JPH0581833B2 - - Google Patents

Description

[Detailed Description of the Invention] [Field of Industrial Application] The present invention relates to a heat storage device using latent heat, and more particularly to a heat storage device using latent heat based on the phase change phenomenon of melting and solidification of a substance that occurs at a constant temperature. .

[Problems to be solved by conventional technology and invention]

As is well known, heat storage methods using latent heat storage materials have higher heat storage density than sensible heat utilization technology, can obtain a considerable amount of heat, and can be made compact. It has been attracting attention recently for a number of reasons. Therefore, conventionally, latent heat storage materials,
Technological developments have been made on heat storage tanks that use them, latent heat storage methods, devices, systems, etc., and proposals centering on latent heat storage materials that specifically target thermal heat such as solar heat have been made.

Of these, if we look at the overall system of the latent heat storage device, for example, in "Energy and Resources" published by the Energy and Resources Study Group, Vol. 4 No. 4 (1983), p. 51-54, there is Several reports have been made regarding solar systems and air conditioners, and as shown in Figure 14, the heat transfer medium exiting the compressor A and condenser B is passed through a heat storage tank C and circulated back to the source. Heat storage mode and heat transfer medium in heat storage tank C
A heat storage cooling device is known that enables a heat radiation mode in which heat is circulated between the air cooler D and the air cooler D. Although this is a fairly effective technique, this conventional technique is simple in that during the heat dissipation mode, the entire amount of the heat transfer medium that leaves the air cooler D always passes through the heat storage tank C and is returned to the air cooler D again. This is because there is no special way to control and supply a heat transfer medium at a temperature that matches the heat usage conditions of the heat-using equipment, such as an air cooler, to the heat-using equipment. However, many issues remain to be resolved in order to put this technology to practical use without going beyond the scope of experimental research. Therefore, the first invention of the present application,
One purpose is to focus on the fact that by changing the flow rate of the heat transfer medium passing through the heat storage tank, the amount of heat released from the heat storage tank to the heat transfer medium changes. By detecting the actual temperature of the heat transfer medium entering the exchanger and using it as an operation signal to manipulate the flow rate of the heat transfer medium passing through the heat storage tank, the flow rate of the heat transfer medium passing through the heat storage tank is controlled. To provide a device which can constantly control the temperature of a heat medium in accordance with predetermined heat usage conditions of a heat usage device, and which can easily carry out the control.

In addition, it goes without saying that what is important for the efficient operation of these latent heat storage devices or systems is the heat storage tank that constitutes a part of them. In most cases, a shell-and-tube type or a spiral coil type is used, in which a tube is passed through the tank body and a heat storage medium, which is a phase change material, is packed around the tube. This applies to the heat storage tank C of the device shown in FIG. 14 mentioned above and the heat storage tank shown in Japanese Patent Publication No. 53-9596. In addition, JP-A-53-25939
As seen in the above publication, a method has been proposed in which the heat storage medium is placed in a cylindrical steel container, and the container is placed on a roller and rotated by a small motor to exchange heat with the air. However, according to recent research by the applicant and others, these shell-and-tube type and spiral coil type heat storage tanks have a certain limit in improving the volume of the heat storage medium (heat storage capacity) in the heat storage tank due to their structure. There are many difficulties in shortening the heat storage and heat dissipation time, there are restrictions on the shape of the heat storage container because circular tubes and spiral coils are used, and it cannot be immediately incorporated into existing heat storage tanks of arbitrary shapes. It was discovered that cracks occurred at the corners, etc., and the durability was not very good.In order to advance the latent heat storage device from the testing stage to the practical stage, it was desired to develop a heat storage tank to replace it.

Therefore, as a result of several tests and studies in response to the above-mentioned request, the present applicant and others have found that it is possible to use a small spherical heat storage body in which a heat storage medium, which is a phase change material, is filled into small spheres. Reaching the recognition that this would solve the problems of A technology containing small spherical heat storage bodies has been disclosed. The device of this invention also has a heat storage tank containing the above-mentioned small spherical heat storage body and can solve the above-mentioned problems, but the device of the above-mentioned patent application filed in 1982
Among issues such as No. 52974, the following unresolved parts were still left.

One is that for stable operation, it is necessary that the heat transfer medium passing through the heat storage tank and the small spherical heat storage bodies come into uniform contact with each other, so this is an improvement measure for this purpose.
There are two types of this, one of which is:
When passing the heat transfer medium from the entrance of the heat storage tank towards the group of small spherical heat storage bodies, it must be dispersed as much as possible, and this is a means to ensure this.

Another problem is that when a heat transfer medium passes between a group of small spherical heat storage bodies, if non-uniform convection occurs between one part and another, the thermal conductivity of each part becomes non-uniform, and each small spherical heat storage body Since the body does not exchange heat equally, this is an improvement measure to prevent uneven convection from occurring in each part.

Another reason is that the longer the residence time of the heat transfer medium in the heat storage tank, the higher the temperature efficiency of heat exchange. This must be determined optimally, but since the flow rate through the tank is greatly affected by pressure loss due to fluid friction, this pressure loss must be determined appropriately. Therefore, the diameter and length of the tank must be determined appropriately. Furthermore,
After the small spherical heat storage element is housed in the heat storage tank, there is the problem of draining water, which is extremely important in practice.

Therefore, another object of the first invention of the present application is to maximize the heat storage capacity in a tank of constant volume, and to
It has a good heat transfer amount per unit volume and can be designed to shorten heat storage/radiation time as much as possible, has fewer corroded parts and can improve durability, and is not subject to tank design restrictions from the heat storage body side. To provide a heat storage device utilizing latent heat having a heat storage tank having the following advantages, and in particular, to uniformly diffuse the heat transfer medium flowing into the heat storage tank into each part of the cross section perpendicular to the direction of flow immediately after the flow of the heat transfer medium into the heat storage tank. The purpose of the present invention is to provide a device that has a means for uniformly contacting a small spherical heat storage body, and the heat storage tank itself is of a horizontal stationary type, eliminating the influence of external forces and gravity that cause unpredictable convection. To provide a device having a heat storage tank in which uniform convection occurs in each part of a group of small spherical heat storage bodies, and uniform heat transfer is performed in each part, and further to determine the pressure loss of a heat transfer medium passing through the heat storage tank. By appropriately determining the relationship between the diameter and length of the heat storage tank, which is in the range of 1:3 to 6, according to various experiments of the applicant, it is possible to achieve a temperature-efficient heat exchange. An object of the present invention is to provide an apparatus having a tank that can ensure the flow rate (residence time in the tank) of a heat transfer medium.

In addition, when the heat transfer medium is drained as necessary after the group of small spherical heat storage bodies is densely housed, the drain can be easily removed without dropping the accumulated small spherical heat storage bodies downward, making it easy to use on-site. An object of the present invention is to provide a device having a tank that is convenient to handle.

