US20030111217A1

US20030111217A1 - Bubble cycling heat exchanger system

Info

Publication number: US20030111217A1
Application number: US10/355,010
Authority: US
Inventors: Jia Li
Original assignee: Individual
Current assignee: Individual
Priority date: 2000-04-10
Filing date: 2003-01-31
Publication date: 2003-06-19

Abstract

A bubble cycling heat exchanger system includes a closed fluid cycling loop containing a working fluid therein for removing heat from a heat source thermally coupled to a longitudinally extended heat-conducting block. The closed fluid cycling loop is contacted in proximity to the beat-conducting block with only one side portion thereof near the heat source for establishing a temperature difference and a density difference of the working fluid to aid in achieving a unidirectional flow therein.

Description

CROSS-REFERENCE TO RELATED APPLICATIONS

This Application is a Continuation-in-Part application of prior application Ser. No. 09/546,604 filed Apr. 10, 2000.[0001]

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to a bubble cycling heat exchanger system, and especially to a closed fluid cycling loop, which will form a cold flow and a hot flow for performing a steady heat exchange.

2. Description of the Related Art

A general heat-pipe type radiator includes a closed vacuum chamber filled with proper working fluid therein, a plurality of radiating fins are installed thereon, and a capillary section is installed in the chamber. The heating way is to heat one end of the chamber so as to boil and evaporate the working fluid. The heat is transferred from a hot section at one side to a cold section at another side. After the gas is condensed to become liquid at the cold section. The liquid flows back due to gravitation or capillary force. Thus, due to the structure of the heat pipe, the amount of heat to be transferred will be deteriorated with the increment of an operation inclination. Due to the capillary force from the structure of the heat pipe, if overheat occurs, a dry-out will be induced. Once dry-out occurs, no liquid flows back, and the heating area are full of high temperature gas so that only gas phase exists. Therefore, temperature will increase dramatically so that heat supper conduction in the heat pipe is fail and thus the effect is reduced greatly. Furthermore, the non-condensing gas in the heat pipe must be exhausted completely otherwise super conduction will be affected. Moreover, since an operation inclination exists, the heat pipe is possibly moved or folded. Accordingly, it is apparent that heat pipe has some original disadvantages necessary to be improved. Therefore, there has an eager demand for an improved heat exchanger system.

SUMMARY OF THE INVENTION

Accordingly, the primary object of the present invention is to provide a bubble cycling heat exchanger system, wherein an original pushing force is formed by a temperature difference and density difference as the liquid is heated, bubbles will generate and then an unbalance guide is used to guide the bubbles, so that a steady flow is generated in the closing loop and thus, heat in each heat source is driven to a heat dissipating section unidirectionally under a steady control, then the fluid flow back. The returning flow will not mix with the output flow. By various designs, a preferred heat dissipating effect is achieved.

Another object of the present invention is to provide a bubble cycling heat exchanger system, wherein the loop itself has a flow-returning tube which will flow through the heat source, so that each coil of the loop will obtain a longitudinal temperature uniformity, and a transversal temperature uniformity will also be achieved, and thus, heat transfer is more effective.

In accordance with one aspect of the present invention, a closing fluid cycling loop includes a plurality of spiral tubes being interlaced together in proximity one to another and thermally coupled to a heat source through a heat conductive block, and each of the loops containing a working fluid therein. The plurality of spiral tubes each are contacted in proximity to the heat conducting block with only one side portion thereof near the heat source for establishing a temperature difference and a density difference of the working fluid with respect to two side portions of each loop, so as to aid in achieving a unidirectional flow therein; whereby, when each loop is radiated continuously, the working fluid in each loop will generate bubbles, and flow of the working fluid at one side portion of each of the loops will be suppressed and flow of working fluid at the opposing side portion will be guided to flow, so that a unidirectional steady heat transfer is performed to the working fluid in each of the loops.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a perspective view of the first embodiment in the present invention. [0009]
FIG. 2 is a schematic view of the first embodiment in the present invention. [0010]
FIG. 3 is a schematic view of the second embodiment in the present invention. [0011]
FIG. 4 is a schematic view of the third embodiment in the present invention. [0012]
FIG. 5 is a schematic view of the fourth embodiment in the present invention. [0013]
FIG. 6 is a schematic view of the fifth embodiment in the present invention. [0014]
FIG. 7 is a perspective view of the sixth embodiment in the present invention. [0015]
FIG. 8 is a schematic view of the sixth embodiment in the present invention. [0016]
FIG. 9 is a perspective view of the seventh embodiment in the present invention. [0017]
FIG. 10 is a schematic view of the seventh embodiment in the present invention. [0018]
FIG. 11 is a schematic view of the eighth embodiment in the present invention. [0019]
FIG. 12 is a perspective view of the ninth embodiment in the present invention. [0020]
FIG. 13 is a perspective view of the tenth embodiment in the present invention. [0021]
FIG. 14 is a schematic view of the tenth embodiment in the present invention. [0022]
FIG. 15 is a schematic view of the eleventh embodiment in the present invention. [0023]
FIG. 16 is a schematic view of the twelfth embodiment in the present invention. [0024]
FIG. 17 is a schematic view of the thirteenth embodiment in the present invention. [0025]
FIG. 18 is a schematic view of the fourteenth embodiment in the present invention. [0026]
FIG. 19 is a schematic view of the fifteenth embodiment in the present invention. [0027]
FIG. 20 is a schematic view of the sixteenth embodiment in the present invention. [0028]
FIG. 20A is a perspective view of the sixteenth embodiment in the present invention. [0029]
FIG. 20B is an exploded view of FIG. 20A. [0030]
FIG. 21 is a schematic view of the seventeenth embodiment in the present invention. [0031]
FIG. 22 is a schematic view of the eighteenth embodiment in the present invention.[0032]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

