GRAVITY-DRIVEN GAS-LIQUID CIRCULATION DEVICE

Abstract

The present invention provides a gravity-driven gas-liquid circulation device, comprising a condensation unit and an evaporation unit. The condensation unit has an end connected to a gaseous phase input tube and another end connected to a liquid phase output tube. The evaporation unit comprises a thermally conductive base for contact with an external high-temperature device, a plurality of fins integrally formed on the thermally conductive base, and an integrally formed sealing housing provided on the thermally conductive base and enclosing the fins, wherein the integrally formed sealing housing is provided with a gas outlet hole and a liquid inlet hole, the gas outlet hole is lower than the gaseous phase input tube and is connected to an end of the gaseous phase input tube in order to guide a high-temperature gaseous-state working fluid through the gaseous phase input tube to the condensation unit, and the liquid inlet hole is level with or lower than the liquid phase output tube and is connected to an end of the liquid phase output tube in order to receive a liquid-state working fluid, allowing a force of gravity acting on the liquid-state working fluid to provide a siphoning force and thereby cause circulation of the liquid-state working fluid and the gaseous-state working fluid.

Description

BACKGROUND OF THE INVENTION

1. Technical Field

The present invention relates to a gas-liquid circulation device and more particularly to a miniaturized gravity-driven gas-liquid circulation device for use in an electronic product.

2. Description of Related Art

Electronic equipment is generally provided with a central processing unit (CPU) for processing commands and software data. The computation speed and data transfer rate of a piece of electronic equipment hinge on the performance of its CPU.

A CPU can maintain its performance or capacity at a reasonable level in most cases. If, however, the heat generated by a CPU cannot be dissipated effectively, the CPU may be overheated, and the electronic equipment using the CPU may eventually slow down or even stop working as a result. The high temperature of the overheated CPU may also damage the neighboring electronic components such that the service life of the electronic equipment is cut short. It is therefore imperative to use a suitable method or technique to cool a CPU sufficiently and thereby maintain its normal operation.

One typical technique for cooling the CPU of a piece of electronic equipment is to provide the electronic equipment with a built-in fan, the objective being to generate an air flow that helps bring down the temperature of the CPU. However, the cooling effect of the fan will be compromised when ambient temperature is high. Another cooling technique involves the use of a cooling agent or refrigerant such as water.

According to the above, the conventional methods for cooling a CPU still leave room for improvement. The inventor of the present invention thought it necessary to devise a novel method for cooling a CPU.

BRIEF SUMMARY OF THE INVENTION

The primary objective of the present invention is to provide a miniaturized gas-liquid circulation device that is suitable for use in electronic equipment.

In order to achieve the above objective, the present invention provides a gravity-driven gas-liquid circulation device, comprising a condensation unit and an evaporation unit. The condensation unit has an end connected to a gaseous phase input tube and another end connected to a liquid phase output tube. The evaporation unit comprises a thermally conductive base for contact with an external high-temperature device, a plurality of fins integrally formed on the thermally conductive base, and an integrally formed scaling housing provided on the thermally conductive base and enclosing the fins, wherein the integrally formed sealing housing is provided with a gas outlet hole and a liquid inlet hole, the gas outlet hole is lower than the gaseous phase input tube and is connected to an end of the gaseous phase input tube in order to guide a high-temperature gaseous-state working fluid through the gaseous phase input tube to the condensation unit, and the liquid inlet hole is level with or lower than the liquid phase output tube and is connected to an end of the liquid phase output tube in order to receive a liquid-state working fluid, allowing a force of gravity acting on the liquid-state working fluid to provide a siphoning force and thereby cause circulation of the liquid-state working fluid and the gaseous-state working fluid.

Furthermore, the thermally conductive base is provided thereon with a reinforcement member, wherein the reinforcement member is clamped vertically between the integrally formed sealing housing and the thermally conductive base and serves to increase the compressive strength.

Furthermore, the reinforcement member is provided with at least one through hole and/or at least one aperture to enable passage of the liquid-state working fluid.

Furthermore, the integrally formed sealing housing includes a first housing portion and a second housing portion. The first housing portion is provided on the thermally conductive base and encloses the fins. The second housing portion is integrally formed with, and lies on top of, the first housing portion.

Furthermore, the top sides of the tins are higher than the bottom edge, and lower than the top edge, of the liquid inlet hole or are higher than the top edge of the liquid inlet hole.

Furthermore, the gas outlet hole has a larger hole diameter than the liquid inlet hole.

