Plate heat exchanger type heat dissipation fin assembly

Abstract

The present invention relates to a plate heat exchanger type heat dissipation fin assembly, and provides the advantage of improving heat dissipation performance by minimizing flow resistance between evaporated gas-phase refrigerant and condensed liquid-phase refrigerant in a refrigerant flow space, by comprising: one heat exchange panel; the other heat exchange panel forming a refrigerant flow space in which a refrigerant filled therebetween flows while undergoing a phase change; and a gas-liquid refrigerant separation portion disposed, in the refrigerant flow space, between a relatively lower space and an upper space in the gravitational direction.

Description

Plate heat exchanger type heat dissipation fin assembly

[0001] The present invention relates to a plate heat exchanger type heat dissipation fin assembly, and more specifically, to a plate heat exchanger type heat dissipation fin assembly capable of improving heat dissipation performance by minimizing flow resistance between a gaseous refrigerant that evaporates and diffuses inside and a liquid refrigerant that condenses and flows down.

[0002] Generally, electronic devices include electrically operated heating elements, and the performance of the electronic device depends on whether the heat generated from the heating elements is rapidly dissipated.

[0003] A heat dissipation body equipped with a plurality of heat dissipation fins may be applied for rapid heat dissipation of heat generated from a heating element to the outside air side. The heat dissipation body is generally configured to make surface thermal contact with the heat-generating surface of the heating element, transfer heat through the heat conduction of the material itself, and then dissipate heat through heat exchange with the outside air via a portion exposed to the outside air side.

[0004] However, when relying on the heat conduction method of the heat dissipation material itself, the heat dissipation must be extended as far as possible from a heat source, such as a heat transfer element, in order to increase the surface area exposed to the outside air. This leads to the disadvantage of increasing the volume of the product, while there is a problem of heat concentration occurring at a location close to the heat source.

[0005] In order to overcome the disadvantages of the heat conduction method inherent to such materials, there has recently been a continuing trend of developing active heat dissipation fins in which a refrigerant is filled inside each fin of the heat dissipation body. The filled refrigerant evaporates due to heat received from the heat transfer element and diffuses across the entire surface area of ​​the fin, thereby enabling uniform heat transfer over the entire surface area of ​​the fin.

[0006] The applicant of the present invention has also obtained a patent registration for an active heat dissipation fin through Korean Registered Patent Publication No. 10-2741552 (registered on December 6, 2024) (hereinafter referred to as the 'Applicant's Registered Patent').

[0007] However, while the applicant's registered patent is undeniably superior to existing heat dissipation fins made of aluminum, a problem regarding the flow resistance of phase-change refrigerants has been discovered. This is because the refrigerant flow space where the refrigerant is filled is slim and narrow, causing mutual collisions between the gravitational flow of the liquid refrigerant and the diffusion process of the gaseous refrigerant during the process of dissipating heat from a relatively high-output heat transfer element. The flow resistance occurring between the evaporated gaseous refrigerant and the condensed liquid refrigerant can lead to a reduction in the refrigerant circulation cycle, which can result in a decrease in heat dissipation performance.

[0008]

[0009] The present invention has been devised to solve the aforementioned technical problem and aims to provide a plate-type heat exchanger type heat dissipation fin assembly capable of minimizing flow resistance caused by mutual collision between evaporated gaseous refrigerant and condensed liquid refrigerant within a refrigerant flow space.

[0010] In addition, another objective of the present invention is to provide a plate-type heat exchanger type heat dissipation fin assembly comprising a gas-liquid refrigerant separator that separates a flow space for a liquid refrigerant and a flow space for a gaseous refrigerant.

[0011] The problems of the present invention are not limited to those mentioned above, and other problems not mentioned will be clearly understood by those skilled in the art from the description below.

[0012]

[0013] A plate-type heat exchanger type heat dissipation fin assembly according to one embodiment of the present invention comprises a heat exchange panel on one side, a heat exchange panel on the other side that forms a refrigerant flow space in which a refrigerant filled between the heat exchange panel on the one side flows while undergoing a phase change, and a gas-liquid refrigerant separation unit disposed between a space on the lower side in the direction of gravity and a space on the upper side of the refrigerant flow space.

[0014] Here, the gas-liquid refrigerant separation unit can divide the refrigerant flow space into at least three spaces in the thickness direction.

[0015] Additionally, the refrigerant flow space comprises a first refrigerant flow path in which the refrigerant evaporates from a liquid refrigerant to a gaseous refrigerant as a space corresponding to the lower side in the direction of gravity, a plurality of second refrigerant flow paths formed inclined toward the first refrigerant flow path and inducing the flow of the gaseous refrigerant among the refrigerants to the lower part of the condensed liquid refrigerant, and a plurality of third refrigerant flow paths formed between the plurality of second refrigerant flow paths and formed as spaces smaller than the thickness of the second refrigerant flow paths, and the gas-liquid refrigerant separation unit may be positioned in close proximity to the first refrigerant flow path.

[0016] In addition, the gas-liquid refrigerant separation unit may be arranged to separate the second refrigerant path and the third refrigerant path in the thickness direction.

[0017] In addition, the gas-liquid refrigerant separation unit may be provided in pairs to partition the second refrigerant flow path toward the one-sided heat exchange panel and the other-sided heat exchange panel, respectively.

[0018] In addition, the gas-liquid refrigerant separation unit may divide the second refrigerant flow path into three sections with a thickness of 'd / 3' when the thickness of the refrigerant flow space is 'd'.

