JP7486128B2 - Heat removal device, heat removal method, power generation device, and power generation method - Google Patents

Description

The present invention relates to a heat removal device, a heat removal method, a power generation device, and a power generation method.

Condensing units have been used as a means of heat exchange with a heat exchange target such as a liquid or gas. As described in Patent Document 1, for example, a condensing unit has a compressor that compresses a refrigerant to produce a high-temperature, high-pressure gas refrigerant, a condenser that condenses the high-temperature, high-pressure gas refrigerant from the compressor to produce a high-pressure liquefied refrigerant, an expansion valve that reduces the pressure of the high-pressure liquefied refrigerant from the condenser to produce a low-temperature, low-pressure humid gas refrigerant, and an evaporator that evaporates the low-temperature, low-pressure humid gas refrigerant from the expansion valve to produce a low-pressure gas refrigerant, and exchanges heat between the refrigerant and the heat exchange target in the evaporator to cool the heat exchange target.

JP 2017-053570 A

However, such condensing units do not provide high heat exchange efficiency, and it is difficult to instantly (rapidly) cool the heat exchange target.

The present invention aims to provide a heat removal device and a heat removal method that can achieve high heat removal efficiency (heat exchange efficiency) and instantly remove heat from the object to be removed, and also to provide a power generation device and a power generation method that use this heat removal device and heat removal method and have excellent power generation efficiency.

The above objectives are achieved by the present invention as described below in (1) to (10).

(1) A spiral tube formed by spirally winding a tube having a groove extending in a circumferential direction on an outer periphery thereof;
an inner tube disposed inside the spiral tube;
an outer tube disposed outside the spiral tube and disposed so as to accommodate the spiral tube between the outer tube and the inner tube;
A heat removal device characterized by flowing a refrigerant through the spiral tube and flowing an object to be removed between the inner tube and the outer tube, thereby performing heat exchange between the refrigerant and the object to be removed, and removing heat from the object to be removed.

(2) A heat removal device as described in (1) above, in which adjacent spiral tubes are in contact with each other.

(3) A heat dissipation device as described in (1) or (2) above, in which the groove is formed in a spiral shape.

(4) The inner tube is in contact with the inner circumference of the spiral tube,
The heat removal device according to any one of the above (1) to (3), wherein the outer tube is in contact with an outer periphery of the spiral tube.

(5) a compressor that compresses the refrigerant to produce a high-temperature, high-pressure gas refrigerant;
a condenser for condensing the gas refrigerant into a wet gas refrigerant;
A first spiral tube that reduces pressure and liquefies the wet gas refrigerant to form a liquid refrigerant;
and a second spiral tube for decompressing and expanding the liquid refrigerant to produce a low-temperature, low-pressure liquid refrigerant.
The heat removal device according to any one of (1) to (4) above, wherein the liquid refrigerant having a low temperature and a low pressure from the second spiral tube is introduced into the spiral tube.

(6) A spiral tube formed by spirally winding a tube having a groove extending in a circumferential direction on an outer periphery thereof;
an inner tube disposed inside the spiral tube;
An evaporator having an outer tube disposed outside the spiral tube and disposed so as to accommodate the spiral tube between the outer tube and the inner tube,
A heat removal method comprising the steps of: flowing a refrigerant through the spiral tube; and flowing an object to be removed from the heat removal between the inner tube and the outer tube, thereby carrying out heat exchange between the refrigerant and the object to be removed from the heat removal, thereby removing heat from the object to be removed from the heat removal.

(7) a pressure pump that pressurizes and delivers the liquid;
A heat removal device according to any one of (1) to (5) above, which removes heat from the liquid pumped out from the pressure pump;
a storage tank that stores the liquid whose heat has been removed by the heat removal device;
a pressurizing unit that introduces a gas into the storage tank and pressurizes the liquid in the storage tank;
a power generation unit that is driven by collision with the liquid discharged from the storage tank.

(8) The power generation device according to (7) above, in which the power generation unit has a rotating body that rotates due to collision with the liquid.

(9) A power generating device as described in (7) or (8) above, in which the liquid that collides with the rotating body is introduced into the pressure pump.

(10) Pressurize the liquid with a pressure pump and send it out.
The liquid pumped out from the pressure pump is deheated by the heat removal method described in (6) above;
storing the liquid whose heat has been removed in a storage tank;
introducing a gas into the storage tank to pressurize the liquid in the storage tank;
A power generation method comprising driving a power generation unit by collision with the liquid discharged from the storage tank.

