JPS60171389A - Heat transfer device - Google Patents

Abstract

PURPOSE:To prevent the pulsation of heat transportation by a method wherein the inflow operation of operating fluid into one accumulator and the recirculating operation of the same into a heat receiving unit are effected alternately while the same operations of the same into the other accumulator in reverse sequence are effected alternately. CONSTITUTION:Steam 6B, generated in the heat receiving unit 1, flows to a heat radiating unit 2 through a pipeline 11A, is cooled and condensed, then, the condensed liquid 6A flows into the accumulator 22 through the pipelines 11B, 23D and the opening and closing valve 27 thereof, whereby the heat, absorbed in the heat receiving unit 1, is transported to the heat radiating unit 2. Voltage is impressed on a thermoelectric element 30 so as to heat the accumulator 21 and cool the accumulator 22, and the internal pressure of the accumulator 21 becomes higher than the same of the accumulator 22, therefore, a driving force to flow the liquid into the direction from the accumulator 21 to the accumulator 22 is generated and the liquid in the accumulator 21 is recirculated to the heat receiving unit 1 through the pipeline 23A and the opening and closing valve 24. The operating fluid 6 may be recirculated to the heat receiving unit 1 continuously by switching the opening and closing valves 24-27 and the current of the thermoelectric element 30.

Description

DETAILED DESCRIPTION OF THE INVENTION [Technical Field of the Invention] The present invention relates to a heat transfer device used in an air conditioner or the like.

[Prior art]

Heat transfer devices generally enclose a heat transport medium in a pipe and utilize the phase change of this heat transport medium between liquid and steam.
The heat absorbed by the heat receiving part is transported to the heat radiating part and dissipated.

FIG. 1 shows a conventional heat transfer device shown in, for example, Japanese Utility Model Application Publication No. 57-66381, in which l indicates a heat receiving section disposed horizontally at the top, and 2 indicates a heat receiving section disposed vertically at the bottom. 3A and 3B are first and second check valves that allow flow in only one direction, and 4 is an accumulator. 5A is a pipe between the heat receiving part 1 and the heat radiating part 2, 5B is a pipe between the heat radiating part 2 and the first check valve 3A, and 5C is a pipe between the first check valve 3A and the second check valve 3A. The pipe line between stop valve 3B and 5D is the second
This is a pipe line between the check valve 3B and the heat receiving part 1. In this way, each pipe line forms a loop, a so-called closed pipe line, and an accumulator 4 is connected to the pipe line 5C. A suitable amount of fluid 6 is enclosed.

A chamber 7 is interposed in the middle of a conduit 5D connected from above the heat receiving part 1 on the accumulator 4 side. This chamber 7
As shown in FIG. 2, the inside of the container is pivotably supported around a fulcrum O so that it can freely swing and rotate, and when no liquid is stored inside, the center of gravity G1 is below the fulcrum 0. When the opening is at the top and a predetermined amount of liquid has been stored,
A liquid reservoir 8 whose center of gravity G2 moves and is automatically rotated is provided above the fulcrum 0. Here, liquid working fluid 6
Assuming that the liquid 6A is the liquid 6A and the gaseous working fluid 6 is the steam 6B, the pipe line is filled with the liquid 6A at startup.

Now, when heat is supplied to the heat receiving section 1, the liquid 6A in the heat receiving section 1 generates high pressure steam 6B corresponding to the given temperature, creating a pressure difference between the heat receiving section 1 and the accumulator 4. Since the pressure in the heat receiving part 1 is higher than that in the heat receiving part 1, the liquid 6A in the pipe 5A, the heat radiating part 2, and the pipe 5B flows into the accumulator 4, and the pressure in the accumulator 4 is gradually increased.

The steam 6B generated in the heat receiving part 1 passes through the pipe line 5A and reaches the heat radiating part 2, where it is cooled and liquefied by releasing the heat of condensation. As a result, the pressure of the steam 6B in the heat receiving part 1, the pipe line 5A, and the heat radiating part 2 becomes a saturated vapor pressure corresponding to a temperature approximately intermediate between the heat receiving part temperature and the heat radiating part temperature, Therefore, while the liquid 6A is being evaporated in the heat receiving section 1, the pressure in the accumulator 4 is also maintained at approximately this pressure.

In this state, the steam 6B generated in the heat receiving part 1 reaches the heat radiating part 2 and is liquefied again, so that the heat in the heat receiving part 1 is transferred to the heat radiating part 2. 1
This continues until liquid 6A runs out.