Furthermore, the most fundamental thing for this type of latent heat storage device is the heat storage medium that is filled in the heat storage body housed in the heat storage tank, and a considerable amount of research and development has gone into this. Although many technologies have been proposed, most of them have melting or freezing points of about 5° C. or higher. There are only a few types of heat storage media proposed in JP-A-59-93780 and the like that have temperatures below 0°C. However, since these are heat storage media themselves, there are not many disclosures about the devices themselves using the heat storage media.

Therefore, the objects of the second to fourteenth inventions of the present application each have the following objects in addition to the object of the first invention. That is, the object of the present invention is to provide a latent heat storage device in which a heat storage medium that operates at melting and freezing points of -3°C, -6°C, -8°C, and -10°C is sealed in a small spherical heat storage body. Therefore, it can be used as a cold source for storage and reaction processes in beer factories, soft drink factories, etc., as a cold source for low-temperature reactors in dairy plants, and as a cold source for freezing products and product display cases, as well as for the distribution of flowers and fruits. An object of the present invention is to provide a heat storage device using latent heat suitable for use as a cold heat source for industrial storage.

Furthermore, melt at -15℃, -17℃, -18℃, and -21℃, respectively.
An object of the present invention is to provide a heat storage device using latent heat, in which a heat storage medium that acts as a freezing point is enclosed in a small spherical heat storage body, and this is housed in a heat storage tank. Therefore, we have developed a heat storage device using latent heat that is suitable for use as a cold source for meat storage in slaughterhouses, meat centers, etc., as a cold source for ice rinks, and as a cold source for storage facilities in drug factories, blood storage facilities, etc. It is on offer.

In addition, although it is a heat storage medium that operates at 0°C as its melting and freezing point, it is especially sealed in a small spherical heat storage body and housed in a heat storage tank. To provide a heat storage device using latent heat suitable for.

Furthermore, although it is a heat storage medium that operates as a melting and freezing point at -21℃, -28℃, -33℃, and -37℃, it is especially encapsulated in a small spherical heat storage body, which is housed in a heat storage tank. It is an object of the present invention to provide a heat storage device using latent heat which is particularly suitable for a cold heat source for a frozen warehouse having a characteristic tank.

Another objective is to provide a heat storage device using latent heat that uses a heat storage medium that operates at a melting and freezing point of 64°C, which is suitable for commercial building heating, hot water supply, water heaters, etc. It is also an object of the latent heat storage devices of the second to fourteenth inventions to operate stably even after repeated melting and solidification, and to improve stability.

[Means and actions for solving problems]

Means for solving the above problems will be explained below using FIGS. 1 to 13, which correspond to embodiments. That is, in the first invention of the present application, first, the heat exchanger 1 on the heat generation equipment side, the pump 2, the heat storage tank 7, and the heat exchanger 3 on the heat usage equipment side are sequentially and cyclically connected to the heat transfer medium heat exchanger tube. The branch point 9 between the heat storage tank 7 and the heat exchanger 3 on the heat-using equipment side, and between the heat exchanger 3 on the heat-using equipment side and the heat exchanger 1 on the heat-generating equipment side is connected to the pipe 8. At the same time, a pipe 10 connects between the heat exchanger 3 on the heat-using equipment side and the branch point 9, and between the heat exchanger 1 on the heat-generating equipment side and the pump 2, and the three-way control valve 1
1 and 12, the heat transfer medium discharged from the heat exchanger 1 on the heat generation equipment side is transferred to the heat storage tank 7 by the pump.
In the heat storage mode, the heat transfer medium exiting the heat storage tank 7 is passed through the heat exchanger 3 on the heat-using equipment side by a pump, and is returned via the pipe 10 to the heat exchanger 1 on the heat generating equipment side. At the same time, a bypass pipe 13 is connected between the pump 2 and the heat storage tank 7 and a position in front of the heat exchanger 3 on the heat-using equipment side, and a flow rate is connected to the bypass pipe 13. By disposing the quantity control valve 14, when the actual detected temperature t of the heat transfer medium at the position 15 before entering the heat exchanger 3 on the heat-using equipment side exceeds the control target set temperature T at the same position, the deviation is controlled. Using Δt as an operation signal, in the heat dissipation mode, the flow rate control valve 14 is operated so that a part of the heat transfer medium that has exited the heat exchanger 3 on the heat-using equipment side passes through the bypass pipe 13 again and is transferred to the heat-using equipment for heat exchange. The opening degree is controlled so that the heat storage tank 7 can be returned to the container, and the heat storage tank 7 is configured as a horizontal stationary type, and has a cylindrical body 19 and connection ports 22, which are attached to both left and right ends of the body 19, respectively. 23 are formed on the body lids 20 and 21, and the body 19 faces the respective connection ports.
Flow diffusion members 24 arranged near both left and right ends of the
25 and a draining means 33 formed below the body 19 which is placed horizontally, and the ratio of the diameter D of this heat storage tank 7 to the total length L corresponding to the horizontal length is 1:3 to 6. It is defined within the range of
Inside the tank 28, which is partitioned by the one and the other flow diffusion members 24 and 25, there is a heat storage medium 3 inside.
The small spherical heat storage body 29 filled with 0 is densely housed, and the drain removal means 33 does not allow the small spherical heat storage body 29 to pass through, and the small spherical heat storage body 29 is
A drain pipe 36 including one or more drain gaps 35 formed on the lower surface of the body to allow passage of a heat transfer medium in the gaps therebetween, and the drain pipe 36
This is a heat storage device using latent heat, characterized in that it is constituted by an on-off valve 37 that is normally closed.

With such a configuration, the following heat storage and heat dissipation operations are performed.

The heat storage operation is performed by switching the three-way control valves 11 and 12 to transfer the heat transfer medium between the heat exchanger 1 on the heat generating equipment side and the heat storage tank 7.
circulate between.

The heat dissipation operation is performed by switching between the three-way controls 11 and 12 to circulate the heat transfer medium between the heat storage tank and the exchanger 3 on the heat-using equipment side. In this heat dissipation operation, the actual detected temperature of the heat transfer medium passing through the front position 15 of the heat exchanger on the heat-using equipment side is t, the set temperature as a control target at the same position is T, and the deviation between t and T is Δt. Then, t
exceeds T, that is, when the target is cold heat, t<T, which means it is too cold, and when the target is heat, t>T, which means it is too warm. In this case, the opening of the flow rate control valve 14 is controlled using the deviation temperature Δt as an operating signal, and a part of the heat transfer medium exiting the heat exchanger 3 on the heat-using equipment side is transferred to the bypass pipe 13.
Also, the heat transfer medium returns to the heat exchanger 3 on the heat-using equipment side through there. As a result, the flow rate of the heat transfer medium through the heat storage tank 7 is reduced, and the temperature of the heat transfer medium at the position 15 in front of the inlet of the heat exchanger 3 on the heat-using equipment side is controlled based on the control target.