Furthermore, the spacing between each two adjacent fins forms a flow channel, and the spacing ranges from 0.2 mm to 1 mm.

Furthermore, the liquid inlet hole is in alignment with the flow channels.

Furthermore, the fins are integrally formed on the thermally conductive base by a relieving means.

Furthermore, each fin has a thickness ranging from 0.2 mm to 1 mm.

Furthermore, the condensation unit comprises a front condensation assembly, a rear condensation assembly, and a plurality of heat dissipation fins. The front condensation assembly comprises a front left flow tube, a front right flow tube, and a plurality of front heat dissipation tubes. The front left flow tube and the front right flow tube are provided on two opposite lateral sides of the front condensation assembly respectively and are connected to the gaseous phase input tube and the liquid phase output tube respectively. The front heat dissipation tubes are in communication with the front left flow tube and the front right flow tube and are vertically spaced apart. The rear condensation assembly comprises a rear left flow tube, a rear right flow tube, and a plurality of rear heat dissipation tubes. The rear left flow tube and the rear right flow tube are provided on two opposite lateral sides of the rear condensation assembly respectively. The rear heat dissipation tubes are in communication with the rear left flow tube and the rear right flow tube and are vertically spaced apart. Gaps between the rear heat dissipation tubes and gaps between the front heat dissipation tubes correspond to each other and jointly form a plurality of through grooves. The heat dissipation fins are in contact with surfaces of the front heat dissipation tubes and surfaces of the rear heat dissipation tubes to enable heat exchange between the heat dissipation fins and the heat dissipation tubes. The front left flow tube and the rear left flow tube are separately formed. The front right flow tube and the rear right flow tube are separately formed.

Furthermore, the condensation unit comprises a front condensation assembly, a rear condensation assembly, and a plurality of heat dissipation fins. The front condensation assembly comprises a front left flow tube, a front right flow tube, and a plurality of front heat dissipation tubes. The front left flow tube and the front right flow tube are provided on two opposite lateral sides of the front condensation assembly respectively and are connected to the gaseous phase input tube and the liquid phase output tube respectively. The front heat dissipation tubes are in communication with the front left flow tube and the front right flow tube and are vertically spaced apart. The rear condensation assembly comprises a rear left flow tube, a rear right flow tube, and a plurality of rear heat dissipation tubes. The rear left flow tube and the rear right flow tube are provided on two opposite lateral sides of the rear condensation assembly respectively. The rear heat dissipation tubes are in communication with the rear left flow tube and the rear right flow tube and are vertically spaced apart. Gaps between the rear heat dissipation tubes and gaps between the front heat dissipation tubes correspond to each other and jointly form a plurality of through grooves. The heat dissipation fins are in contact with surfaces of the front heat dissipation tubes and surfaces of the rear heat dissipation tubes to enable heat exchange between the heat dissipation fins and the heat dissipation tubes. The front left flow tube and the rear left flow tube are jointly formed by two stamped plates. The front right flow tube and the rear right flow tube are jointly formed by two stamped plates.

Furthermore, at least one left opening is provided between the front left flow tube and the rear left flow tube. At least one right opening is provided between the front right flow tube and the rear right flow tube. The left opening and the right opening are diagonally arranged with respect to each other, wherein the bottom side of the left opening is higher than the top side of the right opening.

Furthermore, both the front heat dissipation tube and the rear heat dissipation tube have a flattened configuration.

Furthermore, the front heat dissipation tube is provided therein with a plurality of supporting ribs, which extend through the front heat dissipation tube. The rear heat dissipation tube is provided therein with a plurality of supporting ribs, which extend through the rear heat dissipation tube.

Furthermore, a plurality of microstructures are provided on the surface of each heat dissipation fin to increase the area of contact between each heat dissipation fin and air.

Furthermore, the heat dissipation fins have a corrugated configuration or a serrated configuration.

Furthermore, the condensation unit includes a plurality of condensation plate assemblies and a plurality of heat dissipation fins. The condensation plate assemblies are vertically spaced apart. The heat dissipation fins are inserted between the condensation plate assemblies and are therefore also spaced apart from one another. Each condensation plate assembly is provided with a left flow tube on the left side, a right flow tube on the right side, and a flow passage in communication with the left flow tube and the right flow tube, wherein the left flow tube and the right flow tube are connected to the gaseous phase input tube and the liquid phase output tube respectively.

Furthermore, each condensation plate assembly is formed by two metal plates, wherein each metal plate is provided with a plurality of protruding structures on the side facing the flow passage in order to increase the strength of the condensation plate assembly.

