LOOP-TYPE HEAT EXCHANGE DEVICE

Abstract

A loop-type heat exchange device (10) is disclosed, which includes an evaporator (20), a condenser (40), a vapor conduit (30) and a liquid conduit (50). The evaporator defines therein a chamber for containing a working fluid. The chamber is divided into an evaporating region and a micro-channel region. The working fluid in the evaporator evaporates into vapor after absorbing heat at the evaporating region, and the generated vapor flows, via the vapor conduit, to the condenser where the vapor releases its latent heat of evaporation and is condensed into condensate. The condensate then returns back, via the liquid conduit, to the evaporator to thereby form a heat transfer loop. The evaporator is configured in such a manner that an amount of vapor to be formed and accumulated in the micro-channel region can be minimized.

Description

FIELD OF THE INVENTION

The present invention relates generally to an apparatus for transfer or dissipation of heat from heat-generating components, and more particularly to a loop-type heat exchange device suitable for removing heat from electronic components.

DESCRIPTION OF RELATED ART

As progress continues to be made in electronic industries, electronic components such as integrated circuit chips are produced to have more powerful functions while maintaining a unchanged size or even a smaller size. As a result, the amount of heat generated by these electronic components during their normal operations is commensurately increased, which in turn will adversely affect their workability and stability. It is well known that cooling devices are commonly used to remove heat from heat-generating components. However, currently well-known cooling devices such as heat sink plus cooling fan are no longer qualified or desirable for removing the heat from these electronic components due to their low heat removal capacity. Conventionally, increasing the rotation speed of the cooling fan and increasing the size of the heat sink are two approaches commonly used to improve the heat dissipating performance of the cooling device involved. However, if the rotation speed of the cooling fan is increased, problems such as large noise will inevitably be raised. On the other hand, by increasing the size of the heat sink, it will make the cooling device bulky, which contravenes the current trend towards miniaturization.

Currently, an advantageous mechanism for more effectively removing the heat from these electronic components and overcoming the aforementioned disadvantages is adopted, which is related to use of heat pipe technology. Heat pipes are an effective heat transfer means due to their low thermal resistance. A heat pipe is usually a vacuum casing containing therein a working fluid. Preferably, a wick structure is provided inside the heat pipe, lining an inner wall of the casing. The heat pipe has an evaporating section for receiving heat from a heat-generating component and a condensing section for releasing the heat absorbed by the evaporating section. When the heat is inputted into the heat pipe via its evaporating section, the working fluid contained therein absorbs the heat and turns into vapor. Due to the difference of vapor pressure between the two sections of the heat pipe, the generated vapor moves, with the heat being carried, towards the condensing section where the vapor is condensed into condensate after releasing the heat into ambient environment by, for example, fins thermally contacting the condensing section. Due to the difference of capillary pressure developed by the wick structure between the two sections, the condensate is then drawn back by the wick structure to the evaporating section where it is again available for evaporation.

In the heat pipe, however, there still exists a fatal drawback awaited to be overcome. The movement of the vapor is countercurrent to that of the condensate within the casing of the heat pipe. The movement of the vapor will, to a certain extent, produce a resistance to the flow of the condensate due to an interaction between the vapor and the condensate. This negative effect will lower down the speed of the condensate in supplying to the evaporating section of the heat pipe. If the condensate is not timely sent back to the evaporating section, the heat pipe will suffer a dry-out problem at that section.

In order to overcome the drawback of the conventional heat pipe, a loop-type heat exchange device has been proposed. The loop-type heat exchange device includes an evaporator, a condenser, a vapor conduit and a liquid conduit. The evaporator defines therein a chamber for containing a working fluid. The vapor and liquid conduits each are connected between the evaporator and the condenser by two individual pipes. Specifically, the working fluid in the evaporator evaporates into vapor after absorbing the heat from the heat-generating component, and the generated vapor then flows, via the vapor conduit, to the condenser where the vapor is condensed into condensate after releasing its latent heat of evaporation. The condensate then returns back to the evaporator via the liquid conduit to thereby be available again for evaporation, thus forming a heat transfer loop. One of the advantages of the loop-type heat exchange device in relation to the conventional heat pipe is that the vapor and the condensate move separately and do not interfere with each other.