In these heat storage/dissipation modes, the heat storage tank 7 of the present invention has a structure that accommodates small spherical heat storage bodies, so it can store about 65% of the heat storage capacity in a tank with a constant volume, which makes it different from other types. In addition to being able to have a significantly larger heat storage capacity compared to the heat storage tank 7, the heat storage/radiation time can be shortened, and in particular, the heat transfer medium can be diffused into and passed through the heat storage tank 7, so these advantages are exhibited. be done. And there are almost no problems caused by corrosion. In addition, since the heat storage tank itself is a horizontal cylindrical stationary type, it does not require any movable source and is durable, and the heat transfer medium passing through the heat storage tank 7 does not generate convection due to external rotational force or convection caused by falling in the direction of gravity. The convection is mainly a flow from one side to the other, and the heat transfer is approximately uniform in each part of the small spherical heat storage bodies 29, so the heat storage and release characteristics of the device are stabilized. , the diameter D and length L of the horizontally stationary heat storage tank 7 are set in the range of 1:3 to 6, and the pressure loss when the fluid passes is set appropriately to achieve heat transfer with good temperature efficiency in heat exchange. It is possible to ensure the flow rate of the medium (residence time in the tank). In addition, the drain gap 35 does not allow the passage of the small spherical heat storage body 29 and allows only the heat transfer medium to pass through.
Since there is a drain pipe 36 including the drain pipe 36, draining is easy. Further, according to the second to fourteenth inventions of the present application, the small spherical heat storage body 2 in the heat storage tank 7 of this device
9 are filled with the following main liquids.

That is, a eutectic mixture of sodium carbonate (Na ₂ CO ₃ ) aqueous solution, a eutectic mixture of potassium hydrogen carbonate (KHCO ₃ ) aqueous solution, a eutectic mixture of barium chloride (BaCl ₂ ) aqueous solution, and a potassium chloride (KCl) aqueous solution, respectively. Eutectic mixture of aqueous solutions, ammonium chloride (NH ₄ Cl) eutectic mixture of aqueous solutions, ammonium nitrate (NH ₄ NO ₃ )
Eutectic mixture in aqueous solution, sodium nitrate (NaNO ₃ )
Eutectic mixture in aqueous solution, sodium chloride (NaCl)
Eutectic mixture in aqueous solution, sodium bromide (NaBr)
Eutectic mixture of aqueous solution, eutectic mixture of magnesium chloride (MgCl ₂ ) aqueous solution, eutectic mixture of potassium carbonate (K ₂ CO ₃ ) aqueous solution, sodium hydroxide (NaOH) aqueous solution, water (H ₂ O) It is filled with a solution containing a trace amount of sulfuric acid (H ₂ SO ₄ ). By these, each -3
℃, -6℃, -8℃, -10℃, -15℃, -17℃, -18
A latent heat utilizing device is provided that operates at temperatures of 0°C, -21°C, -28°C, -33°C, -37°C, 64°C, and 0°C as melting and freezing points.

〔Example〕

Next, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

In this embodiment, a case where the present invention is applied to a cooling or freezing device as a heat-using device will be described below.

1 is an evaporator as a heat exchanger on the heat generating equipment side; 2
is a pump, 3 is a cooler as a heat exchanger on the heat-using equipment side, and evaporator 1 and pump 2 are connected by pipe 4.
The pump 2 and the cooler 3 are connected by a pipe 5, and the cooler 3 and the evaporator 1 are connected by a pipe 6, respectively. This constitutes a normal cooling loop in which the heat transfer medium cooled in the evaporator 1 returns to the evaporator 1 again through the pipe 4, pump 2, pipe 5, cooler 3, and pipe 6.

A heat storage tank 7 is disposed in the middle of the pipe 5, and a pipe 8 is connected between the downstream side and the middle of the pipe 6, so that the heat transfer medium cooled by the evaporator 1 can be transferred to the pipe 4,
A heat storage loop returns to the evaporator 1 through the pump 2, the pipe 5, the heat storage tank 7, the pipe 8, and the branch point 9.

By connecting the pipe 10 between the upstream position of the branch point 9 in the pipe 6 and the pipe 4, the heat transfer medium leaving the heat storage tank 7 is transferred to the cooler 3, the pipe 10, the pump 2, and the pipe 4. 5 and returns to the heat storage tank 7 again, forming a heat dissipation loop.

In order to enable these normal cooling operation mode, heat storage mode, and heat radiation mode, a three-way switching valve 11 is connected to the connection point between the pipes 5 and 8, and a three-way switching valve 12 is connected to the connection point between the pipes 6 and 10. is connected.

A bypass pipe 13 is branched from the pipe 5 between the pump 2 and the heat storage tank 7 and connected between the heat storage tank 7 and the cooler 3, and a flow rate control valve 14 is disposed in the middle of the bypass pipe 13. The control valve 14 is opened and closed under proportional control by a regulator using the detected temperature of the heat transfer medium passing through the front position 15 of the cooler 3 as an operating signal.
18 indicates a controller, and 18 indicates a setting device.

In the above, the operating conditions of the three-way switching valves 11 and 12 are set as follows. During normal cooling operation Inlet a of the three-way control valve 11 is closed, outlet b is closed, and outlet c is open; Inlet d of the three-way control valve 12 is open, outlet e is closed, and outlet f is open. During heat storage operation, the three-way control valve 11 is closed. Inlet a open, outlet b open, outlet c closed, three-way control valve 12 inlet d closed, outlet e closed, outlet f open, during heat storage operation, three-way control valve 11 inlet a open, 24b closed, outlet c open , Inlet d of three-way control valve 12 is open, outlet e is open, outlet f is closed, during backup operation Inlet a of three-way control valve 11 is open, outlet b is closed, outlet c is open, and inlet d of three-way control valve 12 is open. , outlet e is closed, outlet f is open, and the operating conditions of the flow rate control valve 14 are as follows.

That is, t = actual detected temperature of the heat transfer medium passing through the detection position 15 before the cooler 3 T = set temperature as a control target of the heat transfer medium passing through the detection position 15 before the cooler 3 Δt = deviation between t and T , when t=T, it is closed, and when t<T, it is open, and this opening degree is proportionally controlled according to Δt. however,
During normal cooling operation, it is opened by an operation signal.

Next, the heat storage tank 7 constituting this device will be described in detail.

The heat storage tank 7 is configured as a horizontal stationary type,
It has a cylindrical body 19 and body covers 20 and 21 attached to both left and right ends of the body.