Comparing to the conventional techniques, the present invention has the following advantages:

The gas-liquid circulation device disclosed herein is provided with a condensation unit and an evaporation unit that utilize not only the phase change of a working fluid to cool an electronic product (i.e. the phase change taking place while the working fluid is changed between a heat-absorbing state and a heat-releasing state), but also the force of gravity acting on the working fluid to enable continuous operation of the gas-liquid circulation device, thereby saving the cost and space otherwise required for installing an electromechanical driving device.

BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWINGS

FIG. 1 is a perspective view of the gravity-driven gas-liquid circulation device of the present invention.

FIG. 2 is a sectional view of the front condensation assembly according to the first embodiment of the condensation unit of the present invention.

FIG. 3 is a sectional view of the rear condensation assembly according to the first embodiment of the condensation unit of the present invention.

FIG. 4 is a perspective view of the heat dissipation fin according to the first embodiment of the condensation unit of the present invention.

FIG. 5 is a perspective view of the front heat dissipation tube according to the first embodiment of the condensation unit of the present invention.

FIG. 6 is a perspective view of the evaporation unit of the present invention.

FIG. 7 is the sectional view (I) of the evaporation unit of the present invention.

FIG. 8 is the sectional view (II) of the evaporation unit of the present invention.

FIG. 9 is a schematic circulation diagram of the gravity-driven gas-liquid circulation device of the present invention.

FIG. 10 is a perspective view of the second embodiment of the condensation unit of the present invention.

FIG. 11 is a sectional view of the front condensation assembly according to the second embodiment of the condensation unit of the present invention.

FIG. 12 is a sectional view of the rear condensation assembly according to the second embodiment of the condensation unit of the present invention.

FIG. 13 is an assembled perspective view according to the third embodiment of the condensation unit of the present invention.

FIG. 14 is an exploded perspective view according to the third embodiment of the condensation unit of the present invention.

DETAILED DESCRIPTION OF THE INVENTION

The details and technical solution of the present invention are hereunder described with reference to accompanying drawings. For illustrative sake, the accompanying drawings are not drawn to scale. The accompanying drawings and the scale thereof are not restrictive of the present invention.

Please refer to FIG. 1 for a perspective view of the gravity-driven gas-liquid circulation device of the present invention.

The gravity-driven gas-liquid circulation device 100 shown in FIG. 1 is configured for use mainly in the fields of optics, communications, data processing, servers, and so on where high-heat laminated circuits are typically required. The present invention can be applied to such electronic products as servers, data displays, remote radio units (RRUs) for communication purposes, artificial intelligence (AI) devices, display chips, and laser chips to provide a cooling/heat dissipation effect through conduction-, convection-, or material-based heat exchange. The gas-liquid circulation device of the present invention is intended to dissipate heat from an electronic product via a continuously circulated working fluid that is driven by the force of gravity acting on the working fluid itself, thereby saving the cost and space otherwise required to drive the circulation electromechanically.

The gravity-driven gas-liquid circulation device 100 includes a condensation unit 10A and an evaporation unit 20A. A working fluid is circulated through the two units while undergoing a cyclic change of phase, which occurs when the working fluid is changed between a heat-absorbing state and a heat-releasing state. The phase change helps cool down the electronic product to which the gravity-driven gas-liquid circulation device 100 is applied, lest the electronic components of the product be damaged, or the performance of the product be lowered, due to prolonged exposure to high heat.

Please refer to FIG. 2 and FIG. 3 for sectional views respectively of the front and rear condensation assemblies of the condensation unit of the present invention.

In this embodiment, the condensation unit 10A is connected to a gaseous phase input tube AT at one end and a liquid phase output tube WT at another end. The condensation unit 10A includes a front condensation assembly 11A, a rear condensation assembly 12A, and a plurality of heat dissipation fins 13A. The front condensation assembly 11A includes a front left flow tube 111A, a front right flow tube 112A, and a plurality of front heat dissipation tubes 113A in communication with the front left flow tube 111A and the front right flow tube 112A. The front left flow tube 111A and the front right flow tube 112A are provided on the two opposite lateral sides of the front condensation assembly 11A respectively and are connected to the gaseous phase input tube AT and the liquid phase output tube WT respectively. The front heat dissipation tubes 113A are vertically spaced apart. The rear condensation assembly 12A is parallel to the front condensation assembly 11A and includes a rear left flow tube 121A, a rear right flow tube 122A, and a plurality of rear heat dissipation tubes 123A in communication with the rear left flow tube 121A and the rear right flow tube 122A. The rear left flow tube 121A and the rear right flow tube 122A are provided on the two opposite lateral sides of the rear condensation assembly 12A respectively. The rear heat dissipation tubes 123A are vertically spaced apart. The gaps between the rear heat dissipation tubes 123A and those between the front heat dissipation tubes 113A correspond to each other and jointly form a plurality of through grooves GA.

