a and heat pipe 172 has a large difference for each angle.

Specifically, in a state that an inlet 171d′, 171d″ side end portion of the heater case 171a is inclined upward by 2° with respect to an outlet 171c′, 171c″ side end portion thereof (in a state that the inlet 171d′, 171d″ side is inclined upward by 2° with respect to the outlet 171c′, 171c″ side), it does not show a large difference from the foregoing graphs.

However, in a state that an inlet 171d′, 171d″ side end portion of the heater case 171a is inclined upward by 3° with respect to an outlet 171c′, 171c″ side end portion thereof (in a state that the inlet 171d′, 171d″ side is inclined upward by 3° with respect to the outlet 171c′, 171c″ side), it is seen that the temperature of the heater case 171a suddenly rapidly increases and decreased at an initial stage. Furthermore, in a state that an inlet 171d′, 171d″ side end portion of the heater case 171a is inclined upward by 4° with respect to an outlet 171c′, 171c″ side end portion thereof (in a state that the inlet 171d′, 171d″ side is inclined upward by 4° with respect to the outlet 171c′, 171c″ side), it is seen that the temperature of the heater case 171a continuously increases, and the heat pipe 172 is not largely deviated from an initial temperature.

It denotes that even if working fluid (F) is heated by the heater 171b, it is difficult to flow down toward the entrance portion 172c′, 172c″ in which the working fluid (F) is located at a relatively lower position when an inlet 171d′, 171d″ side end portion of the heater case 171a is inclined upward more than 3° with respect to an outlet 171c′, 171c″ side end portion thereof (in a state that the inlet 171d′, 171d″ side is inclined upward more than 3° with respect to the outlet 171c′, 171c″ side).

In particular, when an inlet 171d′, 171d″ side end portion of the heater case 171a is inclined upward more than 4° with respect to an outlet 171c′, 171c″ side end portion thereof (in a state that the inlet 171d′, 171d″ side is inclined upward more than 4° with respect to the outlet 171c′, 171c″ side), working fluid (F) does not flow down toward the entrance portion 172c′, 172c″ but flow backward not to allow circulation, and thus the temperature of the heater case 171a continuously increases to cause overheating.

Considering the experimental result, an inlet 171d′, 171d″ side end portion of the heater case 171a may be preferably disposed to have an angle range greater than −90° but less than 2° with respect to an outlet 171c′, 171c″ side end portion thereof.

For reference, it is seen that the temperature of the lowest column of the heater 171b of the heat pipe 172 more rapidly increases when FIGS. 23A through 23C are compared with each other, as an inlet 171d′, 171d″ side end portion of the heater case 171a is disposed to be inclined downward with respect to an outlet 171c′, 171c″ side end portion thereof. It is because the flow of working fluid (F) is easily carried out as the outlet 171c′, 171c″ side of the heater case 171a is disposed upward with respect to the inlet 171d′, 171d″ side thereof.

Hereinafter, a connection structure between the heating unit 171 and the heat pipe 172 for easily carrying out the flowing of working fluid (F) in consideration of a rising characteristic of heated working fluid (F) will be described.

FIGS. 24 through 26 are longitudinal cross-sectional views illustrating a modified example of a connection structure between the heating unit 171 and the heat pipe 172 in the heating unit 171 applied to FIGS. 19 and 20. For reference, the present drawings briefly illustrate a heating unit 1171, 1271, 1371 with only a heater case 1171a, 1271a, 1371a and a heater 1171b, 1271b, 1371b for the sake of convenience of explanation. The foregoing detailed structure (a structure formed with first and second extension fins, a sealing member, outer fins, inner fins, and the like) may be of course applicable to the heating unit 1171, 1271, 1371.

Hereinafter, the present disclosure will be describes based on that the heater case 1171a, 1271a, 1371a is disposed horizontally to the evaporator, but the present disclosure may not be necessarily limited to this. As described above, the heater case 1171a, 1271a, 1371a may be disposed such that an inlet 1171d″, 1271d″, 1371d″ (an inlet at an opposite side is not shown) side end portion has an angle range greater than −90° but less than 2° with respect to an outlet 1271c″, 1271c″, 1371c″ (an outlet at an opposite side is not shown).