[0019] In addition, the first refrigerant path is further provided with an absorbent that promotes the absorption and evaporation of the liquid refrigerant among the refrigerants, and the gas-liquid refrigerant separation unit may be arranged parallel to the upper part of the absorbent.

[0020] In addition, the absorbers are provided as a pair disposed on the side of the one heat exchange panel and the side of the other heat exchange panel, and the space between the pair of absorbers may be an empty space.

[0021] Additionally, the third refrigerant flow path is defined by a plurality of inclined guides formed such that the one-sided heat exchange panel and the other-sided heat exchange panel are each recessed toward the refrigerant flow space between the second refrigerant flow path, and the gas-liquid refrigerant separation unit may be positioned to contact the inner surface of the plurality of inclined guides in the refrigerant flow space.

[0022] In addition, the gas-liquid refrigerant separation unit includes a one-side separation unit disposed on the side of the one-side heat exchange panel and a other-side separation unit disposed on the side of the other-side heat exchange panel, and the one-side separation unit and the other-side separation unit may be spaced apart by a predetermined distance in the thickness direction within the refrigerant flow space.

[0023]

[0024] According to a plate-type heat exchanger type heat dissipation fin assembly according to one embodiment of the present invention, various effects such as the following can be achieved.

[0025] First, by separating the rising section of the evaporated gaseous refrigerant and the descending section of the condensed liquid refrigerant within the refrigerant flow space using a gas-liquid refrigerant separator, it has the effect of minimizing mutual flow resistance of the refrigerants.

[0026] Second, by minimizing the flow resistance of the refrigerant and reducing the phase change cycle interval of the refrigerant, it has the effect of improving heat dissipation performance within a limited refrigerant flow space.

[0027] The effects of the present invention are not limited to those mentioned above, and other unmentioned effects will be clearly understood by those skilled in the art from the description in the claims.

[0028]

[0029] FIG. 1 is a rear perspective view of an antenna device including a plate-type heat exchanger type heat dissipation fin assembly according to one embodiment of the present invention, and

[0030] FIG. 2 is a perspective view showing a plate-type heat exchanger type heat dissipation fin assembly according to one embodiment of the present invention, and

[0031] FIG. 3 is an exploded perspective view of the configuration of FIG. 2, showing one side heat exchange panel and the other side heat exchange panel disassembled.

[0032] FIG. 4 is an exploded perspective view of the detailed configuration of FIG. 3, and

[0033] FIG. 5 is a perspective view showing the internal configuration of FIG. 2 with the other side heat exchange panel removed, and

[0034] FIG. 6 is a cross-sectional perspective view taken along the line A-A' of FIG. 5, and

[0035] FIG. 7 is an enlarged perspective view of section "B" of FIG. 6, and

[0036] FIG. 8 is a front view of FIG. 2, and

[0037] FIG. 9 is a cross-sectional view taken along the line C-C' of FIG. 8 and an enlarged view of the part thereof, and

[0038] Fig. 10 is a partial cutaway perspective view taken along the line C-C' of Fig. 8.

[0039]

[0040] <Explanation of Symbols>

[0041] 200: Heat dissipation fin assembly 201: Evaporator end

[0042] 203: Condenser section 205: Refrigerant flow space

[0043] 210: First refrigerant path 215: Inclined guide

[0044] 220: Second refrigerant path 220a: First space

[0045] 220-1: Second Space 220-2: Third Space

[0046] 230: Third refrigerant path 240: Strength reinforcement

[0047] 300: Absorbent 350: Gas-liquid refrigerant separator

[0048] 350a: One-side separator 350b: Other-side separator

[0049]

[0050] Hereinafter, a plate-type heat exchanger type heat dissipation fin assembly according to one embodiment of the present invention will be described in detail with reference to the attached drawings.

[0051] It should be noted that when assigning reference numerals to the components of each drawing, the same components are assigned the same reference numeral whenever possible, even if they are shown in different drawings. Furthermore, in describing the embodiments of the present invention, if it is determined that a detailed description of related known components or functions would hinder understanding of the embodiments of the present invention, such detailed description is omitted.

[0052] In describing the components of the embodiments of the present invention, terms such as first, second, A, B, (a), (b), etc., may be used. These terms are intended merely to distinguish the components from other components, and the essence, order, or sequence of the components is not limited by these terms. Furthermore, unless otherwise defined, all terms used herein, including technical or scientific terms, have the same meaning as generally understood by those skilled in the art to which the present invention pertains. Terms such as those defined in commonly used dictionaries should be interpreted as having a meaning consistent with their meaning in the context of the relevant technology, and should not be interpreted in an ideal or overly formal sense unless explicitly defined in this application.

[0053]

[0054] FIG. 1 is a rear perspective view of an antenna device including a plate-type heat exchanger type heat dissipation fin assembly according to one embodiment of the present invention.

[0055] First, the general configuration and heat dissipation-related configuration of an antenna device (1) to which a plate-type heat exchanger type heat dissipation fin assembly (200) according to one embodiment of the present invention is applied will be briefly described.

[0056] Generally, heating devices (electronic devices) are manufactured in various forms across the industry. However, as the applicant of the present invention is a company engaged in the manufacture of other wireless communication equipment, in order to facilitate understanding of the present invention, an antenna device will be described as a representative heating device (electronic device) in the following embodiments.