The heat removal device and method of the present invention can efficiently release the energy in the heat removal target in the evaporator. This allows high heat removal efficiency and instantaneous heat removal from the heat removal target. In addition, the power generation device and power generation method of the present invention use the heat removal device and heat removal method described above, so the liquid can be kept at a low temperature and its evaporation and vaporization can be suppressed, resulting in excellent power generation efficiency.

FIG. 1 is an overall view showing a heat removal device according to a first embodiment. FIG. 2 is a diagram showing a helical tube of the heat removal device of FIG. FIG. 3 shows a tube that is spirally wound to form the helical tube of FIG. FIG. 4 shows a helical groove formed in the tube of FIG. FIG. 5 is a cross-sectional view of an evaporator included in the heat removal device of FIG. FIG. 6 is a vertical cross-sectional view of an evaporator included in the heat removal device of FIG. FIG. 7 is a diagram showing the flow of water in the evaporator. FIG. 8 is a diagram showing grooves formed in a spiral tube according to the second embodiment. FIG. 9 is an overall view showing a power generating device according to the third embodiment.

First Embodiment
First, a heat removal device 100 according to a first embodiment of the present invention will be described.

The heat removal device 100 shown in Fig. 1 is a device that can instantly remove heat, i.e., cool water W (H ₂ O) as a heat removal target. Such a heat removal device 100 includes a compressor 110 that compresses a refrigerant Q (heat medium) to obtain a high-temperature, high-pressure gas refrigerant Q1, a condenser 120 that condenses the high-temperature, high-pressure gas refrigerant Q1 from the compressor 110 to obtain a high-pressure liquefied gas refrigerant Q2, a first spiral tube 130 (thick spiral tube) that reduces pressure and liquefies the high-pressure liquefied gas refrigerant Q2 from the condenser 120 to obtain a liquid refrigerant Q3, a second spiral tube 140 (thin spiral tube) that reduces pressure and expands the liquid refrigerant Q3 from the first spiral tube 130 to obtain a low-temperature, low-pressure liquid refrigerant Q4, an evaporator 150 that evaporates the liquid refrigerant Q4 from the second spiral tube 140 to obtain a low-pressure gas refrigerant Q5, and a pipe 160 that connects these. In the heat removal device 100, heat is exchanged between the refrigerant Q and the water W in the evaporator 150, and the heat is instantly removed from the water W. Note that the object of heat removal is not limited to the water W, and may be any liquid or gas.

The refrigerant Q used in the heat removal device 100 is not particularly limited, and may be, for example, various fluorocarbon refrigerants such as HFC-134a and R-1234yf, or various natural refrigerants such as ammonia (NH ₃ ) or carbon dioxide (CO _{2 )} . Among these, it is preferable to use an environmentally friendly refrigerant having a low ozone depletion potential and global warming potential.

[Compressor 110]
The compressor 110 compresses the gas refrigerant Q5 from the evaporator 150 to produce high-temperature, high-pressure gas refrigerant Q1.

[Condenser 120]
The condenser 120 is disposed downstream of the compressor 110, and receives the gas refrigerant Q1 from the compressor 110. The condenser 120 uses a fan 121 to blow air into the piping, and dissipates heat from the gas refrigerant Q1 flowing through the piping. As a result, part of the gas refrigerant Q1 is liquefied, and becomes a high-pressure liquefied gas refrigerant Q2 (wet gaseous refrigerant). The amount of liquefaction is not particularly limited, but it is sufficient that about 70% to 80% of the entire gas refrigerant Q1 be liquefied. This configuration allows the condenser 120 to be made smaller.

[First spiral tube 130]
The first spiral tube 130 is disposed downstream of the condenser 120, and the liquefied gas refrigerant Q2 from the condenser 120 is introduced into the first spiral tube 130. Two first spiral tubes 130 are disposed in parallel, and a collector pipe 131 that joins the two first spiral tubes 130 is connected to the upstream ends of the two first spiral tubes 130, and a collector pipe 132 that joins the two first spiral tubes 130 is also connected to the downstream ends. The collector pipe 131 functions as a buffer for smoothly introducing the liquefied gas refrigerant Q2 into the first spiral tube 130.

When the liquefied gas refrigerant Q2 from the condenser 120 is introduced into the first spiral tube 130, the molecules of the refrigerant Q (hereinafter also referred to as "refrigerant molecules") vibrate and rotate within the first spiral tube 130, radiating energy. The energy radiation caused by the vibration and rotation of the refrigerant molecules reduces the pressure of the liquefied gas refrigerant Q2 and liquefies it, resulting in a refrigerant Q that is even more moist than the liquefied gas refrigerant Q2. In particular, in this embodiment, almost 100% of the refrigerant Q is liquefied to become liquid refrigerant Q3 (liquid refrigerant).