Moreover, hereinafter, the present disclosure will be described based on that the inlet 1171d″, 1271d″, 1371d″ and outlet 1271c″, 1271c″, 1371c″ are formed at positions separated by a predetermined distance along a length direction at both lateral surfaces of the heater case 1171a, 1271a, 1371a (a structure illustrated in the above FIG. 4), but the present disclosure may not be necessarily limited to this. At least one of the inlet 1171d″, 1271d″, 1371d″ and outlet 1271c″, 1271c″, 1371c″ of the heating unit 1171, 1271, 1371 may be formed at an end portion of the heater case 1171a, 1271a, 1371a (a structure illustrated in the above FIGS. 7 through 9).

As described above, working fluid (F) is collected through the inlet 1171d″, 1271d″, 1371d″ and then heated again by the heater 1171b, 1271b, 1371b and discharged to the outlet 1271c″, 1271c″, 1371c″. In consideration of the flow direction of working fluid (F) and the rising characteristic of heated working fluid (W), a return portion 1172d″, 1272d″, 1372d″ of the heat pipe (an opposite side is not shown) may be disposed in parallel to the heater case 1171a, 1271a, 1371a or extended and formed (or extended downward and bent to be horizontally extended and formed) in a downward direction of the heater case 1171a, 1271a, 1371a, and an entrance portion 1172c″, 1272c″, 1372c″ of the heat pipe (an opposite side is not shown) may be disposed in parallel to the heater case 1171a, 1271a, 1371a or extended and formed in an upward direction of the heater case 1171a, 1271a, 1371a.

Here, the meaning of being extended and formed in an upward and/or downward direction may include being extended and formed in a vertical manner as well as being extended and formed in an inclined manner.

Moreover, in a combination of the cases, both the return portion 1172d″, 1272d″, 1372d″ and entrance portion 1172c″, 1272c″, 1372c″ may be extended and formed along a length direction of the heater case 1171a, 1271a, 1371a, but in the aspect of flow design in consideration of a rising force of working fluid (F), only either one of the return portion 1172d″, 1272d″, 1372d″ and entrance portion 1172c″, 1272c″, 1372c″ may be preferably extended and formed along a length direction of the heater case 171a.

For an example, FIG. 24 illustrates a view in which the return portion 1172d″ of the heat pipe is extended and formed along a length direction of the heater case 1171a, and the entrance portion 1172c″ of the heat pipe is extended and formed in an upward direction of the heater case 1171a.

For another example, FIG. 25 illustrates a view in which the return portion 1272d″ of the heat pipe is extended and formed in a downward direction of the heater case 1271a, and the entrance portion 1272c′, 1272c″ of the heat pipe is extended and formed in an upward direction of the heater case 1271a.

The foregoing two examples may be applicable to a structure in which the heating unit 171 is directly connected to a vertical extension portion of the heat pipe 172 as illustrated in FIG. 19 in the aspect that the entrance portion 1172c″, 1272c″ of the heat pipe is extended and formed in an upward direction of the evaporator. In this case, a lower end portion of the vertical extension portion constitutes the entrance portion 1172c″, 1272c″.

For reference, as illustrated in FIG. 19, the foregoing two examples are configured such that the a terminal (not shown) of the heater 1171b, 1271b is formed adjacent to an outlet 1271c″, 1271c″ of the heater case 1171a, 1271a, and a lead wire 1173, 1273 is connected to the terminal and extended to an outside.

According to the above structure, natural flow is formed such that working fluid (F) heated by the heater 1171b, 1271b is raised and discharged to the entrance portion 1172c″, 1272c″ extended and formed upward, and thus working fluid (F) heated by the heater 1171b, 1271b may be efficiently discharged through the entrance portion 1172c″, 1272c″ even in a state that the heater case 1171a, 1271a is disposed in a horizontal manner

In particular, the structure illustrated in FIG. 25 is a structure in which working fluid (F) heated to have a rising force is unable to flow backward to the return portion 1272d″ as the return portion 1272d″ of the heat pipe 1272 has a structure of being extended and formed at a downward direction of the heater case 1271a. Accordingly, it may be possible to form a more natural flow of discharging the heated working fluid (F) through the entrance portion 1272c″ without flowing backward to the return portion 1272d″.