The front left flow tube 11A and the rear left flow tube 121A are separately formed, and so are the front right flow tube 112A and the rear right flow tube 122A. The two flow tubes on either lateral side of the condensation unit 10A are fixedly coupled to each other by a pair of sealing covers 114A (one on top and the other at the bottom) to increase the compressive strength of the flow tubes. The front left flow tube 111A, the front right flow tube 112A, the rear left flow tube 121A, and the rear right flow tube 122A are generally square tubes, with the sides facing diametrically away from the front heat dissipation tubes 113A (or the rear heat dissipation tubes 123A) having an outwardly protruding, (circularly) curved shape to allow more efficient use of the space inside the flow tubes.

To enable communication between the front condensation assembly 11A and the rear condensation assembly 12A, at least one left opening LO is provided between the front left flow tube 111A and the rear left flow tube 121A, and at least one right opening RO is provided between the front right flow tube 112A and the rear right flow tube 122A. In the preferred embodiment shown in FIG. 1, a linking element 115A is provided between the front left flow tube 111A and the rear left flow tube 121A and is aligned, and in communication, with the left opening LO so as to connect, and allow communication between, the flow tubes. Similarly, a linking element (not shown) is provided between the front right flow tube 112A and the rear right flow tube 122A and is aligned, and in communication, with the right opening RO. As shown in FIG. 2, there is one left opening LO and one right opening RO, and the two openings are rectangular openings diagonally arranged with respect to each other, wherein the bottom side of the left opening LO is higher than the top side of the right opening RO. The area of the left opening LO is larger than that of the right opening RO to enable rapid input and slow output of the working fluid. It should be pointed out, however, that the openings described above serve only as an example; the present invention imposes no limitation on the number or shapes of those openings.

Please refer to FIG. 4 for a perspective view of a heat dissipation fin in the condensation unit of the present invention.

The heat dissipation fins 13A are inserted in the through grooves GA respectively and extend through the front condensation assembly 11A and the rear condensation assembly 12A. The heat dissipation fins 13A are in contact with the surfaces of the front heat dissipation tubes 113A and of the rear heat dissipation tubes 123A so that heat exchange can take place between the heat dissipation fins 13A and the heat dissipation tubes 113A and 123A. The heat dissipation fins 13A may have a corrugated configuration, a serrated configuration, or any other configuration achievable by bending a metal plate. Each heat dissipation fin 13A has a height D1 ranging from 4 mm to 8 mm and a length D2 ranging from 12 mm to 60 mm. The distance D3 between each two adjacent bends of each heat dissipation fin 13A ranges from 2 mm to 4 mm. There are a plurality of microstructures 131A on the surface of each heat dissipation fin 13A. The microstructures 131A may extend outward or inward with respect to the heat dissipation fins 13A to increase the area of contact between each heat dissipation fin 13A and air, thereby enhancing the efficiency of heat dissipation. 10052j Please refer to FIG. 5 for a perspective view of a front heat dissipation tube in the condensation unit of the present invention.

As shown in FIG. 5, the front heat dissipation tube 113A has a flattened configuration. The two ends of the front heat dissipation tube 113A are inserted in the front left flow tube 111A and the front right flow tube 112A respectively to connect the two flow tubes together. The front heat dissipation tube 113A has a height D4 ranging from 1 mm to 2 mm to facilitate passage of, and allow sufficient heat absorption by, the working fluid. The front heat dissipation tube 113A has a width D5 ranging from 12 mm to 40 mm so as to provide a relatively large heat dissipation area that enhances contact, and hence heat exchange, with air and the adjacent heat dissipation fins 13A. The front heat dissipation tube 113A is provided therein with a plurality of supporting ribs R, which extend through the front heat dissipation tube 113A. The number of the supporting ribs R may range from the value of one half of the width (in millimeter) of the front heat dissipation tube 113A to the value of the full width (in millimeter) of the front heat dissipation tube 113A. For example, when the width of the front heat dissipation tube 113A is 12 mm, there may be 6 to 12 supporting ribs R for reinforcing, and thereby preventing deformation of, the front heat dissipation tube 113A. The rear heat dissipation tubes 123A in the present invention are structurally identical to the front heat dissipation tubes 113A and therefore will not be described or shown repeatedly.