Here, we will briefly explain the aforementioned phenomenon of energy radiation, with some speculation. When refrigerant Q is introduced into the first spiral tube 130, friction occurs between the molecules of refrigerant Q, and the refrigerant molecules repeatedly collide and separate, causing the refrigerant molecules to vibrate and rotate (this is called "vibration rotation"). Furthermore, centrifugal force is applied to the refrigerant molecules due to the vibration rotation, and when this centrifugal force reaches a certain level or greater, energy is radiated from the refrigerant molecules. This energy radiation reduces the pressure and liquefies the liquefied gas refrigerant Q2, turning it into liquid refrigerant Q3.

The inner diameter of the first spiral tube 130 is larger than the inner diameter of the second spiral tube 140. The inner diameter of the first spiral tube 130 is not particularly limited, but can be, for example, about 2 mm to 10 mm. The spiral diameter of the first spiral tube 130 is larger than the spiral diameter of the second spiral tube 140. The spiral diameter of the first spiral tube 130 is not particularly limited, but can be, for example, about 30 mm to 50 mm. The first spiral tube 130 is longer than the second spiral tube 140. The length (total length) of the first spiral tube 130 is not particularly limited, but can be, for example, about 1500 mm to 2000 mm. Each dimension of the first spiral tube 130 can be set appropriately, for example, depending on the refrigerant capacity, etc.

The above describes the first spiral tube 130, but the configuration is not particularly limited. For example, the number of first spiral tubes 130 can be set appropriately according to the refrigerant capacity, and may be one, or three or more may be provided in parallel. In addition, two or more first spiral tubes 130 may be connected in series. In addition, there is no particular limit to the size relationship of each dimension with the second spiral tube 140.

[Second spiral tube 140]
The second spiral tube 140 is disposed downstream of the first spiral tube 130, and the liquid refrigerant Q3 is introduced into the second spiral tube 140 from the first spiral tube 130. Similar to the above-described first spiral tube 130, two second spiral tubes 140 are disposed in parallel, and a collecting pipe 141 that joins the two second spiral tubes 140 is connected to the upstream ends of the two second spiral tubes 140, and a collecting pipe 142 that joins the two second spiral tubes 140 is also connected to the downstream ends. The collecting pipe 141 functions as a buffer for smoothly introducing the liquid refrigerant Q3 into the second spiral tube 140.

When liquid refrigerant Q3 from the first spiral tube 130 is introduced into the second spiral tube 140, the liquid refrigerant Q3 is pulled by the second spiral tube 140, increasing its speed, and the molecules of the refrigerant Q vibrate and rotate within the second spiral tube 140, radiating energy. This increase in speed and the radiation of energy due to the vibration and rotation of the refrigerant molecules reduce the pressure of the liquid refrigerant Q3, causing it to expand and become low-temperature, low-pressure liquid refrigerant Q4. Note that the energy radiation in the second spiral tube 140 follows the same principle as the first spiral tube 130, so a description of this will be omitted.

As mentioned above, in this embodiment, almost 100% of the refrigerant Q is liquefied in the first spiral tube 130, but if this is not the case, i.e., if gas components remain, the remaining gas components are liquefied by the second spiral tube 140, resulting in almost 100% liquid refrigerant.

The inner diameter of the second spiral tube 140 is smaller than the inner diameter of the first spiral tube 130. The inner diameter of the second spiral tube 140 is not particularly limited, but can be, for example, about 1 mm to 5 mm. The spiral diameter of the second spiral tube 140 is smaller than the spiral diameter of the first spiral tube 130. The spiral diameter of the second spiral tube 140 is not particularly limited, but can be, for example, about 10 mm to 30 mm. The second spiral tube 140 is shorter than the first spiral tube 130. The length (total length) of the second spiral tube 140 is not particularly limited, but can be, for example, about 500 mm to 1000 mm. Each dimension of the second spiral tube 140 can be set appropriately, for example, depending on the refrigerant capacity, etc.

The second spiral tube 140 has been described above, but its configuration is not particularly limited. For example, the number of second spiral tubes 140 can be set appropriately according to the refrigerant capacity, and may be one, or three or more may be provided in parallel. In addition, two or more second spiral tubes 140 may be connected in series. Furthermore, there is no particular limitation on the size relationship of each dimension with the first spiral tube 130.