When all of the liquid 6A in the heat receiving part 1 evaporates, the pressure of the steam 6B in the heat receiving part 1, the pipe 5A, and the heat radiating part 2 is regulated only by the temperature of the heat radiating part 2, and becomes low. Since a pressure difference is generated between the heat receiving part 1 and the pressure in the accumulator 4 is high, the liquid 6A stored in the accumulator 4 flows back toward the heat receiving part 1 through the second check valve 3B. Become. At this time, the liquid 6A does not immediately reach the heat receiving part 1, but is temporarily stored in the liquid reservoir 8 of the chamber 7 interposed in the pipe line 5D. That is, the liquid reservoir 8 stores a predetermined amount of the liquid 6A therein, and when it moves to the center of gravity G2 above the fulcrum 0, it rotates and the liquid 6A is stored inside the liquid reservoir 8.
is discharged to the heat receiving section 1 at once. As a result, a large amount of liquid 6A can be supplied to the heat receiving section 1, and the entire heat receiving section 1 can be effectively operated.

By sequentially repeating the above operations, the heat from the upper heat receiving section 1 can be transported to the lower heat radiating section 2 without using any power.

However, in the conventional heat transfer device of this type, all of the liquid 6A in the heat receiving part 1 evaporates and the accumulator 4
When a pressure difference is generated between the heat receiving part 1 and the liquid 6A, the liquid 6A stored in the accumulator 4 is temporarily stored and then supplied to the heat receiving part 1. The flow will stop. As a result, the amount of heat transported from the heat receiving section 1 to the heat radiating section 2 decreases or stops, causing a problem that temporal pulsations occur in the heat transport.

[Summary of the invention]

The present invention was developed in view of the above circumstances, and includes a plurality of accumulators piped in parallel in a pipeline on the second-stream side of the heat-receiving section and downstream of the heat-radiating section, and a heating and cooling means for heating and cooling the accumulators. and causing at least one accumulator to alternately perform an operation of causing the working fluid to flow into the accumulator and an operation of causing the working fluid to flow back to the heat receiving section, and alternately perform the same operation in the reverse order of the aforementioned operation for the other accumulators. The present invention provides a heat transfer device that can prevent pulsation of heat transport with an extremely simple configuration that includes a control means for controlling the heat transfer. Hereinafter, its configuration and the like will be explained in detail with reference to embodiments shown in the drawings.

[Embodiments of the invention]

FIG. 3 is a system diagram showing a heat transfer device according to the present invention, in which 1 is a heat receiving section, 2 is a heat radiating section, and 6 is a condensable working fluid such as fluorocarbon or methyl alcohol as a heat transport medium. A suitable amount of the working fluid 6 is sealed in a loop-shaped pipe line 11 which has the heat receiving section 1 and the heat radiating section 2 interposed therebetween. 1
Reference numeral 2 denotes a blower fan provided in the heat radiating section 2 to effectively radiate heat.

Reference numerals 21 and 22 denote a plurality of accumulators interposed in the pipe line 11 connecting the upstream side of the heat receiving section 1 and the downstream side of the heat dissipating section 2; in this embodiment, the first and second accumulators 211i1;
This is an accumulator with 211M pipes connected in parallel.

That is, IIA is a pipe connecting the downstream side of the heat receiving part 1 and the upstream side of the heat radiating part 2, and 11B is a pipe connecting the upstream side of the heat receiving part 1 and the downstream side of the heat radiating part 2. The heat receiving part 1 side is branched into a pipe line 23A and a pipe line 23B which communicate and connect the first and second accumulators 21, 22 and the heat receiving part 1, and the heat dissipating part 2 side is branched into a pipe line 23A and a pipe line 23B which communicate and connect the first and second accumulators 21, 22 and the heat receiving part 1. .22 and the heat radiation part 2 are connected in series 1ffl.
C and a conduit 23D. Reference numerals 24 to 27 indicate on-off valves as opening/closing means for selectively opening and closing the respective branched pipe lines 23A to 23D;
3A and 23B are interposed in the first and second on-off valves as on-off means, and 26 and 27 are the third and fourth on-off valves as on-off means and on the pipe line 23C and the pipe line 23D. be.