Please refer to FIG. 6 to FIG. 8 in conjunction with FIG. 1, wherein FIG. 6 to FIG. 8 respectively show a perspective view and two different sectional views of the evaporation unit of the present invention.

The evaporation unit 20A includes a thermally conductive base 21A for contact with a high-temperature device, a plurality of fins 22A integrally formed on the thermally conductive base 21A, and an integrally formed sealing housing 23A provided on the thermally conductive base 21A to enclose the fins 22A. In this preferred embodiment, the thermally conductive base 21A, the fins 22A, and the integrally formed sealing housing 23A are made of aluminum or copper. The integrally formed sealing housing 23A includes a first housing portion 231A and a second housing portion 232A. The first housing portion 231A is provided on the thermally conductive base 21A and encloses the fins 22A. The second housing portion 232A is integrally formed with, and lies on top of, the first housing portion 231A. The interior space of the second housing portion 232A is smaller than that of the first housing portion 231A to accelerate the working fluid. The thermally conductive base 21A is provided with a plurality of locking holes 211A for securing the evaporation unit 20A to a high-temperature device.

The integrally formed sealing housing 23A is provided with a gas outlet hole 233A, which is lower than the gaseous phase input tube AT and is connected to one end of the gaseous phase input tube AT in order to guide the high-temperature gaseous-state working fluid through the gaseous phase input tube AT to the condensation unit 10A. The integrally formed scaling housing 23A is also provided with a liquid inlet hole 234A, which is level with or lower than the liquid phase output tube WT and is connected to one end of the liquid phase output tube WT in order to receive the liquid-state working fluid. The force of gravity acting on the liquid-state working fluid will provide a siphoning force that causes circulation of the working fluid, thereby enabling the gravity-driven gas-liquid circulation device 100 to operate continuously without being driven by an electromechanical means. In this preferred embodiment, the gas outlet hole 233A has a larger hole diameter than the liquid inlet hole 234A to make it easier for the force of gravity acting on the liquid-state working fluid to serve as a driving force of the gravity-driven gas-liquid circulation device 100.

The fins 22A are integrally formed on the thermally conductive base 21A by a relieving means. Each fin 22A has a thickness ranging from 0.2 mm to 1 mm to facilitate rapid heat exchange with the liquid-state working fluid. The spacing S between each two adjacent fins 22A forms a flow channel 221A. The spacing S ranges from 0.2 mm to 1 mm so that the liquid-state working fluid can flow through the flow channels 221A with ease to carry out heat exchange with the fins 22A sufficiently.

The liquid inlet hole 234A is in alignment with the flow channels 221A. The top sides H of the fins 22A may be higher than the bottom edge, and lower than the top edge, of the liquid inlet hole 234A or be higher than the top edge of the liquid inlet hole 234A, the objective being to allow as much liquid-state working fluid as possible to flow through the flow channels 221A and thereby increase the heat absorption efficiency of the evaporation unit 20A.

The thermally conductive base 21A is provided thereon with a reinforcement member 24A. The reinforcement member 24A is clamped vertically between the integrally formed sealing housing 23A and the thermally conductive base 21A and serves to increase the compressive strength, and thereby prevent deformation of, the evaporation unit 20A. The reinforcement member 24A is provided with at least one through hole 241A and at least one aperture 242A to enable passage of the liquid-state working fluid. Or, the reinforcement member 24A may have only the through hole(s) 241A or the aperture(s) 242A; the present invention has no limitation in this regard.

Please refer to FIG. 9 for a schematic circulation diagram of the gravity-driven gas-liquid circulation device of the present invention.

The liquid-state working fluid in the condensation unit 10A is guided into the evaporation unit 20A through the liquid phase output tube WT. Meanwhile, the force of gravity acting on the liquid-state working fluid provides a siphoning force such that the gaseous-state working fluid in the evaporation unit 20A is driven into the condensation unit 10A through the gaseous phase input tube AT. Thus, the gravity-driven gas-liquid circulation device 100 forms a continuous heat exchange cycle without having to be driven by an electromechanical means.

The following paragraphs describe the second preferred embodiment of the condensation unit of the disclosed gravity-driven gas-liquid circulation device. The second embodiment is different from the foregoing embodiment only in the structure of the flow tubes, so the remaining structures of the condensation unit, as well as the evaporation unit, will not be described repeatedly.