The first helical tube 130 and the second helical tube 140 as described above are formed, for example, by the following method. First, a copper tube is prepared, a piano wire is inserted into this copper tube, and the copper tube is narrowed to the outer diameter (thickness) of the piano wire to form a straight tube. The straight tube is then wound helically to form a helical tube, thereby forming the first helical tube 130 and the second helical tube 140.

By twisting the copper tube, a helical groove (hereinafter also referred to as "helical groove") is formed on the inner wall of the first helical tube 130 and the second helical tube 140. Furthermore, by helically winding a straight tube with a helical groove formed thereon, the outside of the helix is pulled in the length direction as a whole, and the pitch of the helical groove becomes wider than in the straight tube state, while the inside of the helix is compressed in the length direction as a whole, and the pitch of the helical groove becomes narrower than in the straight tube state. In addition, by twisting the copper tube in the axial direction during the process of helically winding the straight tube, a "neck" is formed. The feed angle and pitch of the helical groove, and the position and number of the neck are appropriately set for each of the first helical tube 130 and the second helical tube 140.

In this way, the pitch of the spiral groove is different between the outer periphery and the inner periphery of the first and second spiral tubes 130, 140, and further, the constrictions are formed, so that the refrigerant molecules vibrate and rotate in the first and second spiral tubes 130, 140, which has a particularly favorable effect on the heat conversion in the first and second spiral tubes 130, 140. In other words, the feed angle and pitch of the spiral groove, the formation position and number of constrictions, etc. are set in the first and second spiral tubes 130, 140 so that the refrigerant molecules vibrate and rotate inside. However, this is only one example, and the configuration and formation method of the first and second spiral tubes 130, 140 are not particularly limited as long as they can perform the above-mentioned functions. In addition, instead of the first and second spiral tubes 130, 140, for example, an expansion valve or the like that performs the same function may be used.

[Evaporator 150]
The evaporator 150 is disposed downstream of the second spiral tube 140, and liquid refrigerant Q4 is introduced from the second spiral tube 140. The temperature of the liquid refrigerant Q4 introduced into the evaporator 150 is not particularly limited, but is preferably equal to or lower than 0°, which is the freezing temperature of water W, and is, for example, about −30° to −10°.

As shown in FIG. 2, the evaporator 150 has a spiral tube 151. The spiral tube 151 is formed by spirally winding a long, straight tube 152 (circular tube) having a circular cross section, more specifically, a circular inner and outer circumference, as shown in FIG. 3. In addition, in the spiral tube 151, adjacent tubes 152 are in contact with each other. In other words, the tubes 152 are spirally wound without any gaps. However, this is not limited to the above, and for example, a gap may be formed between adjacent tubes 152.

The dimensions of such a tube 152 are not particularly limited, and can be, for example, about 6 to 10 turns, an inner diameter of about 10 mm to 30 mm, a spiral diameter of about 100 mm to 200 mm, and a total length of about 5 m to 10 m. In addition, the cross-sectional shape of the tube 152 is not limited to a circle, and can be, for example, an ellipse, an oval, a polygon, etc.

A groove 153 is formed on the outer periphery of the tube 152, extending in the circumferential direction of the tube 152. The groove 153 is inclined with respect to the axis of the tube 152, and forms a spiral shape that extends in the axial direction while rotating in the circumferential direction. The dimensions of the groove 153 are not particularly limited, and for example, as shown in FIG. 4, the depth D can be about 0.1 mm to 3 mm, the pitch P can be about 0.1 mm to 3 mm, and the feed angle θ of the tube 152 can be about 5° to 20°.

As shown in FIG. 5, the evaporator 150 has a double tube 154 with a spiral tube 151 disposed inside. The double tube 154 is configured with a cylindrical inner tube 155 and an outer tube 156 disposed concentrically, and the space S between the inner tube 155 and the outer tube 156 is a flow path through which the water W to be removed heat flows. The spiral tube 151 disposed concentrically with the double tube 154 is provided in the space S, and the smooth flow of the water W is hindered by the spiral tube 151. In other words, the evaporator 150 has a configuration including the spiral tube 151, the inner tube 155 disposed inside the spiral tube 151, and the outer tube 156 disposed outside the spiral tube 151 and disposed to accommodate the spiral tube 151 between the inner tube 155 and the outer tube 156.

The outer diameter of the inner tube 155 and the inner diameter of the helical tube 151 are approximately equal, and the outer peripheral surface of the inner tube 155 is in contact with the inner circumference of the helical tube 151. Similarly, the inner diameter of the outer tube 156 and the outer diameter of the helical tube 151 are approximately equal, and the inner peripheral surface of the outer tube 156 is in contact with the outer circumference of the helical tube 151. Therefore, the helical tube 151 is sandwiched between the inner tube 155 located on the inside and the outer tube 156 located on the outside.