In practice, however, many improvements still can be made on the design of the loop-type heat exchange device in order to exhibit its full advantages. For example, since both the vapor conduit and the liquid conduit are connected to the evaporator, if no effective mechanism is provided to prevent the vapor generated in the evaporator from moving backwards towards and entering into the liquid conduit, a situation that the vapor flows in the liquid conduit along a direction countercurrent to that of the condensate will happen. In this situation, the loop-type heat exchange device cannot have an optimal heat dissipation performance. Furthermore, the irregular movement of the vapor into the liquid conduit also produces significant resistance to the condensate to enter the evaporator, which will prevent the condensate from being supplied to the place where the evaporation of the working fluid is effectuated. If the condensate is not brought back to that place timely due to the influence of the vapor, a dry-out problem will accordingly be raised in the evaporator.

Therefore, it is desirable to provide a loop-type heat exchange device which overcomes the foregoing disadvantages.

SUMMARY OF INVENTION

The present invention relates to a loop-type heat exchange device for removing heat from a heat-generating component. The heat exchange device includes an evaporator, a condenser, a vapor conduit and a liquid conduit. The evaporator defines therein a chamber for containing a working fluid. The chamber is divided into two regions. The working fluid is capable of turning into vapor in the evaporator upon receiving the heat at one region of said chamber from the heat-generating component. Each of the vapor and liquid conduits is connected between the evaporator and the condenser. The vapor generated in the evaporator is capable of being transferred via the vapor conduit to the condenser and turning into condensate in the condenser upon releasing the heat carried by the vapor. The condensate is capable of being transferred via the liquid conduit to the evaporator. The heat exchange device further includes means formed on the evaporator for reducing an amount of vapor being accumulated in the other region of the chamber of the evaporator.

In one embodiment of the present heat exchange device, said means for reducing the amount of vapor being accumulated in the other region of the chamber of the evaporator is a cooling device thermally connected to the evaporator corresponding to that region. The cooling device may be a plurality of cooling fins connected to an outer surface of the evaporator. In an alternative embodiment, the evaporator includes a top cover and a bottom cover cooperating with each other to define the chamber of the evaporator and said means is a projected section from the bottom cover corresponding to the one region of the chamber of the evaporator. The cooling device is capable of condensing that portion of vapor having entered into the other region of the chamber and meanwhile maintaining a low temperature for that region. The projected section of the bottom cover is used to receive the heat from the heat-generating component and functions for reducing an amount of the heat to be conducted from the projected section to the remaining part of the bottom cover and finally to the other region of the chamber. On this basis, the vapor formed and accumulated in the other region of the chamber is reduced to a minimum amount and the unidirectional working fluid movement mechanism along the heat transfer loop established by the present heat exchange device is well followed, thus effectively taking the heat away from the heat-generating component.

Other advantages and novel features of the present invention will become more apparent from the following detailed description of preferred embodiment when taken in conjunction with the accompanying drawings, in which:

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is an isometric view of a loop-type heat exchange device in accordance with a first embodiment of the present invention;

FIG. 2 is a cross-sectional view of an evaporator of the loop-type heat exchange device of FIG. 1, taken along line II-II thereof;

FIG. 3 is an isometric view of the evaporator of the loop-type heat exchange device of FIG. 1, with a top cover thereof being removed;

FIG. 4 is a bottom plan view of the evaporator of the loop-type heat exchange device of FIG. 1;

FIG. 5 is an isometric view of a loop-type heat exchange device in accordance with a second embodiment of the present invention; and

FIG. 6 is an isometric view of a loop-type heat exchange device in accordance with a third embodiment of the present invention.

DETAILED DESCRIPTION

FIG. 1 illustrates a loop-type heat exchange device 10 in accordance with a first embodiment of the present invention. The heat exchange device 10 includes an evaporator 20, a vapor conduit 30, a condenser 40 (shown in broken lines) and a liquid conduit 50. The evaporator 20 preferably is made of two separable portions connected together, as will be discussed in more detail later. The vapor and liquid conduits 30, 50 lie in parallel to each other, although they are not limited to this relationship. Two ends of each of the vapor and liquid conduits 30, 50 are respectively connected to the evaporator 20 and the condenser 40. The vapor and liquid conduits 30, 50 preferably are made of flexible metal or non-metal materials so that they could be bent or flattened easily in order to cause the heat exchange device 10 to be applicable in electronic products having a limited mounting space such as notebook computers.