[0057] However, the plate-type heat exchanger type heat dissipation fin assembly (200) according to one embodiment of the present invention described below should not be interpreted as being limited only to antenna devices. For instance, it is obvious that the plate-type heat exchanger type heat dissipation fin assembly (200) according to one embodiment of the present invention can be applied to any heating device (or electronic device) that includes a heat-generating element that operates by consuming high-output electrical energy and generates high-temperature heat.

[0058] The antenna device (100) includes a heat dissipation housing body (110) formed in a rectangular shape (or housing shape) that forms a receiving space that is open to the front, as referenced in FIG. 1, and has a long and thin front-to-back receiving width in the vertical direction.

[0059] In the inner side of the receiving space of the heat dissipation housing body (110), although not shown in the drawing, a main board can be stacked and arranged such that a plurality of MBF (Micro Bellows Filter) elements are mounted on the front side via a clamshell as a substrate for a PAU (Power Amplifier Unit) and a DTU (Digital Transceiver Unit), and heating elements equipped with a type of heating element are mounted on the back side.

[0060] Here, heating elements (heating bodies) that generate a large amount of heat during operation, such as RFIC elements or PA elements, may be mounted on the back side of the main board. However, it should be noted that in the embodiment of the present invention, the heating elements (140) are not limited to the above configuration, but are merely described by adopting an electronic device as an antenna device. For example, it may be possible for the heating elements (140) to be adopted as semiconductors, which are representative heating elements.

[0061] A radome panel (50) is installed on the front of the receiving space of the heat dissipation housing body (110) to protect the radiating elements implemented as antenna elements from the outside and to enable smooth radiation from the radiating elements.

[0062] Meanwhile, on the back surface of the heat dissipation housing body (110), heat dissipation means of various specifications, including a plate-type heat exchanger type heat dissipation fin assembly (200) according to one embodiment of the present invention, may be installed. More specifically, as referenced in FIG. 1, the heat dissipation means of various specifications may be arranged on the back surface of the heat dissipation housing body (110), and a plurality of them may be arranged so as to be inclined upward toward the left end and the right end of the back surface, centered on the upper and lower vertical lines in the middle of the back surface of the heat dissipation housing body (110).

[0063] Here, the various heat dissipation means may include an integrated heat dissipation fin assembly (200F-1, 200F-2) integrally molded on the back surface of a heat dissipation housing body (110) to perform heat dissipation by the heat conduction of the material itself, and a plate-type heat exchanger type heat dissipation fin assembly (200) according to an embodiment of the present invention, which is configured to perform heat dissipation using a phase change cycle of a refrigerant, which is a phase change material filled inside.

[0064] Here, the plate-type heat exchanger type heat dissipation fin assembly (200) according to one embodiment of the present invention is provided in multiple units, all of which are formed with the same dimensions of a rectangular shape extending in the longitudinal direction, and can be installed in multiple fin installation grooves (150) provided in the shape of the inclined pattern described above on the back surface of the heat dissipation housing body (110). Additionally, the remaining integrated heat dissipation fin assemblies (200F-1, 200F-2), excluding the plate-type heat exchanger type heat dissipation fin assembly (200) according to one embodiment of the present invention, can be disposed in the remaining portion of the back surface of the heat dissipation housing body (110) that is not occupied by the plate-type heat exchanger type heat dissipation fin assembly (200).

[0065] The integrated heat dissipation fin assembly (200F-1, 200F-2) may include an upper integrated heat dissipation fin (200F-1) disposed on the upper side of the rear portion of the heat dissipation housing body (110) that is not occupied by the plate heat exchanger type heat dissipation fin assembly (200) according to one embodiment of the present invention as referenced in FIG. 1, and a lower integrated heat dissipation fin (200F-2) disposed on the left and right lower sides of the rear portion of the heat dissipation housing body (110) that is not occupied by the plate heat exchanger type heat dissipation fin assembly (200) according to one embodiment of the present invention.

[0066] It is stated in advance that the upper integrated heat dissipation fin (200F-1) and the lower integrated heat dissipation fin (200F-2), unlike the heat exchange panel type heat dissipation fin assembly (200) according to one embodiment of the present invention, are configured to transfer heat according to the thermal conductivity of the metal material itself without being filled with a refrigerant inside.

[0067] Meanwhile, in that a plurality of fin installation grooves (150) in which a plate-type heat exchanger type heat dissipation fin assembly (200) according to one embodiment of the present invention is installed are arranged to be inclined upward toward the left and right ends with respect to the center (see reference numeral 170) of the back surface of the heat dissipation housing body (110), the plate-type heat exchanger type heat dissipation fin assembly (200) installed in the fin installation grooves (150) can also be arranged to form a 'V' shape with respect to the center (170) of the back surface of the heat dissipation housing body (110).

[0068] The fin installation groove (150) may be provided in a slot shape so that a portion of the front end of the plate-type heat exchanger type heat dissipation fin assembly (200) according to approximately one embodiment of the present invention is inserted.

[0069] Here, although not shown in the drawing, it is preferable to press-fit the pin installation groove (150) after thermal epoxy treatment to improve heat transfer efficiency.

[0070] Additionally, the fin installation groove (150) may be arranged to pass through at least one of the heat-forming mating surfaces (not shown) formed to protrude while being recessed backward so as to accommodate the heat-forming surfaces of the heating elements on the inner surface corresponding to the rear side of the heat dissipation housing body (110). FIG. 2 is a perspective view showing a plate-type heat exchanger type heat dissipation fin assembly according to an embodiment of the present invention, FIG. 3 is an exploded perspective view showing one side heat exchange panel and the other side heat exchange panel of the configuration of FIG. 2 exploded, and FIG. 4 is an exploded perspective view of the detailed configuration of FIG. 3.