As shown in FIG. 6, a funnel-shaped guide section 157 is provided upstream of the double pipe 154 to guide the water W into the double pipe 154, and a funnel-shaped recovery section 158 is provided downstream to recover the water W that has passed through the double pipe 154. This allows the water W to be introduced into the double pipe 154 and recovered from the double pipe 154 smoothly and without stagnation.

In the evaporator 150 configured as described above, when water W is introduced into the space S, as shown in FIG. 7, the water W flows downstream in the space S by repeatedly moving to the downstream tube 152 while rotating around the tube 152 several times along the spiral groove 153 formed on the outer periphery of the spiral tube 151. FIG. 7 illustrates how the water W rotates around the groove 153 around the tube 152(n) located nth from the upstream side, moves to the adjacent tube 152(n+1) on the downstream side (n+1th from the upstream side), and then rotates around the groove 153 around the tube 152(n+1) to the adjacent tube 152(n+2) on the downstream side (n+2th from the upstream side).

In this way, by rotating the water W around the tube 152 along the groove 153 and moving it sequentially to the downstream tube 152, efficient heat exchange occurs between the water W passing through the space S and the liquid refrigerant Q4 passing through the spiral tube 151, and the heat and other energy (hereinafter also referred to as "internal energy") latent inside the water W is released all at once, thereby instantly deheating (cooling) the water W. To briefly explain this with some speculation, since the refrigerant Q flows at about -30° to -10° inside the spiral tube 151, the water W flows as described above, causing the water molecules to vibrate and rotate, and a speed difference occurs between the top and bottom of the water molecules (the refrigerant tube 151 side and the opposite side), and the water molecules are deformed (ideally cracked) due to this speed difference, and the internal energy of the water molecules is released all at once. Then, the water W is instantly deheated by the release of this internal energy and the heat exchange with the liquid refrigerant Q4.

The water W passes through the space S in about 1/100th of a second, during which time heat is instantly removed and the temperature drops to about room temperature.

In particular, in this embodiment, as described above, adjacent tubes 152 of the spiral tube 151 are in contact with each other, so that the water W can be prevented from stagnating between adjacent tubes 152, and the above-mentioned flow of water W can be more reliably generated. Also, as described above, the inner tube 155 is in contact with the inner circumference of the spiral tube 151, and the outer tube 156 is in contact with the outer circumference of the spiral tube 151, so that the water W can be easily rotated along the groove 153, and the above-mentioned flow of water W can be more reliably generated. Also, as described above, by making the groove 153 spiral, the water W can be easily rotated along the groove 153, and the above-mentioned flow of water W can be more reliably generated. Note that making the groove 153 spiral has the advantage that the groove 153 can be easily formed by cutting.

The liquid refrigerant Q4 passing through the spiral tube 151 becomes a low-pressure gas refrigerant Q5 through heat exchange with the water W. The gas refrigerant Q5 is then introduced into the compressor 110 and discharged again as high-temperature, high-pressure gas refrigerant Q1. In the heat removal device 100, the water W can be continuously deheated (cooled) by repeating this cycle of refrigerant Q.

Second Embodiment
Next, a heat removal device 100 according to a second embodiment of the present invention will be described. The heat removal device 100 of this embodiment is similar to the heat removal device 100 of the first embodiment described above, except that the configuration of the spiral tube 151 is different. Therefore, in the following description, the differences between this embodiment and the first embodiment will be mainly described, and the description of the similarities will be omitted. In addition, in each drawing of this embodiment, the same reference numerals are used for the same configurations as those of the above-mentioned embodiment.

As shown in FIG. 8, in this embodiment, an annular (ring-shaped) groove 153 is formed on the outer periphery of the tube 152. The annular grooves 153 are formed in a plurality of rows at equal intervals along the axial direction of the tube 152. The spiral tube 151 formed by spirally winding the tube 152 having such a configuration can also achieve the same effect as the first embodiment described above.

In this embodiment, the plane F including the annular groove 153 is perpendicular to the axis of the tube 152, but this is not limited thereto, and the plane F may be inclined with respect to the axis of the tube 152.

This second embodiment can achieve the same effects as the first embodiment described above.

Third Embodiment
Next, a power generating device 200 according to a third embodiment of the present invention will be described.