The evaporator 20 contains therein a working fluid (not shown). As heat from a heat source (not shown) is applied to the evaporator 20, the working fluid contained in the evaporator 20 evaporates into vapor after absorbing the heat. Then, the generated vapor flows, via the vapor conduit 30, to the condenser 40 where the vapor releases its latent heat of evaporation and is thus condensed into condensate. The condensate then returns back from the condenser 40, via the liquid conduit 50, to the evaporator 20 where it is again available for evaporation, thus forming a heat transfer loop. In the present heat transfer device 10, the movements of the vapor and the condensate are carried out respectively and separately in the vapor conduit 30 and the liquid conduit 50.

In the present heat exchange device 10, the condenser 40 is used to dissipate the heat carried by the vapor. Although the condenser 40 located between the vapor conduit 30 and the liquid conduit 50 is schematically shown in broken lines, it is well known by those skilled in the art that the condenser 40 may take various forms, including metal fins, cooling devices (typically including heat sinks and cooling fans), or liquid cooling systems. For example, if the vapor conduit 30 and the liquid conduit 50 are an integral pipe, as shown in FIG. 1, the condenser 40 may be a plurality of fins stacked on the pipe between the vapor and liquid conduits 30, 50. However, the condenser 40 may also be designed to include a hollow casing defined therein a chamber, and a plurality of fins attached to an outer surface of the casing. In this situation, the vapor conduit 30 and the liquid conduit 50 are preferably discrete members, each with a distal end portion being inserted into the chamber of the casing. Thus, the generated vapor in the evaporator 20 is firstly guided to the chamber of the casing, and then the heat carried in the vapor is conducted to the fins outside the chamber of the casing for further dissipation.

With reference to FIGS. 2-4, the evaporator 20 of the present heat exchange device 10 has a plate-type configuration, which includes a top cover 210 and a bottom cover 220. The top and bottom covers 210, 220 cooperate with each other to define a chamber (not labeled) inside the evaporator 20. The bottom cover 220 includes a first, thinner section 221 and a second, thicker section 223 extending from the first section 221. The second section 223 projects downwardly to an extent below the first section 221 with a step (not labeled) formed between the first and second sections 221, 223. As shown in FIGS. 2 and 4, a protrusion 225 is formed by extending further downwardly from a central portion of the second section 223 of the bottom cover 220. A first wick structure 230 is arranged inside the evaporator 20. The first wick structure 230 defines therein a plurality of micro-channels (not labeled) for storage of and providing passageways for the working fluid contained in the evaporator 20. The first wick structure 230 is preferably in the form of sintered powder or a screen mesh made of metal wires or organic fibers woven together. The working fluid contained in the evaporator 20 is saturated in the first wick structure 230. The working fluid is injected into the evaporator 20 via a small tube 203 inserted into the evaporator 20, as shown in FIG. 3. The working fluid is usually selected from liquids such as water or alcohol. Then, the evaporator 20 is vacuumed and the tube 203 is sealed.

Corresponding to the first and second sections 221, 223 of the bottom cover 220 of the evaporator 20, an interior of the chamber of the evaporator 20 is divided into two major regions, i.e., a liquid micro-channel region 231 and an adjacent evaporating region 232. The micro-channel region 231 is fully filled with the first wick structure 230. A portion of the first wick structure 230 extends from the micro-channel region 231 into a middle part of the evaporating region 232 between opposite front and rear sides of the evaporator 20 as viewed from FIG. 3. This portion of the first wick structure 230 has a size substantially equal to that of the protrusion 225 of the bottom cover 220, and is fittingly located above that protrusion 225. Additionally, another portion of the first wick structure 230 also extends from the micro-channel region 231 into opposite front and rear sides of the evaporating region 232. As a result, the first wick structure 230 spans across both the micro-channel region 231 and the evaporating region 232 of the chamber of the evaporator 20. The vapor and liquid conduits 30, 50 are connected to the evaporating region 232 and the micro-channel region 231, respectively. The remaining part of the evaporating region 232 not filled with the first wick structure 230 functions as a vapor-gathering section 233 for accommodating the generated vapor. This vapor-gathering section 233 is communicated with the vapor conduit 30 so as to enable the generated vapor to leave the evaporator 20 and go into the vapor conduit 30. Additionally, corresponding to the micro-channel region 231, each of the top and bottom covers 210, 220 of the evaporator 20 has a plurality of metal fins 250 extending from an outer surface thereof, as shown in FIG. 2.