Connection ports 2 are provided in the center of the body lids 20 and 21, respectively.
2 and 23 are formed, and are connected to the pipe 5 via these connection ports 22 and 23. Near both left and right ends of the body 19, flow diffusion members 24, 25 are installed in the body in the form of partition walls, facing the connection ports 22, 23. A flow port 26 is formed. That is, the flow port 26 is formed to communicate between the partition chamber 27 partitioned by the member 24 or 25 and the tank interior 28,
It is preferable that they are formed radially from the center to the circumferential direction, and that the number of formed pieces increases in the circumferential direction so that the number of formed pieces per unit area is approximately equal in each part. In the tank interior 28 of the heat storage tank 7, a large number of small spherical heat storage bodies 29 are densely housed in the tank. When this small spherical heat storage body 29 changes from liquid phase to solid phase at solidification temperature,
A spherical shell 31 is filled with a heat storage medium 30 that stores cold heat as latent heat of solidification and releases the previously stored cold heat when changing from a solid phase to a liquid phase.

The individual size of the small spherical heat storage body 29 is the diameter
The range is 20mm to 200mm, for example about 65mm,
This means that the required amount of heat storage and heat release for the entire heat storage tank is determined by the conditions of the cooling and refrigeration equipment, heat storage and release operating conditions, etc. It is sufficient to set the standard based on ensuring the above. Preferably, at the same time, the manufacturing cost increases as the number of small spherical heat storage bodies 29 that are accommodated in a certain volume of the heat storage tank 7 increases, that is, the diameter of each small spherical heat storage body 29 decreases. At the same time, it is preferable to process the product so as to satisfy these manufacturing conditions.

There are various materials for the spherical shell 31, such as metal and synthetic resin, and the material is selected based on the ability to maintain the spherical shape against external and internal forces, heat resistance, production processing, etc. , in this invention,
The size of the shell 31 is determined so that a space 32 not occupied by the heat storage medium 30 is formed within the shell 31 when the heat storage medium 30 is in a liquid phase. At the same time, the size of the space 32 is determined so that the amount of expansion caused by the volumetric expansion due to solidification of the heat storage medium is absorbed by the expansion of the space 32 and the shell 31.
Expansion of the shell 31 is made possible by the pressure during expansion of the solidified heat storage medium, and when the heat storage medium changes from a solid phase to a liquid phase, the shell 31 also contracts, but the shell 31 remains at the initially set size. The contraction is stopped leaving a space 32. For example, when the heat storage medium 30 solidifies, it expands by 1.08 times its weight when it is a liquid, that is, by 8%.The space 32 absorbs the expansion by 5.5% and the shell 31 expands by 2.5%.
This determines the size of 2. In other words, when the heat storage medium 30 is filled by injection or the like into the spherical shell 31 processed by a hollow molding method, a vacuum molding method, etc., the heat storage medium 30 is of course a liquid;
When filling the liquid heat storage medium 30, the space 32 is filled with a space equivalent to 5.5% in the above example.

The spherical shell 31 itself is a hard spherical shell, but because it is formed with a thin wall, it expands according to the expansion of the heat storage medium due to the internal pressure when the solidified heat storage medium expands, and when the heat storage medium changes to a liquid phase. Since it naturally returns to its original state while leaving the original space, a variety of materials can be selected, such as metal and synthetic resin, but in order to make the above shell expansion easier, it is best to use a material that has high expansion and contraction properties. Among synthetic resins with a temperature of 90° C. or higher, polypropylene and high-density polyethylene are preferred considering other stress resistance, heat resistance, and processability. Furthermore, regarding the above-mentioned expansion of the shell 31, the following considerations should be taken into consideration in the design. That is, the shell 31 is expanded by the internal pressure when the solidified heat storage medium 30 expands in volume, and the heat storage medium used is adjusted so that the degree of expansion of the shell 31 can be determined to a degree that does not cause material destruction. The size of the space 32 is determined in consideration of the amount of volumetric expansion. For this purpose, it is necessary to keep the expansion and contraction of the shell 31 within the elastic range determined by the material of the shell 31, its radius, the thickness of the thin wall, etc., or to maintain the tensile strength determined by the material of the shell 31, etc. Various engineering methods are used to make expansion possible within a range that takes into account the safety factor (ultimate strength).

Now, a drain removal means 33 is provided at the bottom of the tank 7 that accommodates a large number of such small spherical heat storage bodies 29, and this drain removal means 33 does not allow the small spherical heat storage bodies 29 to pass through. , a drain pipe 36 including one or more drain gaps 35 formed in the lower surface 34 of the body 19 to allow passage of a heat transfer medium in the gaps between the small spherical heat storage bodies, and the drain pipe 36. It consists of an on-off valve 37 that is normally closed, and a heat insulating material 38 attached around them. To explain some specific examples of these draining means, as shown in FIGS. 4 and 5, one is a single circular hole opening in the body 19 and having a diameter smaller than the diameter d of the small spherical heat storage body 29. One or more strip members 3 horizontally across the drain gap 35 and the single circular hole so that the small spherical heat storage body 29 does not sit there and block it.
9 is installed. The other is the drain gap 35, which opens in the body 19 and consists of a plurality of circular holes smaller than the diameter d of the small spherical heat storage bodies, as shown in FIG. The formation pitch P of the small circular holes is set to be smaller than the diameter d of the small spherical heat storage bodies so that the small spherical heat storage bodies 29 do not sit in each of the plurality of small circular holes and block them.

Furthermore, another example is as shown in FIG.
It is conceivable to have a single groove opening 35 narrower than the diameter d of the small spherical heat storage element 29. Furthermore, another example, as shown in FIG. 8, may consist of a plurality of drain gaps 35 opening into the body 19 and having a width narrower than the diameter d of the small spherical heat storage element 29. Other body parts not shown 1
It may be one in which rectangular holes opening at 9 and having sides smaller than the diameter d of the small spherical heat storage body 29 are arranged in a grid pattern. Now, for such a heat storage tank 7, when its diameter is D and the length between one body cover 20 and the other body cover 21 is L, D:L is set in the range of 1:3 to 6. do.

To give some specific examples, D=950mm, L=
3000mm combination, D=1250mm, L=4200mm combination, D=1600mm, L=5300mm combination, D=
1800mm, L=6000mm combination, D=1900mm, L
= 7100 combination, D = 2100mm, L = 9100mm combination, D = 2500mm, L = 10780mm combination,
Combination of D=3000mm, L=11200mm, D=3000
mm, a combination of L=14800 mm, etc.

The main reason for this is that the lower the flow rate when the heat transfer medium passes through the tank, that is, the longer the residence time in the tank, the higher the temperature efficiency of heat exchange. On the other hand, the lower the flow rate, the lower the heat transfer coefficient. Therefore, it is necessary to determine an appropriate flow rate that optimally satisfies both conditions. Therefore, the applicants of the present invention have determined through many experiments that it is sufficient to secure a movement amount of at least 2.5 m ³ /h. And this minimum 2.5
The amount of movement of approximately m ³ /h is determined by the velocity head of the heat transfer medium given by the pump and the pressure loss when passing through the tank, and this pressure loss is proportional to the length L of the tank. It becomes large and is inversely proportional to the diameter D. Therefore, when the velocity head is constant, the above flow velocity can be determined by optimally finding D and L, but it is desirable that D and L are as above, and 1 of D On the other hand, L is selected within the range of 3 to 6 because the pressure loss resulting from fluid friction varies depending on the number of small spherical heat storage bodies.