For another example, in FIG. 26, it is shown that the return portion 1372d″ of the heat pipe 1372 is extended and formed in a downward direction of the heater case 1371a, and the entrance portion 1372c″ of the heat pipe 1372 is extended and formed along a length direction of the heater case 1371a.

The foregoing structure may be applicable to a structure in which the heating unit 171 is directly connected to a horizontal extension portion of the heat pipe 172 as illustrated in FIG. 20 in the aspect that the entrance portion 1372c″ of the heat pipe 1372 is extended and formed along a length direction of the heater case 1371a. In this case, an end portion of the horizontal extension portion constitutes the entrance portion 1372″. For reference, as described in association with FIG. 20, in the above example, it is configured such that a terminal (not shown) of the heater 1371b is formed between the inlet 1371d″ and the outlet 1371c″ of the heater case 1371a, and the led wire 1373 is connected to the terminal and extended to an outside.

It is not a discharge structure appropriate to a characteristic of raising heated working fluid (F) compared to the foregoing structures, but working fluid (F) heated to have a rising force is unable to flow backward to the return portion 1372d″ as the return portion 1372d″ of the heat pipe 1372 has a structure of being extended and formed at a downward direction of the heater case 1371a. Accordingly, it may be possible to form a series of flows of discharging heated working fluid (F) through the entrance portion 1372c″.

On the other hand, the heater case 1471a may be extended and formed in a vertical direction from a lower side of the evaporator 1430 to an upper side thereof such that an inlet 1471d″ (an inlet at an opposite side is not shown) side end portion forms an angle of −90° with respect to an outlet 1471c″ (an outlet at an opposite side is not shown) side end portion.

FIGS. 27 and 28 are a front view and a perspective view illustrating a second embodiment 1470 of the defrosting device 170 applied to the refrigerator 100 in FIG. 1.

Referring to FIGS. 27 and 28, a heating unit 1471 may be disposed at one outer side of a defrosting device 1470. Specifically, a heater case 1471a may be located at an outer side of a support fixture 1433 provided at one side of an evaporator 1430, and extended and formed in a vertical direction from a lower side of the evaporator 1430 to an upper side thereof. Here, at least part of the heater case 1471a may be disposed between a first cooling tube 1431′ and a second cooling tube 1431″

The heater case 1471a is connected to heat pipes 1472, respectively, to form a passage capable of circulating working fluid (F). An outlet 1471c″ and an inlet 1471d″ are formed at an upper and a lower side of the heater case 1471a, respectively. The outlet 1471c″ is connected to an extension portion of the heat pipe 1472, and the inlet 1471d″ is connected to the lowest column of the heat pipe 1472.

A heater 1471b is configured with a plate-shaped heater 1471b extended and formed along one direction, and attached to an outer surface of the heater case 1471a and vertically disposed in a top-down direction of the evaporator 1430. For reference, FIG. 27 briefly illustrates the heater case 1471a with only the heater case 1471a and heater 1471b for the sake of convenience of explanation. The foregoing detailed structure (a structure formed with first and second extension fins, a sealing member, outer fins, inner fins, and the like) may be of course applicable to the heating unit 1471.

According to the present embodiment, it is shown that the heater 1471b is attached to one surface of the heater case 1471a facing outward. According to the layout, it may be possible to prevent defrost water from being brought into contact with the heater 1471b at a predetermined level. However, the present disclosure may not be necessarily limited to this. The heater 1471b may be also attached to another surface of the heater case 1471a facing the support fixture 133. However, in this case, a structure capable of preventing contact between the heater 1471b and defrost water may be preferably provided.

For reference, when the heater 1471b is attached to one surface of the heater case 1471a facing outward, an outer fin may be protruded and formed on another surface of the heater case 1471a facing the support fixture 133, and an inner fin may be protruded and formed on an inner surface of an inner side of one surface to which the heater 1471b is attached.