Preferably, a second wick structure 501 is arranged against an inner surface of the liquid conduit 50 in order to bring the condensate resulting from the vapor back from the condenser 40 to the evaporator 20 timely, as shown in FIG. 3. The second wick structure 501 may be fine grooves integrally formed at the inner surface of the liquid conduit 50, screen mesh or bundles of fiber inserted into the liquid conduit 50, or sintered powder combined to the inner surface of the liquid conduit 50 by a sintering process. Thus, the condensate in the condenser 40 is capable of being timely sent back to the evaporator 20 under a capillary force developed by the second wick structure 501, thereby avoiding the potential dry-out problem occurring at the evaporator 20.

In operation, the protrusion 225 of the evaporator 20 is maintained into thermal contact with the heat source. Preferably, a layer of thermal interface material is applied over their contacting surfaces in order to reduce thermal resistance. The heat generated by the heat source is firstly transferred to the projected second section 223 of the bottom cover 220 and then to the evaporating region 232 of the chamber of the evaporator 20 to cause the working fluid contained in that region to evaporate into the vapor after absorbing the heat from the heat source. Since the micro-channel region 231 is filled with the first wick structure 230, the generated vapor then enters into the vapor-gathering section 233 for temporary storage. Thereafter, due to the difference of vapor pressure between the evaporator 20 and the condenser 40, the vapor accordingly goes into the vapor conduit 30 and moves towards the condenser 40. After the vapor releases its latent heat in the condenser 40 and turns into the condensate, the condensate is then rapidly drawn back to the micro-channel region 231 of the chamber of the evaporator 20 via the liquid conduit 50 due to the capillary force of the second wick structure 501. Since an inventory of working fluid in the evaporating region 232 is reduced due to the evaporation in that region, the condensate returned to the micro-channel region 231 is subsequently drawn to the evaporating region 232 for being available again for evaporation as a result of the capillary force developed by the first wick structure 230, thus forming the heat transfer loop for continuously and effectively removing the heat generated by the heat source. In the present heat exchange device 10, the working fluid takes the heat away from the heat source specially in the unidirectional, circular manner along the heat transfer loop, when the working fluid continuously undergoes phase transitions from liquid to vapor and then from vapor to liquid (condensate). Due to the presence of the first wick structure 230 in the micro-channel region 231, which is saturated by the condensate, the vapor generated in the evaporating region 232 is prevented from moving towards the micro-channel region 231 and proceeding therefrom to the liquid conduit 50.

In order to reduce an amount of vapor to be formed and accumulated in the micro-channel region 231, it is preferred to prevent the condensate returned to and stored in that region from being directly heated and evaporated into vapor, since the thus generated vapor will accumulate in that region and accordingly produce a large resistance to the flow of the condensate towards the evaporating region 232. If the condensate is not timely sent to the evaporating region 232 due to the resistance of the vapor accumulated in the micro-channel region 231, a dry-out problem will be raised in the evaporating region 232. On the other hand, the vapor accumulated in the micro-channel region 231 will also has the chance to enter into and march along the liquid conduit 50, which will disorder the heat transfer mechanism along the heat transfer loop established by the present heat exchange device 10. In the present heat exchange device 10, the heat coming from the heat source is directly transferred to the second, thicker section 223 of the bottom cover 220. The two-section design of the bottom cover 220 is aimed to reduce an amount of the heat from the heat source to be conducted from the second, thicker section 223 to the thinner first section 221 and finally to the micro-channel region 231 of the evaporator 20. Since the second, thicker section 223 has a larger thickness than the first section 221, the heat conducted laterally from the second, thicker section 223 towards the first section 221 is thus capable of being effectively reduced. As a result, the heat transferred from the first section 221 of the bottom cover 220 to the micro-channel region 231 of the evaporator 20 is also effectively reduced, and thus excessive vapor is prevented from being formed and accumulated in that region. The condensate temporarily stored in the micro-channel region 231 is accordingly capable of being timely supplied to the evaporating region 232.