These first to fourth on-off valves 24 to 27 constitute a control means for controlling the operation of the accumulators 21 and 22, so that their opening and closing operations are interlocked with each other as follows. That is, 1st. Both the fourth on-off valves 24.2j are open, and the second. A first state in which the third on-off valves 25 and 26 are both closed; Both the fourth on-off valves 24 and 27 are closed, and the second on-off valves 24 and 27 are both closed. The third on-off valves 25 and 26 are interlocked so that both open and open second states are alternately repeated at appropriate time intervals.

30 is the first and second accumulator 21.22
This thermoelectric element 30 is interposed between accumulators, and one surface 31 is connected to the first accumulator 2.
1 and the other surface 32 is in contact with the second accumulator 2
It is provided so as to be in contact with 2. This thermoelectric element 3
By switching between positive and negative currents, heat generation and heat absorption can be performed alternately on both surfaces 31 and 32. Here, the positive/negative switching is performed when the first to fourth on-off valves 24 to 27 are in the first state.
The surface 31 of the thermoelectric element 30 is in a heat-absorbing state, and the surface 32 is in a heat-absorbing state, and when in the second state, the surface 31 of the thermoelectric element 30 is in a heat-absorbing state, and the surface 32 is in a heat-generating state.

In the heat transfer device configured in this way, when the first state shown in FIG. ,
It cools and condenses. The condensed liquid 6A is passed through the pipe 11B,
The heat absorbed by the heat receiving part 1 is transported to the heat radiating part 2 by the action of passing through the fourth on-off valve 27 via the conduit 23D and flowing into the second accumulator 22. During this time, since the second on-off valve 25 is closed, steam does not directly flow from the heat receiving part 1 to the second accumulator 22 through the pipe line 23B. Further, the first on-off valve 24 is open, and the third on-off valve 26 is closed.

At this time, the thermoelectric element 30 includes the first accumulator 2.
A voltage is applied to heat the first accumulator 22 and cool the second accumulator 22, and the internal pressure of the first accumulator 21 becomes higher than the internal pressure of the second accumulator 22. A driving force is generated that causes the liquid to flow in the direction from the second accumulator 22 to the second accumulator 22 . As a result, the liquid in the first accumulator 21 flows back to the heat receiving section 1 through the pipe line 23A and the first on-off valve 24. In other words, the working fluid 6 is supplied to the heat receiving section 1.

On the other hand, after a certain period or the accumulator 21.2
The first to fourth on-off valves 24 are
27 and the thermoelectric element 30 is switched, the surface 31 of the heating element 30 becomes heat absorbing and the surface 32 becomes heat generating.

In addition, both the first and fourth on-off valves 24 and 27 are closed,
The second and third on-off valves 25 and 26 are both open.
The difference is that when switching to the state, the vapor 6B evaporated in the heat receiving section 1 is liquefied in the heat dissipating section 2 and then flows into the first accumulator 21, and the liquid flows back from the second accumulator 22 to the heat receiving section 1. Heat transport is carried out in exactly the same manner as in the first state.

In this way, by switching the opening and closing of the first to fourth on-off valves 24 to 27 and switching the current of the thermoelectric element 30, the accumulators 21 and 22 are switched at the time when the working fluid 6 is flowing back into the heat receiving part 1, The working fluid 6 can be returned to the heat receiving section 1 substantially continuously.

Therefore, the working fluid 6 is not completely evaporated in the heat receiving part 1, and the steam 6B in the heat receiving part 1 is transferred to the heat radiating part.
Since the heat can be continuously circulated through the heat transport, the pulsation of heat transport can be reduced, the change in the amount of heat transport can be reduced, and the heat transport efficiency can be increased. Moreover, since gravity is not used for liquid reflux, the accumulator 21. ．． 22 is located below the heat receiving part 1, heat can of course be transported regardless of the installation position, but also in cases where the pressure loss in the heat receiving part 1 and the heat dissipating part 2 is large, or even in zero gravity such as in space. Heat can be transported even at the bottom.

That is, the first to fourth on-off valves 24 to 27 cause the working fluid 6 condensed in the heat radiating section 2 to flow into the accumulator, and the working fluid 6 in the accumulator is transferred to the heat receiving section. Control means is configured to alternately perform the operation of recirculating the water to the accumulator 1, and to alternately cause the other accumulators to perform the same operation in the reverse order of the aforementioned operation. Further this means.

The return of the working fluid 6 to the heat receiving section 1 and the inflow into the accumulator are performed more effectively by heating and cooling the accumulator with the thermoelectric element 30.