A hot wire 1471b2 of the heater 1471b is extended and formed between the inlet 1471d″ and the outlet 1471c″ toward the outlet 1471c″, and configured to reheat working fluid (F) collected through the inlet 1471d″. A terminal (not shown) of the heater 1471b may be formed at an end portion of the heater 1471b located between the inlet 1471d″ and the outlet 1471c″, and a lead wire 1473 is connected to the terminal and extended toward a lower side of the evaporator 1430.

On the other hand, working fluid (F) may be preferably filled at a higher position than that of the highest end of the heater 1471b extended in a vertical direction within the heater case 1471a. According to the foregoing configuration, defrosting operation may be stably carried out in a state that the heating unit 1471 is not overheated, and the continuous supply of working fluid (F) in a gas phase to the heat pipe 1472 may be stably carried out.

Hereinafter, a design change of a heat pipe 1572 in consideration of convection according to a temperature of working fluid (F) when the working fluid (F) circulates the heat pipe 1572 will be described.

FIG. 29 is a conceptual view illustrating a third embodiment 1570 in which a width between upper columns and lower columns of the heat pipe 1572 is differently formed in the defrosting device 170 applied to the refrigerator 100 in FIG. 1. According to the present embodiment, the defrosting device 1570 is shown on a front surface (a) and a lateral surface (b) thereof.

For reference, FIG. 29A illustrates a configuration that a first cooling tube 1531′ at a front side is omitted to exhibit the entire shape of the heat pipe 1572. Furthermore, part of a second cooling tube 1531″ may not be seen due to overlapping with the heat pipe 1572, but referring to the layout of a cooling fin 1532 and FIG. 29B, the entire shape of the first and the second cooling fin 1531′, 1521″ may be seen.

Referring to FIG. 29, the cooling tube 1531 and heat pipe 1572 are repeated bent in a zigzag shape to form a plurality of columns

Specifically, the cooling tube 1531 may be configured with a combination of horizontal pipe portions and bending pipe portions. The horizontal pipe portions are horizontally disposed in a top-down direction, and configured to pass through cooling fins 1532, and the bending pipe portions are connected between an end portion of an upper horizontal pipe portion and an end portion of a lower horizontal pipe portion to communicate with each other. Here, each column of the horizontal pipe portions may be disposed at predetermined intervals as illustrated in the drawing.

The heat pipe 1572 is disposed between a first cooling tube 1531′ and a second cooling tube 1531″ to form a single row. The heat pipe 1572 may include an extension portion 1572a and a heat emitting part 1572b. The description of the extension portion 1572a will be substituted by the description of previous embodiment.

The heat emitting part 172b is extended in a zigzag shape along the cooling tube 1531 of the evaporator 1530 from the extension portion 1572a connected to an inlet of the heating unit 1571. The heat emitting part 1572b is configured in combination with a plurality of horizontal tubes 1572b′ constituting columns and a connecting tube 1572b″ formed in a bent U-shaped tube to connect them in a zigzag shape.

In the foregoing structure, a distance between each column of the horizontal tubes 1572b′ at a lower portion thereof may be formed to be smaller than that of horizontal tubes 1572b′ at an upper portion thereof. It is a design in consideration of convection according to a temperature of working fluid (F) when the working fluid (F) circulates the heat pipe 1572.

Specifically, working fluid (F) introduced through the entrance portion of the heat pipe 1572 is in a high-temperature gas phase, and has the highest temperature during the circulation process of the heat pipe 1572. As illustrated in the drawing, high-temperature working fluid (F) moves toward the cooling tube 1531, and thus high-temperature heat is transferred to a large area by convection around the cooling tube 1531 at an upper portion thereof.

On the contrary, working fluid (F) flows in a state that in a phase that liquid and gas coexist while gradually losing heat, and is finally introduced into the return portion, and the heat at this time is a sufficient temperature for removing frost on the cooling tube 1531, but an amount of heat transfer to the surrounding is smaller than the former case.