A series of operations will be explained based on the above configuration.

FIG. 9 shows the operation during normal cooling operation.

At this time, the temperature control valve 14 is operated to open, the inlet a of the three-way control valve 11 is closed, the outlet b is closed, and the outlet c is open, the inlet d of the three-way control valve 12 is open, the outlet e is closed, and the outlet Since f is open, the heat transfer medium leaving the evaporator 1 as shown by the arrow 40 passes through the bypass pipe 13 by the pump 2, is sent to the cooler 3, and returns to the evaporator 1 again depending on the load.

FIG. 10 shows the operation of the heat storage evaporator.
At this time, the temperature control valve 14 is closed, the inlet a of the three-way control valve 11 is open, the outlet b is open, the outlet c is closed, the inlet d of the three-way control valve 12 is closed, the outlet e is closed, and the outlet f is closed. Since it is open, the heat transfer medium leaving the evaporator 1 is passed through the heat storage tank 7 by the pump as shown by the arrow 41.
It returns to the evaporator 1 via the pipe 8.

When the heat transfer medium passes through the heat storage tank 7, the heat transfer medium comes into contact with a large number of small spherical heat storage bodies 29 in the heat storage tank 7, so that the heat storage medium 30 in the small spherical heat storage bodies 29
solidifies at the freezing point. During solidification, cold heat as latent heat of solidification is transferred to the heat storage medium 30 of the small spherical heat storage body 29.
heat is stored inside.

FIG. 11 shows the first heat dissipation mode when t=T. Usually, this heat dissipation operation is performed when the load demand is high. At this time, the heat generating equipment side evaporator 1 is stopped under the control of a control system (not shown), the inlet a of the three-way control valve 11 is open, the inlet b is closed, the outlet c is open, and the three-way control valve 12 is closed. Entrance d open, exit e
Since the switch is open and exit f is closed, arrow 42
A heat transfer medium is circulated between a heat storage tank 7 and a cooler 3 by a pump 2 as shown in FIG. Cooler 3
When the heat transfer medium passes through the heat storage tank 7, it is transferred to the small spherical heat storage body 29 in the heat storage tank 7,
When it reaches its melting point, it melts and releases the previously stored cold heat to the heat transfer medium as latent heat of melting. Therefore, the heat transfer medium is cooled to meet the cooling and refrigeration load.

FIG. 12 shows the second heat dissipation mode when t<T in the heat dissipation mode of FIG. 11. At this time, the flow rate control valve 14 opens its opening in proportion to Δt, so a part of the heat transfer medium leaving the cooler 3 also flows through the bypass pipe 13 as shown by the arrow 43 and flows through the heat storage tank 7. The heat transfer medium that has come out is combined and circulated to the cooler 3 again. In this case, the flow rate passing through the bypass pipe 13 increases in proportion to Δt. Therefore, the heat storage tank 7
Since the flow rate of the heat transfer medium passing through decreases in proportion to Δt, the amount of heat radiation decreases and the temperature of the heat transfer medium at the control position 15 is controlled to the control target temperature.

FIG. 13 shows the backup operation.
At this time, the flow rate control valve 14 is opened, and the three-way control valve 11 has an inlet a open, an outlet b closed, and an outlet c open.
Furthermore, since the three-way control valve 12 has an inlet d open, an outlet e closed, and an outlet f open, the heat transfer medium leaving the heat storage tank 7 is as shown by the arrow 44.
The heat transfer medium returns to the evaporator 1 as shown in FIG.

In the heat storage/radiation mode described above, when the heat transfer medium passes through the heat storage tank 7, the following characteristics are exhibited. One is that when the heat transfer medium flows into the tank from the connection port 22 or 23 of the heat storage tank 7, it is first guided into the compartment 27, and then is guided through the respective flow ports 26 of the flow diffusion member 24 or 25. Since the heat transfer medium is uniformly diffused in each part of the cross section perpendicular to the flow direction and flows into the tank, the heat transfer medium easily contacts the small spherical heat storage bodies 29 disposed inside the tank evenly in each part. Therefore, heat transfer is performed approximately evenly in each part of the small spherical heat storage body group, and the heat transfer characteristics of the device are stabilized and reliability is achieved.

Another reason is that since this tank is of a horizontal cylindrical stationary type, no convection occurs in the heat transfer medium passing through the tank 7 due to rotational external force or falling in the direction of gravity. The convection is mainly a flow that moves horizontally from one flow diffusion member 24 or 25 to the other flow diffusion member 24 or 25, and approximately uniform heat transfer is carried out in each part of the small spherical heat storage body group. be done. Therefore, the heat transfer coefficient in each part will not be non-uniform, so the heat transfer characteristics of the device will be stable and reliability will be achieved. For one thing, D and L of this tank 7 are set in the range of 1:3 to 6. Therefore, the speed of the heat transfer medium when passing through this tank can be set to a level that ensures a minimum movement of about 2.5 m ³ /h without causing excessive or insufficient pressure loss. The residence time in the tank was appropriate, and the heat transfer coefficient and temperature efficiency of heat exchange were ensured at a good location.

Furthermore, since the drain gap 35 is formed in the lower part of the body 19 of the tank 7, it is possible to easily drain only the drain if necessary. Normally, this tank is provided with manholes 45 and 46 for introducing and discharging the small spherical heat storage bodies into the tank, but when the manhole 46 is opened and drained,
A large number of small spherical heat storage bodies fall together, causing a real problem. However, since the flow gap 35 is formed in this way, the flow gap 35 is not blocked by the small spherical heat storage body, and does not allow the small spherical heat storage body to pass through, and only the drain is allowed to flow, so that the drain can be safely drained. I was able to pull it out.

In the above-mentioned embodiment, an example was shown in which this device was applied to a cooling or freezing device, and a case was shown in which cold heat was transmitted to the cooler 3 as a heat exchanger in a heat-using device. The latent heat utilization heat storage device of the present invention is not limited to this example, and can also be applied to other cold energy utilization devices. For devices that transfer heat to the heat exchanger 3,
This heat storage device using latent heat can be applied, and when storing heat,
Warm heat is stored in the heat storage tank, and at the time of heat release, the heat is released to the heat exchanger of the heat-using equipment. In this case, the above-mentioned flow rate control valve 14 is set to open when t>T, and the actual temperature t of the heat transfer medium at the position 15 before the heat exchanger of the heat-using equipment is set to the control target. When the temperature exceeds the temperature T and becomes too warm, the flow rate control valve 14 opens and allows the heat transfer medium to flow into the bypass pipe 13 in proportion to Δt.

Of course, when this heat is targeted, the heat storage medium 30 filled in the small spherical heat storage body 29 stores heat when it melts and solidifies, and radiates the stored heat when it solidifies.