FIG. 4 is a system diagram showing another embodiment according to the present invention, in which the operation of causing the working fluid 6 condensed in the heat radiation section 2 to flow into the accumulator and the operation within the accumulator are performed for at least one accumulator. The fluid 6 is transferred to the heat receiving section 1
1. shown in FIG. Instead of the second on-off valve 24.25, the first on-off valve 24.25. The first and second check valves 51,52 are installed in the conduit 2 so that the liquid flows only from the second accumulator 21,22 toward the heat receiving part 1.
3A and 23B, and third and fourth on-off valves 26.
27 instead of the first. Third and fourth check valves 61, 62 are interposed such that liquid only flows once into the second accumulator 21, 22. In this embodiment, by switching the heating and cooling by the thermoelectric element 30, the first. Second accumulator 2
1.2 A pressure difference occurs between the first state and the second state.
Switching between the state and the state is performed.

In this switching, if it is required to smoothly reverse the height difference between the pressure in the first accumulator 21 and the pressure in the second accumulator 22, as shown in FIG. and the second accumulator 22 to make the internal pressure uniform.
1, the process can be carried out even more smoothly.

That is, 72 is a fifth on-off valve as an on-off means interposed in the middle of the uniform pipe 71, and this fifth on-off valve 72
The operation of the first to fourth on-off valves 24 to 27 is set so that the first to fourth on-off valves 24 to 27 are synchronously opened and opened at the same time as switching between the first state and the second state, and then closed again after a predetermined period of time has elapsed. ing. To explain this operation, for example, the first to fourth
When the on-off valves 24 to 27 are switched, the on-off valve 72 is controlled to be open, so that the first accumulator 2
1 and the pressure in the second accumulator 22 are:
They become equal instantaneously, and then the on-off valve 72 is closed, so that the heating and cooling action of the thermoelectric element 30 causes the pressure difference within the accumulator 2L22 to increase in the opposite direction. As a result, when the first to fourth on-off valves 24 to 27 are switched, the first to fourth on-off valves 24 to 27 are switched. Second accumulator 21.22
The reversal of the pressure difference within will take place in a short period of time.

6 and 7 are system diagrams showing other embodiments, respectively. In the examples shown in these figures, the first and second accumulators 21 and 22 are filled with a non-condensable gas such as nitrogen or helium. gas reservoir is connected. 6th
In the example shown in the figure, the first. Second gas reservoir 81
．． 82 is connected to the first and second accumulators 21,22. For this reason, 1. Second accumulator 2
The pressure within 1°22 is set to 1. It can be regulated by the pressure of the first and second gas reservoirs 81 and 82, and the range of pressure change can be made small. As a result, the pressure inside the heat receiving part 1 becomes less susceptible to changes due to heat input in the heat receiving part l,
A temperature control effect can be obtained in which the temperature of the heat receiving section 1 does not change much due to changes in heat input.

In the example shown in FIG. 7, one gas reservoir 91 is located at the first. The second accumulator 21.22 is used in common with the gas reservoir 91 and the first. In the middle of each of the pipes connecting the second accumulators 21 and 22, there is a sixth pipe serving as an opening/closing means. A seventh on-off valve 92,93 is interposed. These 6th. Seventh on-off valve 92.93
The operation is the same as the third one above. The opening and closing of the fourth on-off valves 26 and 27 are interlocked. That is, in the first state, the surface 31 of the thermoelectric element 30 generates heat and the surface 32 generates heat.
are controlled so that the 1st and 4th absorb heat. The seventh on-off valves 24, 27.93 are all open, and the second... Third.
The sixth on-off valve 25.26.92 is in the closed state. At this time, the pressure inside the first accumulator 21 is not regulated by the gas reservoir 91 because the sixth on-off valve 92 is closed, and the pressure inside the second accumulator 22 is not regulated by the gas reservoir 91 because the sixth on-off valve 92 is closed. Therefore, it is regulated by the gas reservoir 91. Therefore, the thermoelectric element 30
The pressure in the second accumulator 21 can rise smoothly, and at the same time, the change in the pressure in the second accumulator 22 can be reduced.

As a result, similar to the embodiment shown in FIG. 6, a temperature control effect can be obtained in which the temperature of the heat receiving portion l does not change much due to changes in heat input. In this embodiment, in addition to the advantage that only one gas reservoir is required,
Since regulation by non-condensable gas can be switched, the switching operation can be performed more smoothly. Here, the 6th and 7th on-off valves 92 and 93 are connected to the first valve shown in FIG.
．． The second accumulator 21.22 and the first. Of course, the same effect can be obtained by interposing it between the second gas reservoir 81 and 82.