Please refer to FIG. 10 to FIG. 12 respectively for a perspective view of the second embodiment of the condensation unit of the present invention, a sectional view of the front condensation assembly of the condensation unit, and a sectional view of the rear condensation assembly of the condensation unit.

As shown in FIG. 10 to FIG. 12, the condensation unit 10B includes a front condensation assembly 11B, a rear condensation assembly 12B, and a plurality of heat dissipation fins 13B. The front condensation assembly 11B includes a front left flow tube 111B, a front right flow tube 112B, and a plurality of front heat dissipation tubes 113B in communication with the front left flow tube 111B and the front right flow tube 112B. The front left flow tube 111B and the front right flow tube 112B are provided on the two opposite lateral sides of the front condensation assembly 11B respectively and are connected to the gaseous phase input tube and the liquid phase output tube respectively. The front heat dissipation tubes 113B are vertically spaced apart. The rear condensation assembly 12B is parallel to the front condensation assembly 11B and includes a rear left flow tube 121B, a rear right flow tube 122B, and a plurality of rear heat dissipation tubes 123B in communication with the rear left flow tube 121B and the rear right flow tube 122B. The rear left flow tube 121B and the rear right flow tube 122B are provided on the two opposite lateral sides of the rear condensation assembly 12B respectively. The rear heat dissipation tubes 123B are vertically spaced apart. The gaps between the rear heat dissipation tubes 123B and those between the front heat dissipation tubes 113B correspond to each other and jointly form a plurality of through grooves GB.

The front left flow tube 111B and the rear left flow tube 121B are jointly formed by two stamped plates, including an M-shaped stamped plate and a square U-shaped stamped plate. The front right flow tube 112B and the rear right flow tube 122B are also jointly formed by an M-shaped stamped plate and a square U-shaped stamped plate. The stamped plates are intended to increase the compressive strength of the flow tubes. The two flow tubes on either lateral side of the condensation unit 10B are provided with a pair of scaling covers 114B (one on top and the other at the bottom). The front left flow tube 111B, the front right flow tube 112B, the rear left flow tube 121B, and the rear right flow tube 122B have an outwardly protruding, (circularly) curved shape on the sides facing diametrically away from the front heat dissipation tubes 113B or the rear heat dissipation tubes 123B, in order to allow more efficient use of the space inside the flow tubes.

The heat dissipation fins 13B are inserted in the through grooves GB respectively and extend through the front condensation assembly 11B and the rear condensation assembly 12B. The heat dissipation fins 13B are in contact with the surfaces of the front heat dissipation tubes 113B and of the rear heat dissipation tubes 123B so that heat exchange can take place between the heat dissipation fins 13B and the heat dissipation tubes 113B and 123B. The heat dissipation fins 13B may have a corrugated configuration, a serrated configuration, or any other configuration achievable by bending a metal plate. There are a plurality of microstructures on the surface of each heat dissipation fin 13B. The microstructures may extend outward or inward with respect to the heat dissipation fins 13B to increase the area of contact between each heat dissipation fin 13B and air, thereby enhancing the efficiency of heat dissipation.

To enable communication between the front condensation assembly 11B and the rear condensation assembly 12B, at least one left opening LO1 is provided between the front left flow tube 111B and the rear left flow tube 121B, and at least one right opening RO1 is provided between the front right flow tube 112B and the rear right flow tube 122B. In this embodiment, there is one left opening LO1 and one right opening RO1, and the two openings are diagonally arranged with respect to each other, wherein the bottom side of the left opening LO1 is higher than the top side of the right opening RO1. It should be pointed out, however, that the openings described above serve only as an example; the present invention imposes no limitation on the number or shapes of those openings.

The following paragraphs describe the third preferred embodiment of the condensation unit of the disclosed gravity-driven gas-liquid circulation device. The third embodiment is structurally different from the previous two embodiments, and yet the corresponding evaporation unit is the same as those for use with the foregoing two embodiments (and hence will not be described repeatedly).

Please refer to FIG. 13 and FIG. 14 respectively for an assembled perspective view and an exploded perspective view of the third embodiment of the condensation unit of the present invention.

As shown in FIG. 13 and FIG. 14, the condensation unit 10C includes a plurality of condensation plate assemblies 11C and a plurality of heat dissipation fins 12C. The condensation plate assemblies 11C are vertically spaced apart. The heat dissipation fins 12C are inserted between the condensation plate assemblies 11C and are therefore also spaced apart from one another. Each condensation plate assembly 11C is provided with a left flow tube 111C on the left side, a right flow tube 112C on the right side, and a flow passage 113C in communication with the left flow tube 111C and the right flow tube 112C to allow passage of the gaseous-state working fluid, wherein the left flow tube 111C and the right flow tube 112C are connected to the gaseous phase input tube and the liquid phase output tube respectively.