The power generation device 200 shown in Fig. 9 has a pump unit 210 that pressurizes and sends out water W, a heat removal unit 220 that removes heat from the water W sent out from the pump unit 210, a storage tank 230 that stores the water W that has passed through the heat removal unit 220, a pressurization unit 240 that fills the storage tank 230 with nitrogen _N2 to pressurize the water W in the storage tank 230, a power generation unit 250 that is driven by collision with the water W discharged from the storage tank 230, a pipe 260 that connects these parts and through which the water W circulates, and a check valve 270 installed at several points along the pipe 260. In such a power generation device 200, by driving the pump unit 210, the water W circulates in the pipe 260 in the direction of the arrow A, and thereby power generation is performed by the power generation unit 250.

The liquid (subject to heat removal) circulated through the pipe 260 is not limited to water W. However, by using water W, it is possible to reduce power generation costs.

The pump unit 210 has two pressure pumps 211, 212 arranged in parallel. In this way, by connecting the two pressure pumps 211, 212 in parallel, maintenance of the pump unit 210 is made easier. For example, during normal times, the pressure pumps 211, 212 are each driven at about 50% output, and during maintenance or replacement of the pressure pump 211, the pressure pump 212 is driven at 100%, allowing operation during maintenance to be the same as during normal times. For this reason, it is preferable to use pressure pumps 211, 212 that have the capacity to pressurize the water W to the required pressure at about 50% output.

Each of these pressure pumps 211, 212 is a multi-stage volute pump that pressurizes the water W using centrifugal force caused by the rotation of a bladed wheel called an impeller. A multi-stage volute pump can impart a spiral rotation (centrifugal force) to the molecules of the water W, making it well suited to this system. However, there are no particular limitations on the pressure pumps 211, 212. In addition, the number of pressure pumps included in the pump unit 210 is not limited to two, and may be one, or three or more.

The water W pumped out from the pump unit 210 is introduced into the heat removal unit 220 and heat is removed. By removing heat from the water W, which has been heated by pressurization using the pump unit 210, using the heat removal unit 220, evaporation of the water W can be prevented, and a decrease in the power generation capacity of the power generation device 200 can be prevented.

The heat removal unit 220 has two heat removal devices 221, 222 arranged in parallel. The heat removal device 221 is connected to the pressure pump 211, and the high-pressure water W discharged from the pressure pump 211 is introduced into the heat removal device 221, which removes heat from the water W. Similarly, the heat removal device 222 is connected to the pressure pump 212, and the high-pressure water W discharged from the pressure pump 212 is introduced into the heat removal device 222, which removes heat from the water W. In this embodiment, the heat removal device 100 of the first embodiment described above is used as the heat removal devices 221, 222, and the water from the pressure pumps 211, 212 is introduced into the space S. The water W is then removed heat by flowing through the space S. This allows the water W to be instantly removed heat, and the evaporation of the water W due to the rise in temperature can be more reliably prevented.

The storage tank 230 stores the water W that has been deheated by the heat removal unit 220. The storage tank 230 has a tank body 231 and a floating lid 232 that is arranged inside the tank body 231 and can be raised and lowered freely. Therefore, the inside of the storage tank 230 is divided into a lower space S1 located below the floating lid 232 and an upper space S2 located above the floating lid 232. Water W is introduced and stored in the lower space S1, and gas is introduced from the pressurizing unit 240 into the upper space S2. The volume of water W stored in the storage tank 230 is not particularly limited, but is, for example, about 300 to 500 liters.

The pressurizing unit 240 has a nitrogen generator 241 that generates gaseous nitrogen ( _N2 ), and a compressor 242 that introduces the nitrogen generated by the nitrogen generator 241 into the upper space S2 of the storage tank 230. By introducing nitrogen into the upper space S2 by the compressor 242, the floating lid 232 is forced downward, and the water W stored in the lower space S1 is pressurized. By using nitrogen to pressurize the water W, the safety of the power generation device 200 is increased and costs can be reduced.

However, the gas introduced into the storage tank 230 is not limited to nitrogen, and may be, for example, atmospheric air. In this case, the pressurizing unit 240 is essentially composed of only the compressor 242, so that the power generation device 200 can be made smaller and less expensive. Also, for example, when nitrogen is used, a cylinder filled with nitrogen can be used instead of the nitrogen generator 241.

The power generating unit 250 has a generator 254 and a power generating section 251 that generates power to drive the generator 254. The power generating section 251 also has a water wheel 252 (rotated body) that rotates due to collision with water W discharged from the storage tank 230, and an output shaft 253 that outputs the rotation of the water wheel 252, and the output shaft 253 is connected to the generator 254. Therefore, electricity is generated by the generator 254 when the water wheel 252 rotates.