With reference to FIGS. [0033] 1 to 22, the eighteen embodiments of the bubble cycling heat exchanger system according to the present invention are illustrated. In these embodiments, a closing fluid cycling loop 1 is in contact with a heat source 3 through a heat-conducting block 2. The loop 1 has a bubble generator 40 and an expansion section 4 for generating bubbles in the fluid loop 1. The loop 1 is adhered to or near the heat-conducting block 2 and is asymmetric in left and right sides. Only one side of the loop 1 is near the heat source 3, so that two sides of the loop 1 are formed with a temperature difference and density difference, and thus a unidirectional flow is achieved. As the loop 1 is radiated continuously, it will generate bubbles. Since the asymmetry in the heat flow structure, the fluid flowing in one side will be suppressed. Meanwhile, the fluid in the opposite side will be guided to flow, so that the fluid in the loop will be in a unidirectional steady heat transfer. By the guiding due to unbalance in a guiding section 5, the bubbles in the loop 1 will rapidly flow away from the heat-conducting block 2. Then, by the guiding owing to the unbalance of the guiding section 5, the bubbles in the loop 1 will rapidly flow away from some part of the heat-conducting block 2, so that the fluid in the loop 1 can flow unidirectionally and steadily. Then, by matching a plurality of radiating fins 7 of a radiating body 6 and a fan 8, heat will be guided out of the heat source. The loop 1 operates continuously until a thermal equilibrium is achieved.
The first embodiment of the present invention is illustrated in FIGS. 1 and 2. A [0034] single cycle loop 1 is provided, which is a continuous spiral tube as a general spring. It can be easily manufactured and shaped for reducing the whole manufacturing cost. The number of the coils of the loop 1 is dependent on the number of the heat sources. The lower end of the loop 1 is adhered to the heat-conducting block 2. The joint of the loop 1 and the heat-conducting block 2 is shifted to one side so as to be formed with a condition of loop unbalance. The loops of first coil and second coil each have a round shape.
However, the second embodiment shown in FIG. 3 has an elliptic shape. The third embodiment shown in FIG. 4 has a single circle form formed by two arc sections, one of which is long, while the other of which is short. The fourth embodiment show in FIG. 5 has an inner loop and an outer loop, which are engaged with one another and are tilt at one side. Similarly, the fifth embodiment shown in FIG. 6 has three cycles, which are engaged with each other. The flow-returning tube [0035] 9 has a distal end, which is returned from the loop to be connected to the head portion of the tube. A filling block 10 is existed at the joint. By the filling block 10, liquid can be filled into the loop 1.
Moreover, as the sixth embodiment shown in FIGS. 7 and 8, a [0036] right loop 1R and a left loop 1L are crossed with one another and are used simultaneously. Other than each loop can be used and operated independently. Another characters of this design are that the left loop 1L is guided out through the filling block 10 and then is formed as a spiral shape and extends backwards. The rear end thereof further extends forwards through a straight tube of a loop tube 9L. The outer end of the straight tube is connected to the initial portion of another loop of the right loop 1R. The distal end of the loop 1R extends forwards through a flow-returning tube 9R to be connected to the filling block 10. Therefore, a flow cycle of single loop is formed. Since in a spiral lying type loop, the effect of heat transfer is that temperature is uniform in the longitudinal direction. But it only has a limited effect about the temperature uniformity in the transversal direction. In order to solve the temperature balance problem, the flow-returning tubes 9R and 9L run across the circle of the loop. In one case, the flow-returning tubes 9 are closely adhered to the loop above the heat-conducting block 2 so as to be formed with a simplest structure for temperature uniformity in the transversal direction. While parts of the flow-returning tube 9 is unnecessary to pass through the middle portion of the ring. It can be installed out of the ring and can be installed to resist against the to sides of the heat-conducting block 2. This is a preferred structure under the consideration of temperature uniformity and is helpful for the heat-conducting block 2 to have a steadier heat dissipating structure. The seventh and eighth embodiments are illustrated in FIGS. 9 and 10, wherein a pair of alternative arranged loops 1L and 1R are illustrated, and a loop 1 is at the middle portion. In the ninth embodiment shown in FIG. 11, a further loop 1W is arranged at outer side of the loops 1L and 1R.