Each heat dissipation fin 12C is inserted between, and in contact with the surfaces of, two adjacent condensation plate assemblies 11C to enable heat exchange between the heat dissipation fin 12C and the two condensation plate assemblies 11C. The heat dissipation fins 12C may have a corrugated configuration, a serrated configuration, or any other configuration achievable by bending a metal plate. There are a plurality of microstructures on the surface of each heat dissipation fin 12C. The microstructures may extend outward or inward with respect to the heat dissipation fins 12C to increase the area of contact between each heat dissipation fin 12C and air, thereby enhancing the efficiency of heat dissipation.

Each condensation plate assembly 11C is formed by two metal plates P, wherein each metal plate P is provided with a plurality of protruding structures P on the side facing the flow passage 113C in order to increase the strength of the condensation plate assembly 11C. The protruding structures P1 of each metal plate P are formed by stamping the metal plate P and are preferably cylindrical or dome-shaped so that each pair of metal plates P can be soldered together with ease.

According to the above, the gas-liquid circulation device disclosed herein uses the force of gravity acting on the liquid-state working fluid to drive the gaseous-state working fluid as well as the liquid-state working fluid to circulate continuously in the device, thereby eliminating the need for an additional electromechanical driving device.

The above is the detailed description of the present invention. However, the above is merely the preferred embodiment of the present invention and cannot be the limitation to the implement scope of the present invention, which means the variation and modification according to the present invention may still fall into the scope of the invention.

Claims

1. A gravity-driven gas-liquid circulation device, comprising:

a condensation unit having an end connected to a gaseous phase input tube and another end connected to a liquid phase output tube; and

an evaporation unit comprising a thermally conductive base for contact with an external high-temperature device, a plurality of fins integrally formed on the thermally conductive base, and an integrally formed sealing housing provided on the thermally conductive base and enclosing the fins, wherein the integrally formed sealing housing is provided with a gas outlet hole and a liquid inlet hole, the gas outlet hole is lower than the gaseous phase input tube and is connected to an end of the gaseous phase input tube in order to guide a high-temperature gaseous-state working fluid through the gaseous phase input tube to the condensation unit, and the liquid inlet hole is level with or lower than the liquid phase output tube and is connected to an end of the liquid phase output tube in order to receive a liquid-state working fluid, allowing a force of gravity acting on the liquid-state working fluid to provide a siphoning force and thereby cause circulation of the liquid-state working fluid and the gaseous-state working fluid.

2. The gravity-driven gas-liquid circulation device of claim 1, wherein the thermally conductive base is provided thereon with a reinforcement member, wherein, the reinforcement member is clamped vertically between the integrally formed sealing housing and the thermally conductive base and serves to increase the compressive strength.

3. The gravity-driven gas-liquid circulation device of claim 2, wherein the reinforcement member is provided with at least one through hole and/or at least one aperture to enable passage of the liquid-state working fluid.

4. The gravity-driven gas-liquid circulation device of claim 1, wherein the integrally formed sealing housing includes a first housing portion and a second housing portion; the first housing portion is provided on the thermally conductive base and encloses the fins; and, the second housing portion is integrally formed with, and lies on top of, the first housing portion.

5. The gravity-driven gas-liquid circulation device of claim 1, wherein the top sides of the fins are higher than the bottom edge, and lower than the top edge, of the liquid inlet hole or are higher than the top edge of the liquid inlet hole.

6. The gravity-driven gas-liquid circulation device of claim 1, wherein the gas outlet hole has a larger hole diameter than the liquid inlet hole.

7. The gravity-driven gas-liquid circulation device of claim 1, wherein the spacing between each two adjacent fins forms a flow channel, and the spacing ranges from 0.2 mm to 1 mm.

8. The gravity-driven gas-liquid circulation device of claim 7, wherein the liquid inlet hole is in alignment with the flow channels.

9. The gravity-driven gas-liquid circulation device of claim 1, wherein the fins are integrally formed on the thermally conductive base by a relieving means.

10. The gravity-driven gas-liquid circulation device of claim 1, wherein each fin has a thickness ranging from 0.2 mm to 1 mm.