[0071] A plate-type heat exchanger type heat dissipation fin assembly (200) according to one embodiment of the present invention may include, as referenced in FIGS. 2 to 4, a heat exchange panel (200-1) on one side, a heat exchange panel (200-2) on the other side, a refrigerant flow space (205), and a gas-liquid refrigerant separation section (350).

[0072] The refrigerant flow space (205) may be formed as an empty space between one side heat exchange panel (200-1) and the other side heat exchange panel (200-2). The refrigerant flow space (205) may be filled with a refrigerant capable of phase change to evaporate from a liquid state to a gaseous state when heat is transferred from a predetermined heat source, such as a heat transfer element.

[0073] One side heat exchange panel (200-1) and the other side heat exchange panel (200-2) are manufactured in the shape of panels made of a predetermined metal material and can be formed by a sheet metal manufacturing method among the mold manufacturing methods.

[0074] Each one-sided heat exchange panel (200-1) and the other-sided heat exchange panel (200-2), formed by a sheet metal manufacturing method, can be joined by welding along the edge. At this time, the one-sided heat exchange panel (200-1) and the other-sided heat exchange panel (200-2) can be joined in a sealed manner so that the refrigerant filled in the internal refrigerant flow space (205) does not leak to the outside. More specifically, the one-sided heat exchange panel (200-1) and the other-sided heat exchange panel (200-2) can be joined together as shown in FIG. 3 to form a refrigerant flow space (205) in which the refrigerant filled inside can flow.

[0075] Here, one side heat exchange panel (200-1) and the other side heat exchange panel (200-2) can each be divided into an evaporation end (201) that is positioned close to the heat transfer element and receives a relatively large amount of heat from the heat transfer element, and a condensation end (203) that condenses the evaporated refrigerant through surface heat contact with the outside air, as the remaining part excluding the evaporation end (203).

[0076] Meanwhile, the evaporation end (201) and the condensation end (203) of the one-sided heat exchange panel (200-1) and the other-sided heat exchange panel (200-2) are not physically completely separated. That is, since the evaporation and condensation actions of the refrigerant may differ depending on the temperature distribution of heat transferred from the outside, in one embodiment of the present invention, the evaporation end (201) can be defined as a lower portion based on the direction of gravity where the liquid refrigerant is collected, as a portion where the evaporation action of the refrigerant is relatively active, and conversely, the condensation end (203) can be defined as the remaining portion excluding the evaporation end (201), as a portion where the condensation action of the refrigerant is relatively active.

[0077] In addition, since the one-sided heat exchange panel (200-1) and the other-sided heat exchange panel (200-2) receive heat from an unillustrated heat transfer element through the evaporation end (201) and perform the function of transferring heat to the upper part of the condensation end (203), which has a relatively long vertical width in the direction of gravity, as the remaining part other than the evaporation end (201), it is preferable that they be made of a metal material with excellent thermal conductivity.

[0078] Among existing metal materials, aluminum (or aluminum alloy) is generally the most preferred material in the relevant technical (industrial) field due to its excellent thermal conductivity; however, despite the excellent thermal conductivity of the aluminum (or aluminum alloy) material itself, the types of refrigerants that can be filled inside may be limited.

[0079] That is, when the materials of the one-sided heat conduction panel (200-1) and the other-sided heat conduction panel (200-2) are adopted as aluminum (or aluminum alloy), it is preferable that the refrigerant to be adopted as the refrigerant filled inside the refrigerant flow space (205) be one that does not undergo a chemical reaction with aluminum (or aluminum alloy). However, if the refrigerant is water, rapid oxidation (chemical reaction) occurs on the surface of the aluminum (or aluminum alloy) that comes into contact with water, generating hydrogen, and the generated hydrogen may cause a problem in which the internal pressure (internal pressure) of the refrigerant flow space (205) increases.

[0080] Accordingly, in the case of a plate-type heat exchanger type heat dissipation fin assembly (200) according to one embodiment of the present invention, the materials of the one-sided heat exchange panel (200-1) and the other-sided heat exchange panel (200-2) can be adopted as SUS (stainless steel) material, which causes almost no chemical reaction even when water (H2O) is adopted as a refrigerant.

[0081] For reference, if the heat exchange panel on one side (200-1) and the heat exchange panel on the other side (200-2) are made of aluminum (or aluminum alloy), water must inevitably be excluded as a refrigerant to minimize the chemical reaction described above, while the adoption of an expensive refrigerant such as Honeywell refrigerant or other phase-changeable refrigerants that can cause environmental pollution is unavoidable.

[0082] One side heat exchange panel (200-1) and the other side heat exchange panel (200-2) may be formed in a roughly rectangular shape as referenced in FIGS. 3 and 4, and may have a shape in which some of the four vertices are removed in a chamfered form. Here, an air vent tube (not shown) for vacuuming the refrigerant flow space (205) or filling the refrigerant flow space (205) may be provided at the joint portion of the chamfered one side heat exchange panel (200-1) and the other side heat exchange panel (200-2).

[0083] Hereinafter, for convenience of explanation, the sides forming one end and the other end in the longitudinal direction of the one side heat exchange panel (200-1) and the other side heat exchange panel (200-2) will be referred to as the ‘one side short side’ and the ‘other side short side’, and the sides forming one end and the other end in the width direction of the one side heat exchange panel (200-1) and the other side heat exchange panel (200-2) will be referred to as the ‘one side long side’ and the ‘other side long side’.