Since the micro-channel region 231 is connected with the adjacent evaporating region 232, a portion of the vapor generated in the evaporating region 232 will “creep” from the evaporating region 232 into the micro-channel region 231 due to a large vapor pressure in the vapor-gathering section 233. That is, a specific amount of the vapor generated in the evaporating region 232 will gradually move towards and enter into the micro-channel region 231 due to the large vapor pressure. In addition, the temperature in the micro-channel region 231 will also gradually increase, subject to a relatively high temperature and a flow of the vapor in the evaporating region 232. Thus, in order to reduce the vapor to be brought into and accumulated in the micro-channel region 231 to a minimum amount, it is also preferred to lower the temperature in the micro-channel region 231. In the present heat exchange device 10, the metal fins 250 formed on the top and bottom covers 210, 220 of the evaporator 20 corresponding to the micro-channel region 231 are applied to directly condense that portion of vapor having crept into the micro-channel region 231 into condensate at that region and on the other hand to maintain a relatively low temperature for the micro-channel region 231. In practice, the metal fins 250 may be substituted with other cooling devices such as cooling fans or thermoelectric cooling devices. The metal fins 250 preferably have a low height and are integrally formed with the top and bottom covers 210, 220 so as to minimize the size of the evaporator 20.

In the present heat exchange device 10, the condensate resulting from the vapor after releasing its latent heat in the condenser 40 is sent back to the evaporator 20 for being available again for evaporation under the capillary force developed by the second wick structure 501 arranged in the liquid conduit 50. With respect to the evaporator 20, the two-section design of the bottom cover 220 and the presence of the metal fins 250 on both the top and bottom covers 210, 220 cooperatively maintain a low temperature for the micro-channel region 231 of the evaporator 20 and effectively reduce the amount of vapor to be formed and accumulated in that region, thus enabling the condensate returned to the evaporator 20 to be supplied from the micro-channel region 231 to the evaporating region 232 of the evaporator 20 timely and eliminating the potential dry-out problem occurring at the evaporating region 232. As a result, the unidirectional working liquid movement mechanism along the heat transfer loop established by the present heat exchange device 10 is well followed and the heat generated by the heat source is taken away effectively.

FIG. 5 shows a loop-type heat exchange device (not labeled) in accordance with a second embodiment of the present invention. In this embodiment, the heat exchange device is provided with two heat transfer loops in order to increase its heat removal capacity, thus making it applicable for removing heat from heat-generating components with a high cooling requirement.

FIG. 6 shows a loop-type heat exchange device (not labeled) in accordance with a third embodiment of the present invention. In this embodiment, the heat exchange device includes two heat transfer loops and in each heat transfer loop two vapor conduits 30 are provided so as to reduce a resistance to the vapor generated in the evaporator 20 as it flows towards the condenser 40. To attain this purpose (i.e., reducing resistance to the vapor), the vapor conduit 30 may also be made to have a larger diameter than the liquid conduit 50 so as to enable the generated vapor to move towards the condenser 40 effectively and smoothly.

It is to be understood, however, that even though numerous characteristics and advantages of the present invention have been set forth in the foregoing description, together with details of the structure and function of the invention, the disclosure is illustrative only, and changes may be made in detail, especially in matters of shape, size, and arrangement of parts within the principles of the invention to the full extent indicated by the broad general meaning of the terms in which the appended claims are expressed.

Claims

1. A heat exchange device comprising:

an evaporator defining therein a chamber for containing a working fluid, the chamber being divided into two regions, the working fluid being capable of turning into vapor in the evaporator upon receiving heat at one region of said chamber;

a condenser;

a vapor conduit and a liquid conduit each being connected between the evaporator and the condenser, wherein the vapor generated in the evaporator is capable of being transferred via the vapor conduit to the condenser and turning into condensate in the condenser upon releasing the heat, and the condensate is capable of being transferred via the liquid conduit to the evaporator; and

means formed on the evaporator for reducing an amount of vapor being accumulated in the other region of said chamber.