Accordingly, in consideration of this, each column of the heat pipe 1572 close to the return portion (namely, the horizontal tubes 1572b′ of the heat emitting part 1572b) is disposed with a smaller distance compared to that of the heat pipe 1572 located at an upper portion thereof. For example, each column of the heat pipe 1572 located at an upper portion thereof may be disposed to correspond to a column of the adjoining cooling tube 1531 by interposing one column of the cooling tube 1531 therebetween, and each column of the heat pipe 1572 located at a lower portion thereof may be disposed to correspond to each column of the cooling tube 1531.

Accordingly the foregoing structure, a lower portion of the evaporator 1530 is arranged with a relatively larger number of horizontal tubes 1572b′ of the heat emitting part 1572b than that of an upper portion thereof.

FIGS. 30 and 31 are conceptual views illustrating a modified example 1670 of the defrosting device 1570 illustrated in FIG. 29.

First, FIG. 30 illustrates a front surface (a) and a lateral surface (b) of the defrosting device 1670.

According to the present modified example, a heat pipe 1672 may include a first heat pipe 1672′ at a front side of a first cooling tube 1631′ and a second heat pipe 1672″ at a rear side of a second cooling tube 1631″ to form two columns.

For reference, the second heat pipe 1672″ may not be seen due to overlapping with the first heat pipe 1672′ in FIG. 30A, but referring to FIG. 30B, the entire shape of the second cooling fin 1672″ may be seen.

As illustrated in the drawing, a distance between each column of the horizontal tubes 1672b′ disposed at a lower portion of the first and the second heat pipe 1672′, 1672″ may be formed to be smaller than that between each column of the horizontal tubes 1672b′ disposed at an upper portion thereof. It is a design in consideration of convection according to a temperature of working fluid (F) when the working fluid (F) circulates the heat pipe 1672, and the detailed description thereof will be substituted by the earlier description of FIG. 29.

Next, FIG. 31 illustrates a view in which part of a first and a second cooling tube 1731′, 1731″ is omitted to help understanding.

Referring to FIG. 31, a distance between each column disposed at a lower portion of a first heat pipe 1772′ at a front side of an evaporator 1730 may be formed to be smaller than that of each column disposed at an upper portion thereof. On the contrary, a distance between each column disposed at an upper portion of a first heat pipe 1772′ at a rear side of the evaporator 1730 may be formed to be smaller than that of each column disposed at an lower portion thereof.

According to the layout relationship, a temperature decrease due to any one portion having a smaller distance of the heat pipe 1772 may be compensated by a temperature increase due to another portion having a smaller distance of the heat pipe 1772. Accordingly, the present disclosure may implement an efficient heat transfer structure to a cooling tube 1731 while the first and the second heat pipe 1772′, 1772″ are configured to be shorter than the basic structure (a structure illustrated in FIG. 3).

For a modified example for this, a distance between each column disposed at a lower portion of the first heat pipe 1772′ at a front side of the evaporator 1730 may be formed to be larger that between each column disposed at an upper portion thereof. On the contrary, a distance between each column disposed at an upper portion of the second heat pipe 1772″ at a rear side of the evaporator 1730 may be formed to be larger that between each column disposed at a lower portion thereof.

On the other hand, as working fluid (F) dissipates heat to a cooling tube 1831 while flowing a heat pipe 1872, the working fluid (F) is cooled when closer to an inlet of a heating unit 1871. Accordingly, defrosting for a lower cooling tube 1731 may not be efficiently carried out. Hereinafter, a structure capable of solving this problem will be described.

FIGS. 32 and 33 are a front view and a perspective view illustrating a fourth embodiment 1870 of the defrosting device 170 applied to the refrigerator 100 in FIG. 1. FIG. 32 illustrates a view in which part of a cooling fin 1832 is omitted. For reference, the detailed configuration of an evaporator 1830 is illustrated in more detail in FIG. 33.

Referring to FIGS. 32 and 33, a heat pipe 1872 may be divided into a high-temperature evaporator (E) and a low-temperature condenser (C) in the aspect according to the phase of circulating working fluid (F).

An evaporator (E) as a portion in which working fluid (F) moves in a phase containing a high-temperature gas or high-temperature gas and liquid has a temperature capable of removing frost on the cooling tube 1831. Structurally, the evaporator (E) is connected to an outlet of a heating unit 1871, and disposed to correspond to the cooling tube 1831 of the evaporator 1830 to transfer heat to the cooling tube 1831 of the evaporator 1830.