In the aforesaid structure, the loop is adhered to the surface of the heat-conducting [0037] block 2. In general, the loops are made of copper tube or aluminum tube. The heat-conducting block 2 can be made of a copper block or a material with a preferred conductivity. Soldering and brazing serves to combine the heat conductive block and the loop. In another type, part of the loop passes through the heat conductive block. As the ninth embodiment shown in FIG. 12, two ends of the loop 1 are connected to the two sides of the heat-conducting block 2. In FIG. 12, a line serves to represent the loop 1. Moreover, a returning flow channel 20 or a connecting channel is installed at the heat-conducting block 2 for achieving the function of transversal temperature uniformity. Then, a plug 2 serves to seal the output of the channel 20. The function thereof is identical to the filling opening of the filling block 10. The filling opening is sealed as liquid has completely filled.
Since the loop itself has the function of heat dissipation, as the radiating area is not sufficient, at each cycle of the loop is arranged with a radiating [0038] fin 7 as the tenth embodiment shown in FIGS. 13 and 14. It is a single loop. Moreover, it can be designed as the eleventh embodiment shown in FIG. 15, radiating fins 7 are further installed on the alternative arranged loops 1L and 1R. The radiating fins 7 are parallel to the cycle of the loop. If can be installed at another direction. As the twelfth embodiment shown in FIG. 16, the fins 7 are arranged in parallel to the direction of the returning tube. This also has the function of transversal temperature uniformity.
Besides, the heat transferred to the [0039] loop 1 and the radiating fins 7 must be removed rapidly so as not to accumulate heat energy, and thus, fan 8 for heat dissipation is installed out of the loop 1. In the thirtieth embodiment shown in FIG. 17, a stand fan 8 is installed at a proper position of the fin 7. By the air fluid flow from the fan, the cold air is driven to flow into the space in the loop 1 continuously. In the fourteenth embodiment shown in FIG. 18, the fan 8 is lay on the outer cycle of the loop 1. In the fifteenth embodiment shown in FIG. 19, the fan 8 is installed on the left and right loops.
In the sixteenth embodiment shown in FIG. 20, the [0040] fan 8 is installed with the closed fluid cycling loop 1 that is crossed arranged. Since the closed fluid cycling loop 1 can be designed as various different shapes, for example, a round shape, an ellipse shape a rectangle shape and a trapezoid shape in a cross-sectional contour, etc. They are being fabricated according to practical requirement for matching the desire in heat dissipation. It is a perspective view of the sixteenth embodiment shown in FIG. 20A, and an exploded view of FIG. 20 shown in FIG. 20B. The present invention provides a bubble cycling heat exchanger system with a closed fluid cycling loop 1 containing a working fluid therein, wherein the closed fluid cycling loop 1 includes a plurality of spiral tubes 11R, 11L and 11M being interlaced together in proximity one to another and each defining a plurality of longitudinally arranged coils 110R, 110L and 110M; and a plurality of flow-returning tubes 9R, 9L and 9M each having two opposing ends respectively connected to corresponding opposing ends of each of said spiral tubes 11R, 11L and 11M thereby to longitudinally pass through an inner perimeter of each of the coils 110R, 110L and 110M each of said spiral tubes 11R, 11L and 11M; wherein said coils 110R and 110L each have a left-half portion and a right-half portion of an asymmetric cross-sectional contour thereof with respect to a heat source thermally coupled to a heat-conducting block 2 for establishing a temperature difference and a density difference of the working fluid to aid in achieving a unidirectional flow therein.
Furthermore, a [0041] left spiral tube 11L of the plurality of spiral tubes has a substantial trapezoid shape in a cross-sectional contour, wherein flow of the working fluid at one side of the loop will be suppressed and flow of the working fluid at an opposing side of the loop will be guided to flow, and thereby to transfer heat in a first predetermined direction.
Another a [0042] right spiral tube 11R of the plurality of spiral tubes has a substantial trapezoid shape in a cross-sectional contour, wherein flow of the working fluid at one side of the loop will be suppressed and flow of the working fluid at an opposing side of the loop will be guided to flow, and thereby to transfer heat in a second predetermined direction, wherein the first predetermined direction is opposite to the second predetermined direction.
Additionally, a [0043] middle spiral tube 11M of the plurality of spiral tubes has a first joint end and a second joint end connected to a first joint end of said right spiral tube 11R, said right spiral tube 11R has a second joint end connected to a first joint end of said left spiral tube 11L, and said left spiral tube 11L has a second joint end connected to said first joint end of said middle spiral tube 11M for generating a circulating flow.