[0084] Meanwhile, the refrigerant flow space (205) may include a first refrigerant flow path (210), a second refrigerant flow path (220), and a third refrigerant flow path (330), as referenced in FIGS. 2 to 4.

[0085] The first refrigerant flow path (210) may be formed in a space corresponding to the lower side in the direction of gravity within the refrigerant flow space (205). The first refrigerant flow path (210) is a portion where the refrigerant evaporates from the liquid refrigerant into the gaseous refrigerant by receiving heat from the heat transfer element, and may be formed in a portion close to the evaporation end (201). Accordingly, the evaporation end (201) may be defined as the long side of the one side corresponding to the lower side in the direction of gravity among the long side of the one side heat exchange panel (200-1) and the long side of the other side heat exchange panel (200-2).

[0086] The second refrigerant passage (210) may be formed in the remaining space of the refrigerant flow space (205), excluding the portion of the first refrigerant passage (210) that corresponds to the lower side in the direction of gravity. The gaseous refrigerant evaporated from the first refrigerant passage (210) may diffuse toward the second refrigerant passage (220), and at the same time, the diffused gaseous refrigerant may be condensed into liquid refrigerant through heat exchange with the outside air, and may be formed across the entire condensation end (203).

[0087] Here, a plurality of second refrigerant passages (220) may be formed at the condensation end (203) so as to be inclined toward the first refrigerant passage (210). Each of the plurality of second refrigerant passages (220) may be formed extending from the side corresponding to the upper end relative to the direction of gravity of the one-sided heat exchange panel (200-1) and the other-sided heat exchange panel (200-2) toward the first refrigerant passage (210) formed on the side corresponding to the lower end relative to the direction of gravity. Here, the plurality of second refrigerant passages may be formed spaced apart so as to be parallel to each other in the length direction of the one-sided heat exchange panel (200-1) and the other-sided heat exchange panel (200-2).

[0088] A plurality of second refrigerant passages (220) serve to guide the flow of liquid refrigerant condensed at the condensation end (203) side toward the first refrigerant passage (210) formed below it. In particular, a plurality of second refrigerant passages (220) are formed in parallel and spaced apart at equal intervals, thereby ensuring that a uniform amount of liquid refrigerant is supplied to the first refrigerant passage (210) side.

[0089] For example, in the case where a plate heat exchanger type heat dissipation fin assembly (200) according to one embodiment of the present invention is installed at an angle with respect to any horizontal plane and a plurality of second refrigerant passages (220) are not provided, the condensed liquid refrigerant flows down in the direction of gravity and may flow unevenly toward the inclined first refrigerant passage (210). Additionally, since the first refrigerant passage (210) is arranged to be inclined itself, the amount of liquid refrigerant stored in the lower portion in the direction of gravity and the upper portion in the direction of gravity of the first refrigerant passage (210) may differ.

[0090] Here, the plurality of second refrigerant passages (220) induce a uniform supply of liquid refrigerant by causing the liquid refrigerant condensed at the condensation end (203) to flow down uniformly between one end and the other end in the longitudinal direction of the first refrigerant passage (210). In particular, when the absorbent body (300) described later is placed in the first refrigerant passage (210), the plurality of second refrigerant passages (220) induce a uniform amount of liquid refrigerant absorbed by the absorbent body (300).

[0091] A plurality of second refrigerant passages (220) can be externally distinguished by a plurality of inclined guides (215) formed between adjacent second refrigerant passages (220). More specifically, the plurality of inclined guides (215) are formed between each of the plurality of second refrigerant passages (220), and can be formed to be recessed to a predetermined depth toward the refrigerant flow space (205) from the outside of one heat exchange panel (200-1) and the other heat exchange panel (200-2). At this time, the plurality of inclined guides (215) can be formed to be recessed to a degree such that they do not come into contact with each other within the refrigerant flow space (205).

[0092] A plurality of third refrigerant passages (230) are each formed between a plurality of second refrigerant passages (220) and can be formed as a space smaller than the thickness of the second refrigerant passages (220). More specifically, the third refrigerant passages (230) are defined as a portion defined as a space in the thickness direction of a plurality of inclined guides (215), and can be defined as a spaced-apart space between a plurality of inclined guides (215) that are recessed on the outer side of one heat exchange panel (200-1) and the other heat exchange panel (200-2).

[0093] Here, if the thickness (i.e., the maximum thickness of the refrigerant flow space (205)) when the one-sided heat exchange panel (200-1) and the other-sided heat exchange panel (200-2) are joined together is denoted as "d", then a plurality of inclined guides (215) can be formed so as to be recessed by 'd / 3' toward the refrigerant flow space (205) from the outer surfaces of the one-sided heat exchange panel (200-1) and the other-sided heat exchange panel (200-2), respectively. Therefore, the thickness of the third refrigerant flow path (230) can be understood as 'd / 3'.

[0094] Meanwhile, a plurality of strength reinforcing members (240) may be formed in the plurality of inclined guides (215). The plurality of strength reinforcing members (240) may be formed in a dot-shaped groove shape, and may be formed in a groove shape so as to be recessed toward the refrigerant flow space (205) from the outside of the one-sided heat exchange panel (200-1) and the other-sided heat exchange panel (200-2).