The configuration of the power generating unit 251 is not limited to the above-mentioned configuration, and may be any configuration as long as it can drive the generator 254 using the power of the water W. In addition, in the illustrated configuration, the output shaft 253 and the generator 254 are directly connected, but this is not limited to this, and a transmission such as an accelerator or reducer, or a gear or chain that transmits power may be interposed between them.

The configuration of the generator 254 is not particularly limited as long as it can perform its function. For example, it may be an AC generator having a pair of coils and a magnet disposed between the pair of coils and connected to the output shaft 253, and the magnet rotates between the pair of coils by the rotation of the output shaft 253, or conversely, it may be a DC generator having a pair of magnets and a coil disposed between the pair of magnets and connected to the output shaft 253, and the coil rotates between the pair of magnets by the rotation of the output shaft 253. It may also be a generator of any other structure.

The power generating unit 251 further includes a recovery tank 255 that recovers the water W used to rotate the water wheel 252. The water W recovered in the recovery tank 255 is sent to the pump unit 210.

The power generation device 200 configured as described above is operated as follows. In the power generation device 200, the pump unit 210 is driven to pump out water W at approximately 3 to 7 atmospheres from the pump unit 210 at a flow rate of 5,000 cc to 10,000 cc/sec. The water W pumped out from the pump unit 210 is introduced into the heat removal unit 220 and is instantly removed (cooled) to approximately room temperature. The water W cooled by the heat removal unit 220 is then introduced into the lower space S1 of the storage tank 230. The water W stored in the storage tank 230 is removed heat by mixing with the water W newly introduced from the heat removal unit 220, so the water W in the storage tank 230 is maintained at approximately room temperature. In particular, by using a multi-stage volute pump as the pressure pumps 211, 211, a swirling flow is generated in the water W, and by causing vibrational rotation of the water molecules in the heat removal devices 221, 222, the water becomes more easily mixed in the storage tank 230, making the above-mentioned effects more pronounced.

Nitrogen _N2 is introduced from the pressurizing unit 240 into the upper space S2 of the storage tank 230, and the pressure of the nitrogen _N2 in the storage tank 230 is maintained at about 3 to 7 atmospheres. Therefore, water W at about 3 to 7 atmospheres is discharged from the storage tank 230. The water W discharged from the storage tank 230 is guided by the piping 260 to directly above the water wheel 252, and then discharged toward the water wheel 252. The water W discharged toward the water wheel 252 collides with the water wheel 252, causing the water wheel 252 to rotate. Then, as the water wheel 252 rotates, power generation by the generator 254 begins.

Here, the swirling flow of water W and the oscillatory rotation of water molecules generated by the pressure pumps 211, 212 and the heat sinks 221, 222 are maintained until they hit the water wheel 252 after passing through the storage tank 230. Then, when the water W with the swirling flow and oscillatory rotation still occurs hits the water wheel 252, the pressure of the water W instantly drops to the original pressure of the water W. In other words, it is released from the pressure caused by the nitrogen N2. Therefore, the water W that hits the water wheel 252 and is collected in the collection tank 255 is at atmospheric pressure/16°C. In this way, by creating a large pressure difference between the upstream and downstream sides of the water wheel 252, the water wheel 252 can be rotated faster, improving power generation efficiency.

The water W recovered in the recovery tank 255 is introduced into the pump unit 210, where it is pressurized again and sent out toward the heat removal unit 220. In the power generation device 200, power generation can be continued by circulating the water W in this manner. In particular, by having the heat removal devices 221 and 222, the water W can be maintained at approximately room temperature, and evaporation and vaporization of the water W can be prevented for long periods of time. In other words, measures such as periodically stopping operation to prevent the temperature of the water W from rising are no longer necessary, and continuous operation is possible. This results in a power generation device 200 that can demonstrate excellent power generation efficiency.

The operation of the power generation device 200 has been described above, but the above is only an example, and for example, the temperature and air pressure of the water W in each part, the capacity of the storage tank 230, etc. are not particularly limited.

As described above, the heat removal device 100 according to the present invention includes an evaporator 150 having a helical tube 151 formed by helically winding a tube 152 having a groove 153 extending in the circumferential direction on the outer periphery, an inner tube 155 arranged inside the helical tube 151, and an outer tube 156 arranged outside the helical tube 151 and arranged to accommodate the helical tube 151 between the inner tube 155. The refrigerant Q is passed through the helical tube 151, and water W (to be removed from the heat) is passed between the inner tube 155 and the outer tube 156, whereby heat exchange between the refrigerant Q and the water W is performed, and the water W is removed from the heat. With this configuration, when the water W passes between the inner tube 155 and the outer tube 156, the internal energy of the water molecules is released all at once. Therefore, the water W can be removed from the heat instantly. Therefore, the industrial applicability is great. In addition, the heat removal method, power generation device, and power generation method of the present invention use the same device and principles as the heat removal device of the present invention, so they also have great industrial applicability.