Besides, as the eighteenth embodiment shown in FIG. 21, the left and right three loops are connected to a heat-conducting [0044] block 2 which are connected to the loops at two sides by a protrusion 22.
Furthermore, as the eighteenth embodiment shown in FIG. 22, an [0045] expansion section 4 for generating bubbles is installed at a tube of the loop 1 contacting with a heat-conducting block 2. The loop 1 is formed with a guiding section 5 for guiding bubbles from liquid to flow away, and a bubble generator 40 for speeding the generation of bubbles. The expansion section 4 is at a predetermined space in the loop 1. Since liquid expands thermally and is vaporized, a proper expansion section is required for preventing that the loop 1 is broken. In the present invention, the guiding section 5 is installed in an unbalance way. That is, each turn forming the loop 1 is in a state that one side is hot, while the other side is cold. Namely, one side is near a heat source, while another side is far away the heat source. Then, the densities of the liquid at two sides of the loop are unequal so as to induce a temperature difference. Thus, liquid flows with a lower speed. That is, an asymmetric way is used to install the loop 1 on the heat-conducting block 2. An unbalance is employed to move the loop 1 in advance. By this nature force, a longitudinal temperature uniformity is formed. The bubble generator 40 is installed at the loop 1 having liquid therein. That is, the requirement for overheated temperature for generating boiling bubbles in the loop 1 is not too high so that the temperature for the boiling bubbles become low and therefore, more boiling bubbles are generated. As a result, the recycling in the loop 1 occurs more easily, and the recycling speed is increased. The temperature of the heat source can be further reduced.
In the so-called bubble generator [0046] 40, the inner wall of the loop 1 can be arranged with convex or concave structures with proper sizes, such as points, blocks, surfaces, grooves, thread spirals, or other geometrical structure. Therefore, the loop 2 can have the shape of single loop, double loops, multiple loops or web loops, or is a single layer loop, double layer loop, multiple layer loop, or porous loop, or the combinations thereof. Accordingly, many aspects can be used to embody the bubble generator 40. After bubbles are generated through a heat source 3, the fluid in the loop 1 may be cycled rapidly. A better guide means is required for guiding bubble out of the loop and driving the cycling operation.
The fluid in the [0047] loop 1 can be selected according to the requirement of operation and pressure. The loop 1 can be exhausted to vacuum or not be exhausted to vacuum, which is determined according to the kinds of the fluid or the operating temperature range. The loop has any desired shapes, outlooks, material and the combination thereof. The loop 1 can be rigid, flexible, or the combination thereof. The loops 1 can be connected in series or parallel, independently, multiple, or the combination of the aforesaid structures.
The radiator can be the loop itself, or be extended or prolonged to the place for heating exchanging. The radiator can be connected to the prior art radiating structures for heating exchanging. [0048]
The expanding [0049] section 4 in the loop can be an expanding vapor space or reduced vapor space, which can be placed in the inner space of a loop with a proper size, i.e. the area without filling liquid completely in loop, or the expanding area is attached to the loop. Of course, the expanding area does not be included. It is a device capable of deformation as a proper pressure is applied. Then, the liquid can be filled in the whole loop without including the expandable area. Therefore, a volume is provided for the vapor from heating the liquid within the loop in order to avoid the breakage of the loop.
In summary, in the present invention, continuous curved tubes can be used to adding above the prior art heat absorption block. Other than providing a security, and a transversal temperature uniformity is achieved. It can be presented through many structures which are arranged for achieving the desired requirement. Therefore, the present invention may provide a preferred application, and has a structure completely different from the prior art. [0050]
Although the present invention has been described with reference to the preferred embodiments, it will be understood that the invention is not limited to the details described thereof. Various substitutions and modifications have been suggested in the foregoing description, and others will occur to those of ordinary skill in the art. Therefore, all such substitutions and modifications are intended to be embraced within the scope of the invention as defined in the appended claims. [0051]