[0095] A plurality of strength reinforcing members (240) may be formed by being recessed to the extent that they come into contact with each other in the refrigerant flow space (205). That is, the plurality of strength reinforcing members (240) may be formed by being recessed to have a depth of 'd / 6' in the inclined guide (215) of one heat exchange panel (200-1) and the inclined guide (215) of the other heat exchange panel (200-2), respectively, as they come into contact with each other within the thickness range of the third refrigerant flow path (230). The plurality of strength reinforcing members (240) that come into contact with each other in the refrigerant flow space (205) may be joined together by either a laser welding method or a brazing welding method.

[0096] Meanwhile, a plate-type heat exchanger type heat dissipation fin assembly (200) according to one embodiment of the present invention may further include an absorbent body (300) disposed along a first refrigerant path (210).

[0097] The absorber (300) may be provided as a wick member having a plurality of pores formed therein, in which the refrigerant filled in the refrigerant flow space (65) of the heat exchange panel (60) is easily absorbed and stored. The liquid refrigerant absorbed by the absorber (300) may evaporate due to heat transferred from the heat transfer element to the first refrigerant flow path (210), which is the evaporation end (201). At this time, the plurality of pores formed in the absorber (300) can increase the evaporation rate by maximizing the heat transfer surface area for the liquid refrigerant.

[0098] The phase change process of the refrigerant by the plate-type heat exchanger type heat dissipation fin assembly (200) according to one embodiment of the present invention, configured as described above, is briefly explained as follows.

[0099] The refrigerant filled in the refrigerant flow space (205) is stored and retained in a liquid refrigerant state on the side of the first refrigerant flow path (210) corresponding to the lower side with respect to the direction of gravity at room temperature. The liquid refrigerant is maintained in a state absorbed by the absorbent (300) disposed on the side of the first refrigerant flow path (210), and then evaporates into a gaseous refrigerant by the operating heat of the heat transfer element transferred to the evaporation end (201) side due to the operation of the heat transfer element, and diffuses to the condensation end (203) side.

[0100] The gaseous refrigerant diffused toward the condensation end (203) is condensed back into liquid refrigerant through heat exchange with the outside air, and the condensed liquid refrigerant flows down evenly toward the first refrigerant path (210) in the direction of gravity along the second refrigerant path (220) formed by a plurality of inclined guides (215). At this time, the gaseous refrigerant evaporated from the first refrigerant path (210) is diffused to the entire area of ​​the condensation end (203) through the third refrigerant path (230) corresponding to the space between the second refrigerant path (220) and a plurality of adjacent second refrigerant paths (220).

[0101] Here, when the heating element is a low-power heating element, the refrigerant cycle by phase change can be repeatedly performed smoothly without significant flow resistance between the diffusion flow of the gaseous refrigerant and the flow of the liquid refrigerant in the direction of gravity.

[0102] However, when the heating element is a high-output heating element, the likelihood of mutual collision occurring between the diffusion flow of the gaseous refrigerant and the flow of the liquid refrigerant in the direction of gravity increases. In particular, the flow resistance described above may increase as it approaches the first refrigerant flow path (210), where the evaporation action of the refrigerant is active. Due to such flow resistance between the refrigerants, there is even a risk of blockage of the flow path. Consequently, the flow resistance of the phase-change refrigerant not only impairs the smooth circulation of the refrigerant cycle but also causes vibration of the plate-type heat exchanger type heat dissipation fin assembly (200) according to one embodiment of the present invention, leading to unnecessary energy consumption and ultimately resulting in a problem of reduced heat dissipation performance.

[0103] Referring to FIGS. 2 to 4, a plate-type heat exchanger type heat dissipation fin assembly (200) according to one embodiment of the present invention may further include a gas-liquid refrigerant separation part (350) provided to prevent collision during mutual flow of gaseous refrigerant and liquid refrigerant as described above.

[0104] FIG. 5 is a perspective view showing the internal configuration of FIG. 2 with the other side heat exchange panel removed, FIG. 6 is a cutaway perspective view taken along line A-A' of FIG. 5, and FIG. 7 is an enlarged perspective view of part "B" of FIG. 6.

[0105] As referenced in FIGS. 5 to 7, the gas-liquid refrigerant separation unit (350) may be positioned between the space on the lower side in the direction of gravity and the space on the upper side of the refrigerant flow space (205). More specifically, the gas-liquid refrigerant separation unit (350) may be positioned in the condensation end (203) that is close to the first refrigerant flow path (210) formed on the lower side of the evaporator end (201) of the refrigerant flow space (205). That is, as described above, the evaporator end (201) is defined to be limited to the first refrigerant flow path (210), so it can be understood that the gas-liquid refrigerant separation unit (350) is positioned in the part closest to the first refrigerant flow path (210) among the condensation end (203) in which the second refrigerant flow path (220) and the third refrigerant flow path (230) are formed, excluding the first refrigerant flow path (210).

[0106] Here, the gas-liquid refrigerant separation unit (350) may be arranged to separate the second refrigerant flow path (220) and the third refrigerant flow path (230) in the thickness direction. More specifically, the gas-liquid refrigerant separation unit (350) may divide the thickness-direction space occupied by the second refrigerant flow path (220) into at least three sections. Each thickness of the second refrigerant flow path (220) divided by the gas-liquid refrigerant separation unit (350) may be 'd / 3' when the total thickness of the refrigerant flow space (205) formed inside the one-sided heat exchange panel (200-1) and the other-sided heat exchange panel (200-2) is 'd', as described above.