In addition, in the above embodiment, the first to fourth on-off valves 24 to
The opening/closing control of the heat receiving section 1 or the first . This can be done by detecting a change in the liquid level in the second accumulator 21,22. Among these, the one that detects the liquid level in the heat receiving part 1 and switches the on-off valve can prevent the liquid from running out from the heat receiving part 1, thereby preventing the heat receiving part 1 from overheating and improving the reliability of the device. can be improved and heat transport efficiency can be increased. Further, although an example in which two accumulators are used is described, the present invention is not limited to this (although it is of course possible to use a plurality of accumulators).

〔Effect of the invention〕

As explained above, according to the present invention, a plurality of accumulators are interposed in the conduit connecting the heat receiving section and the heat dissipating section, and a heating and cooling means for heating and cooling these accumulators is provided. A pressure difference is generated between the accumulator and the cooled accumulator, and this pressure difference can be used to return the working fluid to the heat receiving part,
Since the control means for controlling the accumulator for the operation of the working fluid flowing into the accumulator and the operation of the working fluid returning to the heat receiving section is provided, the accumulator that causes the working fluid to return to the heat receiving section and the accumulator that causes the working fluid to flow from the heat radiating section are switched, The working fluid can be continuously returned to the heat receiving section.

Therefore, unlike in the past, the working fluid in the heat receiving section does not completely evaporate, and the steam in the heat receiving section can be continuously circulated to the heat radiating section, reducing changes in the amount of heat transport. It has the effect of preventing heartburn.

[Brief Description of the Drawings] Figs. 1 and 2 are a system diagram and an enlarged view of the main parts of a conventional heat transfer device, Fig. 3 is a system diagram showing a heat transfer device according to the present invention, and Fig. 4 7 is a system diagram showing another embodiment. ■-- Heat receiving section, 2... Heat dissipating section, 11A. 11B...Pipe line, 21.22...First degree second accumulator, 23A-23D...Pipe line, 24-
27... First to fourth on-off valves, 30... Thermoelectric element, 51. , 52...first degree second check valve, 61.
62...3rd. Fourth check valve, 81.8'2...
・First. Second gas reservoir, 91...Gas reservoir, 92.93...6th. Seventh on-off valve. Agent Masuo Oiwa 2! :￥1Illustration3IllustrationPig5Illustration6IllustrationTsuru7Illustration1

Claims (1)

[Scope of Claims] (11) A heat transfer device comprising a loop-shaped pipe line with a heat receiving part and a heat radiating part interposed therebetween, and a condensable working fluid as a heat transport medium is sealed in the pipe line, A plurality of accumulators piped in parallel are interposed in a pipe line upstream of the heat receiving section and downstream of the heat radiating section, and a heating and cooling means for heating and cooling the accumulators is provided, and at least one accumulator is operated to condense in the heat radiating section. The operation of causing fluid to flow into the accumulator and the operation of causing the fluid in the accumulator to flow back to the heat receiving section are performed alternately, and the same operation is alternately performed on other accumulators in the reverse order of the above operations. (2) The control means includes opening/closing means for selectively opening and closing pipes that communicate the accumulator and the heat receiving section, and the accumulator and the heat radiating section, respectively. The heat transfer device according to claim 1, characterized in that: (3) the opening/closing means is constituted by an opening/closing valve interposed in each pipe, and two valves on the same accumulator side Claims characterized in that the opening and closing of the two on-off valves are set to be alternately performed and to be in an open/close state opposite to the open/close state of the two on-off valves on the side of at least one other accumulator. The heat transfer device according to item 2. (4) The opening/closing means is comprised of a check valve through which fluid flows only from the accumulator interposed in each pipe line to the heat receiving section and the heat dissipating section toward the accumulator. The heat transfer device according to claim 2. (5) The heat transfer device according to claim 1, characterized in that the heating and cooling means is constituted by a thermoelectric element that utilizes the Peltier effect. Transmission device. (6) Any one of claims 1 to 5, characterized in that at least two accumulators are connected via a pressure equalizing pipe that is opened and closed by an opening and closing means. (7) The heat transfer device according to any one of claims 1 to 6, wherein a gas reservoir filled with a non-condensable gas is connected to the accumulator. (8) The heat transfer device according to claim 7, characterized in that an on-off valve serving as an on-off means is provided in the pipeline connecting the accumulator and the gas reservoir.