Next, the heat storage medium sealed in the small spherical heat storage body used in this latent heat utilization heat storage device will be described in detail.

As mentioned above, various studies have been conducted on latent heat storage media. The main reasons are that it is easily available as a resource, cheap, and chemically stable. Melting point within the desired operating temperature range. High heat of fusion per volume. To operate reliably and stably against long-term repetition of melting-solidification cycles.
This is being carried out to pursue those who meet the following conditions. In this sense, conventional heat storage media have achieved some results, and some of these can be applied to the latent heat utilization heat storage device of the present invention. However, as mentioned above, conventional heat storage devices using latent heat have been researched as heat storage devices using solar heat, and the latent heat storage medium itself that has been proposed as a practical device has a temperature of +5℃ or higher. Therefore, in the case of a heat storage device using latent heat that can be applied to an air conditioner or a refrigeration device as an example of the present invention, they are almost unsuitable. Therefore, the following is mainly 0℃
It has a melting and freezing point below and the operating temperature of the device is 0.
Disclosed is a heat storage medium suitable for temperatures below °C.

One example is a heat storage medium whose main liquid is a composition in which a small amount of H ₂ SO ₄ (sulfuric acid) is added to H ₂ O (water). This is suitable when the operating temperature of the device is set at around 0℃, and the latent heat per 1 ^m3 is
It is 48.4wh/ ^m3 .

Another preferred is a heat storage medium whose main liquid is a eutectic mixture of an aqueous salt solution.

That is, an aqueous solution of salts can obtain the lowest coagulation temperature at a certain temperature, and a solution with a concentration that provides the lowest temperature is used. According to the eutectic mixture with this eutectic concentration, salts and water solidify as if they were a single substance at the lowest temperature. Therefore, it operates reliably and stably in the melting-solidification cycle. At this time, the heat storage medium 30 stores heat as latent heat of solidification.

Desirable examples of such a eutectic mixture of aqueous salt solutions are shown below.

(1) If the operating temperature of the heat storage device is set at -3°C, a eutectic mixture of Na ₂ CO ₃ (sodium carbonate) aqueous solution. In this case, the eutectic concentration is 37.1%, the eutectic temperature is -3°C, and the latent heat is 48.3 kwh/m ³ .

(2) A eutectic mixture of KHCO ₃ (potassium bicarbonate) aqueous solution if the operating temperature of the heat storage device is set at -6°C. In this case, the eutectic concentration is 14.2%, the eutectic temperature is -6°C, and the latent heat is 44.6 kwh/m ³ .

(3) A eutectic mixture of BaCl ₂ (barium chloride) aqueous solution if the operating temperature of the heat storage device is set at -8°C. In this case, the eutectic temperature at the eutectic concentration is −
The temperature is 8°C, and the latent heat is 50.5kwh/ ^m3 .

(4) If the operating temperature of the heat storage device is set at -10℃, a eutectic mixture of KCl (potassium chloride) aqueous solution.
In this case, the eutectic concentration is 19.7% and the eutectic temperature is −10
℃, and the latent heat is 49.9Kwh/ ^m3 .

(5) If the operating temperature of the heat storage device is set at -15°C, a eutectic mixture of aqueous NH ₄ Cl (ammonium chloride) solution. In this case, the eutectic concentration is 18.9%, the eutectic temperature is -15°C, and the latent heat is 46.4 Kwh/ ^m3 .

(6) A eutectic mixture of aqueous NH ₄ NO ₃ (ammonium nitrate) solution if the operating temperature of the heat storage device is set at -17°C. In this case, the eutectic concentration is 42.0% and the eutectic temperature is -17°C.

(7) A eutectic mixture of NaNO ₃ (sodium nitrate) aqueous solution if the operating temperature of the heat storage device is set at -18°C. In this case, the eutectic concentration is 38.5%, the eutectic temperature is -18°C, and the latent heat is 47.65 Kwh/ ^m3 .

(8) A eutectic mixture of NaCl (sodium chloride) aqueous solution if the operating temperature of the heat storage device is set at -21°C. In this case, eutectic concentration is 23.0%, eutectic temperature is −21
℃, and the latent heat is 39.4Kwh/ ^m3 .

(9) A eutectic mixture of NaBr (sodium bromide) aqueous solution if the operating temperature of the heat storage device is set at -28°C. In this case, the eutectic concentration is 40.1%, the eutectic temperature is −
The temperature is 28℃, and the latent heat is 39.3Kwh/ ^m3 .

(10) If the operating temperature of the heat storage device is set at around -33°C, a eutectic mixture of MgCl ₂ (magnesium chloride) aqueous solution. In this case, the eutectic concentration is 20.6%, the eutectic temperature is -33.6℃, and the latent heat is 44.6Kwh/m ³
It is.

(11) If the operating temperature of the heat storage device is set at around -37°C, a eutectic mixture of K ₂ CO ₃ (potassium carbonate) aqueous solution. In this case, the eutectic concentration is 44.8%, the eutectic temperature is -36.8°C, and the latent heat is 40.0 Kwh/ ^m3 . Of course, a small amount of a nucleating agent is added to the heat storage medium containing these eutectic mixtures as the main liquid, if necessary, to prevent overcooling. Some of them are listed below: magnesium oxide (MgO), magnesium hydroxide (Mg(OH) ₂ ), magnesium carbonate (MgCO ₃ ), magnesium sulfate (MgSO ₄ ),
Magnesium chloride ( _MgCl2 ), magnesium bromide ( _MgBr2 ), calcium oxide (CaO), calcium hydroxide (Ca(OH) ₂ ), calcium carbonate ( _CaCO3 ), calcium sulfate ( _CaSO4 ), copper sulfate ( _CuSO4) ), nickel sulfate (NiSO ₄ ), zinc sulfate (ZnSO ₄ ), strontium hydroxide (Sr
(OH) ₂ ), strontium carbonate (SrCO ₃ ), barium hydroxide (Ba(OH) ₂ ), barium oxide (BaO), barium carbonate (BaCO ₃ ), sodium sulfate (Na ₂ SO ₄ ), sodium tetraborate ( Na ₂ B ₄ O ₇ ) Sodium silicate (Na ₂ SiO ₃ ), Potassium hydroxide (KOH), Potassium nitrate (KNO ₃ ),
The nucleating agent is at least one selected from nickel chloride (NiCl ₂ ).

In the above, we have shown that it is suitable for cooling and freezing, but to describe these more specifically, it is a heat storage device whose main liquid is H ₂ O with a small amount of H ₂ SO ₄ added. Heat storage devices using media can be applied to commercial building cooling and district heating and cooling systems.

A heat storage device using a heat storage medium whose main liquid is a eutectic mixture of Na ₂ CO ₃ , KHCO ₃ , BaCl ₂ aqueous solution and a eutectic mixture of KCl aqueous solution is suitable for storage or reactor use in beer and soft drink factories. As a heat source, and as a heat source for low-temperature reactors in dairy plants, and as a heat source for freezing display cases, as well as for frozen foods, fruits,
It is suitable as a storage heat source for the flower distribution industry.