11. The gravity-driven gas-liquid circulation device of claim 1, wherein the condensation unit comprises a front condensation assembly, a rear condensation assembly, and a plurality of heat dissipation fins; the front condensation assembly comprises a front left flow tube, a front right flow tube, and a plurality of front heat dissipation tubes; the front left flow tube and the front right flow tube are provided on two opposite lateral sides of the front condensation assembly respectively and are connected to the gaseous phase input tube and the liquid phase output tube respectively; the front heat dissipation tubes are in communication with the front left flow tube and the front right flow tube and are vertically spaced apart; the rear condensation assembly comprises a rear left flow tube, a rear right flow tube, and a plurality of rear heat dissipation tubes; the rear left flow tube and the rear right flow tube are provided on two opposite lateral sides of the rear condensation assembly respectively; the rear heat dissipation tubes are in communication with the rear left flow tube and the rear right flow tube and are vertically spaced apart; gaps between the rear heat dissipation tubes and gaps between the front heat dissipation tubes correspond to each other and jointly form a plurality of through grooves; the heat dissipation fins are in contact with surfaces of the front heat dissipation tubes and surfaces of the rear heat dissipation tubes to enable heat exchange between the heat dissipation fins and the heat dissipation tubes; the front left flow tube and the rear left flow tube are separately formed; and, the front right flow tube and the rear right flow tube are separately formed.

12. The gravity-driven gas-liquid circulation device of claim 1, wherein the condensation unit comprises a front condensation assembly, a rear condensation assembly, and a plurality of heat dissipation fins; the front condensation assembly comprises a front left flow tube, a front right flow tube, and a plurality of front heat dissipation tubes; the front left flow tube and the front right flow tube are provided on two opposite lateral sides of the front condensation assembly respectively and are connected to the gaseous phase input tube and the liquid phase output tube respectively; the front heat dissipation tubes are in communication with the front left flow tube and the front right flow tube and are vertically spaced apart; the rear condensation assembly comprises a rear left flow tube, a rear right flow tube, and a plurality of rear heat dissipation tubes; the rear left flow tube and the rear right flow tube are provided on two opposite lateral sides of the rear condensation assembly respectively; the rear heat dissipation tubes are in communication with the rear left flow tube and the rear right flow tube and are vertically spaced apart; gaps between the rear heat dissipation tubes and gaps between the front heat dissipation tubes correspond to each other and jointly form a plurality of through grooves; the heat dissipation fins are in contact with surfaces of the front heat dissipation tubes and surfaces of the rear heat dissipation tubes to enable heat exchange between the heat dissipation fins and the heat dissipation tubes; the front left flow tube and the rear left flow tube are jointly formed by two stamped plates; and, the front right flow tube and the rear right flow tube are jointly formed by two stamped plates.

13. The gravity-driven gas-liquid circulation device of claim 11, wherein at least one left opening is provided between the front left flow tube and the rear left flow tube; at least one right opening is provided between the front right flow tube and the rear right flow tube; and, the left opening and the right opening are diagonally arranged with respect to each other, wherein the bottom side of the left opening is higher than the top side of the right opening.

14. The gravity-driven gas-liquid circulation device of claim 11, wherein both the front heat dissipation tube and the rear heat dissipation tube have a flattened configuration.

15. The gravity-driven gas-liquid circulation device of claim 11, wherein the front heat dissipation tube is provided therein with a plurality of supporting ribs, which extend through the front heat dissipation tube; and, the rear heat dissipation tube is provided therein with a plurality of supporting ribs, which extend through the rear heat dissipation tube.

16. The gravity-driven gas-liquid circulation device of claim 11, wherein a plurality of microstructures are provided on the surface of each heat dissipation fin to increase the area of contact between each heat dissipation fin and air.

17. The gravity-driven gas-liquid circulation device of claim 11, wherein the heat dissipation fins have a corrugated configuration or a serrated configuration.

18. The gravity-driven gas-liquid circulation device of claim 1, wherein the condensation unit includes a plurality of condensation plate assemblies and a plurality of heat dissipation tins; the condensation plate assemblies are vertically spaced apart; the heat dissipation fins are inserted between the condensation plate assemblies and are therefore also spaced apart from one another; and, each condensation plate assembly is provided with a left flow tube on the left side, a right flow tube on the right side, and a flow passage in communication with the left flow tube and the right flow tube, wherein the left flow tube and the right flow tube are connected to the gaseous phase input tube and the liquid phase output tube respectively.

19. The gravity-driven gas-liquid circulation device of claim 18, wherein each condensation plate assembly is formed by two metal plates; wherein, each metal plate is provided with a plurality of protruding structures on the side facing the flow passage in order to increase the strength of the condensation plate assembly.