100...heat removal device, 110...compressor, 120...condenser, 121...fan, 130...first spiral tube, 131...collecting tube, 132...collecting tube, 140...second spiral tube, 141...collecting tube, 142...collecting tube, 150...evaporator, 151...spiral tube, 152...tube, 153...groove, 154...double tube, 155...inner tube, 156...outer tube, 157...induction section, 158...recovery section, 160...piping, 200...power generation device, 210...pump unit, 211...pressure pump, 212...pressure pump, 220...heat removal unit, 221...heat removal device, 222...heat removal Device, 230...storage tank, 231...tank body, 232...floating lid, 240...pressurizing unit, 241...nitrogen generator, 242...compressor, 250...power generating unit, 251...power generating section, 252...water wheel, 253...output shaft, 254...generator, 255...recovery tank, 260...piping, 270...check valve, A...arrow, D...depth, F...surface, P...pitch, Q...refrigerant, Q1...gas refrigerant, Q2...liquefied gas refrigerant, Q3...liquid refrigerant, Q4...liquid refrigerant, Q5...gas refrigerant, S...space, S1...lower space, S2...upper space, W...water, θ...feed angle

Claims (8)

a helical tube formed by winding a tube having a groove extending in a circumferential direction on an outer periphery thereof in a helical shape, the tubes being in contact with each other adjacent to each other ;
an inner tube located on the inner periphery side of the spiral tube and arranged in contact with the inner periphery of the spiral tube ;
an outer tube located on the outer periphery side of the spiral tube, arranged in contact with the outer periphery of the spiral tube, and arranged to accommodate the spiral tube between the outer tube and the inner tube;
A heat removal device characterized in that the object to be removed from the heat source flowing between the inner tube and the outer tube flows downstream by repeatedly moving toward the downstream tube while rotating around the tube along the groove, and during this time, heat is removed by heat exchange with the refrigerant flowing inside the spiral tube . The heat dissipation device according to claim 1, wherein the groove is formed in a spiral shape. A compressor that compresses the refrigerant to produce a high-temperature, high-pressure gas refrigerant;
a condenser for condensing the gas refrigerant into a wet gas refrigerant;
A first spiral tube that reduces pressure and liquefies the wet gas refrigerant to form a liquid refrigerant;
and a second spiral tube for decompressing and expanding the liquid refrigerant to produce a low-temperature, low-pressure liquid refrigerant.
3. The heat removal device according to claim 1, wherein the low -temperature, low-pressure liquid refrigerant from the second spiral tube is introduced into the spiral tube. a helical tube formed by winding a tube having a groove extending in a circumferential direction on an outer periphery thereof in a helical shape, the tubes being in contact with each other adjacent to each other ;
an inner tube located on the inner periphery side of the spiral tube and arranged in contact with the inner periphery of the spiral tube ;
an outer tube that is located on the outer periphery side of the spiral tube , that is disposed in contact with the outer periphery of the spiral tube, and that is disposed so as to accommodate the spiral tube between the outer tube and the inner tube;
A heat removal method characterized in that the object to be removed from the heat source flowing between the inner tube and the outer tube flows downstream by repeatedly moving toward the downstream tube while rotating around the tube along the groove, and heat is removed by heat exchange with the refrigerant flowing inside the spiral tube . A pressure pump that pressurizes and delivers the liquid;
A heat removal device according to any one of claims 1 to 3 , which removes heat from the liquid pumped out from the pressure pump;
a storage tank that stores the liquid whose heat has been removed by the heat removal device;
a pressurizing unit that introduces a gas into the storage tank and pressurizes the liquid in the storage tank;
a power generation unit that is driven by collision with the liquid discharged from the storage tank. The power generating device according to claim 5 , wherein the power generating unit has a driven body that rotates by collision with the liquid. The power generating device according to claim 6 , wherein the liquid that has collided with the rotating body is introduced into the pressure pump. The liquid is pressurized and pumped out by a pressure pump.
The liquid pumped out from the pressure pump is subjected to heat removal by the heat removal method according to claim 4 ,
storing the liquid whose heat has been removed in a storage tank;
introducing a gas into the storage tank to pressurize the liquid in the storage tank;
A power generation method comprising driving a power generation unit by collision with the liquid discharged from the storage tank.

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