Eutectic mixture of NH ₄ Cl, NaNO ₃ aqueous solution and
A heat storage device using a eutectic mixture of NH ₄ NO ₃ aqueous solution can be used as a storage heat source in slaughterhouses and meat centers.
It is suitable as a heat source for skating rinks, ice rinks, drug factory storage, and blood storage. NaCl, NaBr,
A heat storage device using a eutectic mixture of an aqueous solution of MgCl ₂ and K ₂ CO ₃ is suitable mainly as a heat source for a frozen warehouse.

In addition, the device of the first invention of the present application can also be applied to cases where the object is heat, and there have been many proposals for the heat storage medium used in the device in this case, and even if they are used. Good, but for example
CaCl ₂ 6H ₂ O aqueous solution (operating temperature, i.e. melting, solidification temperature 27°C) or MgCl ₂ 6H ₂ O + Mg(NO ₃ ) ₂
6H ₂ O (operating temperature: 57℃), Mg (NO ₃ ) 2.6H _{2 O} (operating temperature: 87℃), etc. may be used, but other materials such as commercial building heating, hot water supply, water heaters, district heating, etc. As a heat storage device using latent heat used as a heat source,
A heat storage material whose main liquid is an aqueous solution of NaOH (sodium hydroxide) is suitable.

This has a concentration of 68.97%, an operating temperature of 64℃, and 1
The latent heat per m ³ is quite high at 68 kwh/m ³ , and for this as well, at least one nucleating agent selected from the above-mentioned nucleating agents is added.

〔Effect of the invention〕

As detailed above, according to the first invention of the present application, in the latent heat storage device, the actual temperature of the heat transfer medium entering the heat exchanger on the heat-using equipment side is detected, and this is used as an operation signal. By manipulating the flow rate of the heat transfer medium passing through the heat storage tank, the temperature of the heat transfer medium supplied to the heat exchanger on the heat-using equipment side can be adjusted to the predetermined heat usage conditions on the heat-using equipment side. In addition, it is possible to provide a device that can perform adaptive control at all times.

In addition, the heat storage capacity can be maximized within a tank of a certain volume, the amount of heat transfer per unit volume is good, the heat storage/heat release time can be shortened as much as possible, and there are few corroded parts, making it durable. It is possible to provide a heat storage device using latent heat that has a heat storage tank that has advantages such as improved performance and is not subject to restrictions on tank design from the heat storage body side. In this case, it is possible to provide a device that has a means for uniformly dispersing the heat to each part of the cross section perpendicular to the inflow direction and uniformly contacting the small spherical heat storage body, and also allows the heat storage tank itself to be a horizontally stationary type. It is possible to provide a device having a heat storage tank in which uniform convection occurs in each part of a small spherical heat storage body group and uniform heat transfer is performed in each part by eliminating the effects of external force and gravity that cause difficult convection. Furthermore, the relationship between the diameter and length of the heat storage tank, which determines the pressure loss of the heat transfer medium passing through the heat storage tank, was determined to be 1:3 by the applicant's various experiments.
By setting the temperature within the range of 6 to 6, it is possible to provide an apparatus having a tank that can ensure a flow rate (residence time in the tank) of the heat transfer medium with good temperature efficiency for heat exchange.

In addition, when draining the heat transfer medium as necessary after accommodating a group of small spherical heat storage bodies densely, the drain can be easily removed without dropping the accumulated small spherical heat storage bodies downward, making it easy to handle on site. It is possible to provide an apparatus having a tank that is convenient.

Also, according to the second to fourteenth inventions of the present application,
Melt at -3℃, -6℃, -8℃, -10℃ respectively,
It is possible to provide a heat storage device using latent heat in which a heat storage medium that operates as a freezing point is sealed in a small ball heat storage body. Therefore, it can be used as a cold source for storage and reaction processes in beer listings, soft drink factories, etc., as a cold source for low-temperature reactors in dairy plants, and as a cold source for freezing products and product display cases, as well as for the distribution of flowers and fruits. It is possible to provide a heat storage device using latent heat suitable for use as a cold heat source for industrial storage.

Furthermore, melt at −15℃, −17℃, −18℃, and −21℃, respectively.
A heat storage device using latent heat can be provided in which a heat storage medium that acts as a freezing point is enclosed in a small spherical heat storage body and this is housed in a heat storage tank. Therefore, we provide a heat storage device using latent heat that is suitable for use as a cold source for meat storage in slaughterhouses, meat centers, etc., as a heat source for ice skating rinks, and as a cold source for storage in drug factories, blood storage facilities, etc. can. In addition, a heat storage medium that melts and operates at 0°C as its freezing point is sealed in a small spherical heat storage body, and this is housed in a heat storage tank. equipment can be provided.

Furthermore, a heat storage medium that acts as a melting and freezing point at -21℃, -28℃, -33℃, and -37℃ is sealed in a small spherical heat storage body, and this is housed in a heat storage tank. It is possible to provide a heat storage device using latent heat that is particularly suitable for cold sources for cold storage warehouses.

In addition, it is possible to provide a heat storage device using latent heat that uses a heat storage medium that operates as a melting and freezing point of 64°C, which is suitable for commercial building heating, hot water supply, water heaters, etc.

[Brief explanation of the drawing]

The attached drawings, FIGS. 1 to 13, show embodiments of the present invention, in which FIG. 1 is an overall view, FIG. 2 is a view of the heat storage tank including a partially broken surface, and FIG. 3 is a view taken along A-A of FIG. 2. An end view taken along the line, FIG. 4 is a diagram showing an example of the drain removal means, FIG. 5 is a view showing the same example of the drain removal means as in FIG. 4, and a view seen from above the group of small spherical heat storage bodies. is a diagram showing another example of the drain removal means, FIGS. 7 and 8 are views showing still other drain removal means, respectively, and are views seen from above the group of small spherical heat storage bodies, and FIGS. FIG. 13 is an explanatory diagram of the heat storage and heat dissipation modes, respectively, and FIG. 14 is a diagram of a conventional example. In the figure, 1... Evaporator as a heat exchanger on the heat generation equipment side, 2... Pump, 3... Cooler as a heat exchanger on the heat usage equipment side, 7... Heat storage tank, 8... Pipes, 11, 12...
Three-way switching valve, 13... Bypass pipe, 14... Flow rate control valve, 15... Temperature detection position of heat transfer medium, 19... Body, 22, 23... Connection port, 24, 25... Flow diffusion member, 26... Flow port, 29...Small spherical heat storage body, 30...
Heat storage medium, 35... Drain gap, 36... Drain pipe,
37...Opening/closing valve.