[0107] To this end, the gas-liquid refrigerant separation unit (350) may be provided as a pair. That is, the gas-liquid refrigerant separation unit (350) may include a one-side separation unit (350a) positioned on the side of one heat exchange panel (200-1) and a other-side separation unit (350b) positioned on the side of the other heat exchange panel (200-2).

[0108] The gas-liquid refrigerant separation unit (350) may be positioned to be in contact with the inner surface of a plurality of inclined guides (215) in the refrigerant flow space (205). That is, one separation unit (350a) may be positioned to be in contact with the inner surface protruding toward the refrigerant flow space (205) of a plurality of inclined guides (215) formed on one heat exchange panel (200-1), and the other separation unit (350b) may be positioned to be in contact with the inner surface protruding toward the refrigerant flow space (205) of a plurality of inclined guides (215) formed on the other heat exchange panel (200-1).

[0109] The gas-liquid refrigerant separation unit (350) is positioned close to the first refrigerant flow path (210) where the flow exchange between the gaseous refrigerant and the liquid refrigerant is most active, and can be positioned to separate the second refrigerant flow path (220) into three spaces in the thickness direction. That is, it can be separated into a first space (220a) corresponding to the space between the one-sided separation unit (350a) and the other-sided separation unit (350b), a second space (220-1) separated to the one-sided heat exchange panel (200-1) side by the one-sided separation unit (350a), and a third space (220-2) separated to the other-sided heat exchange panel (200-2) side by the other-sided separation unit (350b).

[0110] A plurality of reinforcing member penetration holes (355) may be formed to penetrate in the thickness direction in the gas-liquid refrigerant separation section (350). Here, a plurality of strength reinforcing members (240) formed on the side of the one-sided heat exchange panel (200-1) are exposed to the first space (220a) through a plurality of reinforcing member penetration holes (355) formed in the one-sided separation section (350a). Additionally, a plurality of strength reinforcing members (240) formed on the side of the other-sided heat exchange panel (200-2) are exposed to the first space (220a) through a plurality of reinforcing member penetration holes (355) formed in the other-sided separation section (350b). The respective strength reinforcing members (240) of the one-sided heat exchange panel (200-1) and the other-sided heat exchange panel (200-2) exposed to the first space (200a) may have their contacting leading edge portions joined by the welding method described above.

[0111] To this end, a plurality of reinforcement penetration holes (355) may be formed to correspond to the respective locations where a plurality of strength reinforcement members (240) are formed on one side heat exchange panel (200-1) and the other side heat exchange panel (200-2). When the gas-liquid refrigerant separation unit (350) is installed in the refrigerant flow space (205), it is installed so that a plurality of strength reinforcement members (240) penetrate through the reinforcement penetration holes (355), and can be stably fixed by the plurality of strength reinforcement members (240).

[0112] Meanwhile, the gas-liquid refrigerant separation unit (350) described above may be positioned above the absorber (300) in parallel with the absorber (300). Here, the absorber (300) may be provided as a pair. More specifically, one of the pair of absorbers (300) may be positioned to occupy a portion of the thickness direction of the first refrigerant flow path (210) on the side of the heat exchange panel (200-1) of the refrigerant flow space (205), and the other of the pair of absorbers (300) may be positioned to occupy a portion of the thickness direction of the first refrigerant flow path (210) on the side of the heat exchange panel (200-2) of the refrigerant flow space (205).

[0113] At this time, the space between the pair of absorbers (300) may be an empty space. This empty space on the first refrigerant path (210) may be a space where liquid refrigerant that is not absorbed by the pair of absorbers (300) is stored, and may be a space where gaseous refrigerant evaporated by the pair of absorbers (300) is discharged. The empty space here may be connected directly upward to the first space (220a) described above.

[0114] Additionally, each upper portion of a pair of absorbers (300) may be connected to a second space (220-1) and a third space (220-2) separated by a pair of gas-liquid refrigerant separation units (350). That is, the upper portion of the absorber (300) positioned on the side of one heat exchange panel (200-1) of the pair of absorbers (300) may be connected to the second space (220-1), and the upper portion of the absorber (300) positioned on the side of the other heat exchange panel (200-2) of the pair of absorbers (300) may be connected to the third space (220-2).

[0115] Therefore, the liquid refrigerant condensed at the condensation end (203) of one heat exchange panel (200-1) flows downward in the direction of gravity along the second refrigerant path (220), flows into the second space (220-1) which is separated from the first space (220a) by the one-sided separation part (350a), and can be absorbed into the upper side of the absorber (300) located directly below. Additionally, the liquid refrigerant condensed at the condensation end (203) of the other heat exchange panel (200-2) flows downward in the direction of gravity along the second refrigerant path (220), flows into the third space (220-2) which is separated from the first space (220a) by the other-sided separation part (350b), and can be absorbed into the upper side of the absorber (300) located directly below.

[0116] FIG. 8 is a front view of FIG. 2, FIG. 9 is a cross-sectional view taken along the line C-C' of FIG. 8 and an enlarged view of that part, and FIG. 10 is a partial cutaway perspective view taken along the line C-C' of FIG. 8.

[0117] Referring to FIGS. 8 to 10, the operation of the gas-liquid refrigerant separation unit (350) is briefly explained as follows.