On the contrary, a condenser (C) as a portion in which working fluid (F) flows in a low-temperature liquid phase has a temperature lower than that capable of performing defrosting on the cooling tube 1831. Accordingly, even when the condenser (C) is disposed adjacent to the cooling tube 1831, defrosting on the cooling tube 1831 may not be efficiently carried out. The condenser (C) is finally connected to an inlet of the heating unit 1871.

A heat pipe 1872 is extended in a zigzag shape from the top to the bottom, and thus when the heat pipe 1872 is arranged to correspond to the cooling tube 1831, the condenser (C) is disposed adjacent to a lower side of the cooling tube 1831. It denotes that defrosting on the lower cooling tube 1831 cannot be efficiently carried out.

In order to solve this, the condenser (C) is extended from the evaporator (E) and disposed lower than the lowest column cooling tube 1831a of the evaporator 1830. The condenser (C) is configured to including at least two horizontal tubes disposed lower than the lowest column cooling tube 1831a. According to the present embodiment, it is shown a structure in which two columns of the heat pipes 1872 are further provided lower than the lowest column of the cooling tube 1831 of the evaporator 1830 to constitute the condenser (C).

As described above, when the low-temperature condenser (C) of the heat pipe 1872 is disposed lower than the lowest column cooling tube 1831a of the evaporator 1830, only the high-temperature evaporator (E) may be used for defrosting of the evaporator 1830, and thus defrosting on a lower side of the cooling tube 1831 may be efficiently carried out.

According to the foregoing structure, a lower end of the heating unit 1871 is disposed adjacent to the lowest column cooling tube 1831a. Accordingly, a return portion of the heat pipe 1872 is extended in an upward bent shape from the lowest column horizontal tube of the condenser (C) to an inlet of the heating unit 1871 to form a passage capable of collecting the condensed working fluid (F).

A large flow resistance is formed at a portion having a bent shape on the return portion, and thus there is an advantage of suppressing working fluid (F) returned to an inlet of the heating unit 1871 from flowing backward.

FIGS. 34 and 35 are a front view and a perspective view illustrating an example 1970 in which the formation position of the heating unit 1971 is modified in the defrosting device 1870 illustrated in FIGS. 32 and 33.

Referring to FIGS. 34 and 35, at least part of the heating unit 1971 is disposed lower than the lowest column cooling tube 1931 of an evaporator 1930. For an example, a lower end of the heating unit 1971 may be located adjacent to the lowest column horizontal tube of a heat pipe 1972, and an upper end of the heating unit 1971 may be located below the first cooling tube 1931b on the top (namely, second cooling tube on the bottom) from the lowest column cooling tube 1931a of the evaporator 1930.

According to the foregoing structure, a return portion connected between the lowest column horizontal tube of the heat pipe 1972 and an inlet of the heating unit 1971 is formed to be shorter than the return portion of the previous embodiment.

When the lowest column horizontal tube of the heat pipe 1972 and an inlet of the heating unit 1971 are placed on the substantially same level, a return portion may be extended from the lowest column horizontal tube of the heat pipe 1972 in a horizontal direction and connected to the inlet of the heating unit 1971.

Furthermore, according to the foregoing structure, it is configured such that the heating unit 1971 is disposed adjacent to the lowest column horizontal tube of the heat pipe 1972, and thus a heater 1971b is located below a water level of working fluid (F) with a smaller amount of working fluid (F) compared to the previous embodiment. Furthermore, a temperature of the lowest column horizontal tube of the heat pipe 1972 may further increase as a filling amount of working fluid (F) decreases. It denotes that a lower temperature of the evaporator (E) increases compared to the previous examples.

Number	Date	Country	Kind
10-2015-0147010	Oct 2015	KR	national
10-2015-0147011	Oct 2015	KR	national
10-2015-0147012	Oct 2015	KR	national

DEFROSTING DEVICE AND REFRIGERATOR HAVING THE SAME

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