2. The heat exchange device of claim 1, wherein said means is a cooling device thermally connected to the evaporator at a location corresponding to the other region of said chamber.

3. The heat exchange device of claim 2, wherein the cooling device includes a plurality of cooling fins connected to an outer surface of the evaporator.

4. The heat exchange device of claim 1, wherein the evaporator includes a top cover and a bottom cover cooperating with each other to define said chamber, and said means is a protrusion section projecting downwardly from the bottom cover corresponding to the one region of said chamber.

5. The heat exchange device of claim 1, wherein a wick structure is arranged inside the liquid conduit.

6. The heat exchange device of claim 1, wherein a wick structure is arranged inside the evaporator spanning across the two regions of said chamber.

7. The heat exchange device of claim 6, wherein the one region of said chamber is partially filled with the first wick structure and the other region of said chamber is fully filled with the wick structure.

8. The heat exchange device of claim 7, wherein a portion of the wick structure extends from the other region of said chamber into a middle part of the one region of said chamber.

9. The heat exchange device of claim 1, wherein the vapor conduit and the liquid conduit are flexible.

10. The heat exchange device of claim 1, further comprising another vapor conduit connected between the evaporator and the condenser.

11. The heat exchange device of claim 1, further comprising another condenser, another vapor conduit and another liquid conduit, the another vapor conduit and the another liquid conduit each being connected between the another condenser and said evaporator.

12. A heat exchange device comprising:

an evaporator defining therein a chamber for containing a first wick structure and a working fluid saturated in the first wick structure, the chamber being divided into two regions, the first wick structure spanning across both the two regions of the chamber, the working fluid being capable of turning into vapor in the evaporator upon receiving heat at one region of said chamber;

a condenser; and

a vapor conduit and a liquid conduit each being connected between the evaporator and the condenser, the liquid conduit having a second wick structure arranged therein, wherein the vapor generated in the evaporator is capable of being transferred via the vapor conduit to the condenser and turning into condensate in the condenser upon releasing the heat, and the condensate is capable of being transferred via the liquid conduit to the other region of said chamber of said evaporator under a capillary force developed by the second wick structure.

13. The heat exchange device of claim 12, wherein a plurality of cooling fins is thermally connected to an outer surface of the evaporator corresponding to the other region of said chamber.

14. The heat exchange device of claim 12, wherein the evaporator includes a top cover and a bottom cover cooperating with each other to define said chamber, and the bottom cover has a section being thicker than the remaining part of the bottom cover, the section corresponding to the one region of said chamber.

15. A loop heat exchanging device having working fluid therein comprising:

an evaporator having a first region accommodating therein a first wick structure and a second region having a part adapted for receiving heat from a heat generating component for heating the working fluid into vapor;

a vapor conduit having a first end communicating with the second region of the evaporator so that the vapor can enter the vapor conduit and a second end;

a condenser communicating with the second end of the vapor conduit, in the condenser the vapor being condensed to condensate; and

a condensate conduit having a first end communicating with the condenser so that the condensate can enter the condensate conduit and a second end communicating with the first region of the evaporator so that the condensate in the condensate conduit can enter the first region of the evaporator to saturate the first wick structure.

16. The loop heat exchanging device of claim 15, wherein the condensate conduit accommodates a second wick structure therein.

17. The loop heat exchanging device of claim 16, wherein the first wick structure extends to the part of the second region of the evaporator for receiving heat from the heat generating component.

18. The loop heat exchanging device of claim 17, wherein the part of the second region of the evaporator is located at a middle of the second region and the first wick structure extends further to two sides of the second region.

19. The loop heat exchanging device of claim 17, wherein the evaporator has outwardly extending fins at the first region.

20. The loop heat exchanging device of claim 19, wherein the evaporator has an outer wall, the outer wall having first portion and second portion corresponding to the first and second regions, respectively, the second portion being thicker than the first portion.