[0118] Gaseous refrigerant evaporated from the first refrigerant path (210) can be rapidly diffused to the upper condensation end (203) side through the first space (220a) in the part equipped with a gas-liquid refrigerant separation unit (350). At this time, as described above, a void space is provided between a pair of absorbents (300) in the first refrigerant path (210), so that the gaseous refrigerant evaporated by the pair of absorbents (300) can be easily discharged into the void space. In addition, since the refrigerant flow space (205) is partitioned in the thickness direction by a pair of gas-liquid refrigerant separation units (350a, 350b) close to the first refrigerant path (210) side where the refrigerant evaporation action is relatively active, the evaporated gaseous refrigerant can be rapidly diffused through the first space (220a) which is connected directly upward.

[0119] Meanwhile, the liquid refrigerant condensed at the condensation end (203) can be easily guided downward in the direction of gravity along the second refrigerant flow path (220) corresponding to the second space (220-1) on the side of the heat exchange panel (200-1) and the third space (220-2) on the side of the heat exchange panel (200-2), respectively.

[0120] In this way, the gaseous refrigerant rapidly diffuses and flows through the first space (220a) partitioned by the gas-liquid refrigerant separation unit (350), and the liquid refrigerant is guided to flow downward through the second space (220-1) and the third space (220-2) partitioned by the gas-liquid refrigerant separation unit (350), thereby minimizing mutual collision between the gaseous refrigerant and the liquid refrigerant. As a result, blockage of the flow path of the phase change refrigerant can be prevented, and heat dissipation performance can be improved by promoting the circulation of the phase change refrigerant.

[0121]

[0122] For the above, a plate-type heat exchanger type heat dissipation fin assembly (200) according to one embodiment of the present invention has been described in detail with reference to the attached drawings. However, the embodiments of the present invention are not necessarily limited to the above-described embodiment, and it is obvious that various modifications and implementations within an equivalent scope are possible by those skilled in the art to which the present invention belongs. Therefore, the true scope of the rights of the present invention is determined by the claims set forth below.

[0123]

[0124] The present invention provides a plate-type heat exchanger type heat dissipation fin assembly capable of improving heat dissipation performance within a limited refrigerant flow space by minimizing the flow resistance of the refrigerant and reducing the phase change cycle interval of the refrigerant.

Claims

1. One-sided heat exchange panel; Another heat exchange panel forming a refrigerant flow space in which the refrigerant filled between the above-mentioned first heat exchange panel flows while undergoing a phase change; and A plate heat exchanger type heat dissipation fin assembly comprising: a gas-liquid refrigerant separation section disposed between the space relatively lower in the direction of gravity and the space upper in the refrigerant flow space.

2. In Claim 1, The above gas-liquid refrigerant separation unit is a plate-type heat exchanger type heat dissipation fin assembly that divides the refrigerant flow space into at least three spaces in the thickness direction.

3. In Claim 1, The above refrigerant flow space is, A first refrigerant flow path in which the refrigerant evaporates from a liquid refrigerant to a gaseous refrigerant, as a space located relatively below the direction of gravity; A plurality of second refrigerant passages formed inclined toward the first refrigerant passage and inducing flow to the lower part of the liquid refrigerant in which the gaseous refrigerant among the refrigerants has condensed; and A plurality of third refrigerant passages, each formed between the plurality of second refrigerant passages and formed as a space smaller than the thickness of the second refrigerant passages; comprising The above gas-liquid refrigerant separation unit is a plate-type heat exchanger type heat dissipation fin assembly positioned in close proximity to the first refrigerant flow path.

4. In Claim 3, The above gas-liquid refrigerant separation unit is a plate-type heat exchanger type heat dissipation fin assembly arranged to separate the second refrigerant path and the third refrigerant path in the thickness direction.

5. In Claim 3, The above gas-liquid refrigerant separation unit is a plate-type heat exchanger type heat dissipation fin assembly provided in pairs to partition the second refrigerant flow path to the one-sided heat exchange panel and the other-sided heat exchange panel, respectively.

6. In Claim 3, The above gas-liquid refrigerant separation section is a plate-type heat exchanger type heat dissipation fin assembly that divides the second refrigerant flow path into three sections with a thickness of 'd / 3', where the thickness of the refrigerant flow space is 'd'.

7. In Claim 5, The first refrigerant path is further provided with an absorbent that promotes the absorption and evaporation of the liquid refrigerant among the refrigerants, and The above gas-liquid refrigerant separation unit is a plate-type heat exchanger type heat dissipation fin assembly arranged parallel to the upper part of the absorbent.

8. In Claim 7, A plate-type heat exchanger type heat dissipation fin assembly, wherein the absorbers are provided as a pair arranged on the side of the one heat exchange panel and the side of the other heat exchange panel, and the space between the pair of absorbers is an empty space.

9. In Claim 3, The third refrigerant flow path is defined by a plurality of inclined guides formed such that the one-sided heat exchange panel and the other-sided heat exchange panel are each recessed toward the refrigerant flow space between the second refrigerant flow path, and The above gas-liquid refrigerant separation unit is a plate-type heat exchanger type heat dissipation fin assembly arranged to be in contact with the inner surface of the plurality of inclined guides in the refrigerant flow space.

10. In Claim 3, The above-mentioned gas-liquid refrigerant separation unit is, One side separator disposed on the side of the above-mentioned one-side heat exchange panel; and Includes an other side separator disposed on the other side heat exchange panel side; and The above-mentioned one-sided separator and the other-sided separator are a plate-type heat exchanger type heat dissipation fin assembly spaced apart by a predetermined distance in the thickness direction within the refrigerant flow space.

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