Claims

What is claimed is:

1. A bubble cycling heat exchanger system, comprising:

a heat-conducting block thermally coupled to a heat source; and

at least one closed fluid cycling loop containing a working fluid therein, and having a spiral tube defining a plurality of longitudinally arranged coils and a flow-returning tube with two opposing ends respectively connected to corresponding opposing ends of said spiral tube for generating a circulating flow, wherein said coils each have two side portions, one of the two side portions thereof in contact with the heat-conducting block.

2. The bubble cycling heat exchanger system as recited in claim 1, wherein the flow-returning tube is longitudinally disposed and contacted with an inner perimeter of each of said coils.

3. The bubble cycling heat exchanger system as recited in claim 1, further comprising a filling block is arranged on a connected portion between the spiral tube and the flow-returning tube.

4. The bubble cycling heat exchanger system as recited in claim 1, wherein the coils each are formed from a shape selected from the group consisting of a round shape, an ellipse shape a rectangle shape and a trapezoid shape in a cross-sectional contour.

5. The bubble cycling heat exchanger system as recited in claim 1, further comprising a fan installed with the closed fluid cycling loop.

6. A closed fluid cycling loop containing a working fluid therein for removing heat from a heat source thermally coupled to a longitudinally extended heat-conducting block, comprising:

a spiral tube defining a plurality of longitudinally arranged coils, each of said coils having a left-half portion and a right-half portion of an asymmetric cross-sectional contour thereof, the spiral tube being adapted for contact with said heat source at an arbitrary location; and

a flow-returning tube with two opposing ends respectively connected to corresponding opposing ends of said spiral tube for generating a circulating flow.

7. The closed fluid cycling loop as recited in claim 6, further comprising means for generating bubbles adjacent to the heat-conducting block.

8. The closed fluid cycling loop as recited in claim 6, further comprising means for providing an expansion space to inflating gas.

9. The closed fluid cycling loop as recited in claim 6, further comprising means for guiding fluid to flow in a unidirectional direction.

10. A closed fluid cycling loop containing a working fluid therein, comprising:

a plurality of spiral tubes being interlaced together in proximity one to another and each defining a plurality of longitudinally arranged coils; and

a plurality of flow-returning tubes each having two opposing ends respectively connected to corresponding opposing ends of each of said spiral tubes thereby to longitudinally pass through an inner perimeter of each of the coils each of said spiral tubes;

wherein said coils each have a left-half portion and a right-half portion of an asymmetric cross-sectional contour thereof with respect to a heat source thermally coupled to a heat-conducting block for establishing a temperature difference and a density difference of the working fluid to aid in achieving a unidirectional flow therein.

11. The closed fluid cycling loop as recited in claim 10, wherein a left spiral tube of the plurality of spiral tubes has a substantial trapezoid shape in a cross-sectional contour, wherein flow of the working fluid at one side of the loop will be suppressed and flow of the working fluid at an opposing side of the loop will be guided to flow, and thereby to transfer heat in a first predetermined direction.

12. The closed fluid cycling loop as recited in claim 11, wherein a right spiral tube of the plurality of spiral tubes has a substantial trapezoid shape in a cross-sectional contour, wherein flow of the working fluid at one side of the loop will be suppressed and flow of the working fluid at an opposing side of the loop will be guided to flow, and thereby to transfer heat in a second predetermined direction.

13. The closed fluid cycling loop as recited in claim 12, wherein the first predetermined direction is opposite to the second predetermined direction.

14. The closed fluid cycling loop as recited in claim 13, wherein a middle spiral tube of the plurality of spiral tubes has a first joint end and a second joint end connected to a first joint end of said right spiral tube, said right spiral tube has a second joint end connected to a first joint end of said left spiral tube, and said left spiral tube has a second joint end connected to said first joint end of said middle spiral tube for generating a circulating flow.