Claims (1)

[Scope of Claims] 1. The heat exchanger 1 on the heat generation equipment side, the pump 2, the heat storage tank 7, and the heat exchanger 3 on the heat usage equipment side are sequentially and cyclically connected by a heat transfer medium heat exchanger tube, A three-way control valve 11 is provided between the heat storage tank 7 and the heat exchanger 3 on the heat-using equipment side.
The branch point 9 between the heat exchanger 3 on the heat-using equipment side and the heat exchanger 1 on the heat-generating equipment side is connected by a pipe 8 to the branch point 9 between the heat exchanger 3 on the heat-using equipment side and the heat exchanger 3 on the heat-using equipment side. A three-way control valve 12 is interposed between the branch point 9 and the heat exchanger 1 on the heat generating equipment side and the pump 2 through a pipe 10, and the three-way control valves 11, 12 With the switching operation, there is a heat storage mode in which the heat transfer medium discharged from the heat exchanger 1 on the heat generation equipment side is returned to the heat exchanger 1 on the heat generation equipment side via the heat storage tank 7 by the pump, and the heat exchanger 1 on the heat generation equipment side via the pipe 8. 7 is passed through the heat exchanger 3 on the heat-using equipment side by a pump, and is returned to the heat storage tank 7 via the pipe 10, forming a heat radiation mode.
A bypass pipe 13 connects between the pump 2 and the heat storage tank 7 and a position in front of the heat exchanger 3 on the heat-using equipment side, and a flow rate control valve 14 is installed in the bypass pipe 13. When the actual detected temperature t of the heat transfer medium at the position 15 before entering the equipment side heat exchanger 3 exceeds the control target set temperature T at the same position, the deviation Δt is used as an operation signal, and in the heat radiation mode, The opening degree of the flow rate control valve 14 is controlled so that a part of the heat transfer medium that has exited the heat exchanger 3 on the heat-using equipment side is returned to the heat exchanger on the heat-using equipment via the bypass pipe 13. , and the heat storage tank 7
is configured as a horizontal stationary type, and includes a cylindrical body 19, body lids 20 and 21 attached to both left and right ends thereof, each having connection ports 22 and 23 formed therein,
It consists of flow diffusion members 24 and 25 disposed near both left and right ends of the body 19 facing each of the above connection ports, and a draining means 33 formed below the body 19 which is placed horizontally. The diameter D of the tank 7,
The ratio of the total length L corresponding to the horizontal length is 1:3 to 6
A small spherical heat storage body 29 filled with a heat storage medium 30 is densely housed in the tank interior 28, which is defined within a range of The drain removal means 33 is formed on the lower surface of the body so as not to allow the passage of the small spherical heat storage bodies 29, but to allow the passage of the heat transfer medium in the gaps between the small spherical heat storage bodies 29. A heat storage device using latent heat, comprising a drain pipe 36 including one or more drain gaps 35, and an on-off valve 37 for normally closing the drain pipe 36. 2 The heat generating device is a cold heat generating means, and the heat using device is configured as a cold heat utilization device, and the actual detected temperature of the heat transfer medium passing through the front position 15 of the heat exchanger 3 on the heat using device side is t and the same. Assuming that the set temperature as a position control target is T, and the deviation between t and T is Δt, in the heat radiation mode, if t<T, the flow rate control valve 14 is switched to the heat exchanger 3 on the heat-using equipment side. The opening degree is controlled so that a part of the heat transfer medium that has exited the heat storage tank 7 is returned to the heat exchanger 3 on the heat-using equipment side via the bypass pipe 13, and the flow rate of the heat transfer medium passing through the heat storage tank 7 is proportional to Δt. 2. A heat storage device using latent heat according to claim 1, wherein said latent heat storage device is configured to be adjusted as follows. 3 The heat generating device is a heat generating means, and the heat using device is configured as a heat utilizing device, and the actual detected temperature of the heat transfer medium passing through the front position 15 of the heat exchanger 3 on the heat using device side is t and the same. Assuming that the set temperature as a position control target is T, and the deviation between t and T is Δt, in the heat radiation mode, if t>T, the flow rate control valve 14 is closed to the heat exchanger 3 on the heat-using equipment side.
The opening degree is controlled so that a part of the heat transfer medium coming out of the tank is returned to the heat exchanger 3 on the heat-using equipment side via the bypass pipe 13, and the flow rate of the heat transfer medium passing through the heat storage tank 7 is proportional to Δt. 2. A heat storage device using latent heat according to claim 1, wherein said latent heat storage device is configured to be adjusted as follows. 4 Drain gap 35 of the drain removal means 33
is a single circular hole that opens in the body 19 and is smaller than the diameter d of the small spherical heat storage body 29, and a single circular hole that horizontally crosses the single circular hole so that the small spherical heat storage body 29 does not sit there and block it. A heat storage device using latent heat according to claim 1, characterized in that a plurality of striation members 39 are installed. 5 Drain gap 35 of the drain removal means 33
consists of a plurality of circular holes smaller than the diameter d of the small spherical heat storage bodies 29 that open in the body 19, and each small spherical heat storage body 29 of the small spherical heat storage body group is seated in each of the plurality of small circular holes. 2. A heat storage device using latent heat according to claim 1, wherein the formation pitch p of the small circular holes is set to be smaller than the diameter d of the small spherical heat storage body so as not to block the small circular holes. 6 Drain gap 35 of the drain removal means 33
A heat storage device using latent heat according to claim 1, wherein one or more grooves having a width narrower than the diameter d of the small spherical heat storage body 29 are formed in the body 19. 7 Drain gap 35 of the drain removal means 33
is the diameter d of the small spherical heat storage body 29 that opens into the body.
2. A heat storage device using latent heat according to claim 1, wherein square holes having smaller sides are arranged in a grid pattern. 8 Flow diffusion members 24 and 2 disposed near both left and right ends of the body 19 facing the connection ports 22 and 23
Claim 5 is characterized in that a plurality of flow ports 26 are formed radially in a disc.
A heat storage device using latent heat as described in . 9 In the stationary horizontal cylindrical heat storage tank 7, there are a plurality of small spherical heat storage bodies 29 filled with a heat storage medium whose main liquid is a eutectic mixture of sodium carbonate (Na ₂ CO ₃ ) aqueous solution. A heat storage device utilizing latent heat according to claim 1, characterized in that the device is tightly housed. 10 In the stationary horizontal cylindrical heat storage tank 7,
Claim 1, characterized in that a plurality of small spherical heat storage bodies 29 are closely housed, each of which is filled with a heat storage medium whose main liquid is a eutectic mixture of potassium hydrogen carbonate (KHCO ₃ ) aqueous solution. The latent heat utilization heat storage device according to item 1. 11 Inside the stationary horizontal cylindrical heat storage tank 7,
Claim 1, characterized in that a plurality of small spherical heat storage bodies 29 are closely housed, each of which is filled with a heat storage medium whose main liquid is a eutectic mixture of barium chloride (BaCl ₂ ) aqueous solution. A heat storage device using latent heat as described in . 12 In the stationary horizontal cylindrical heat storage tank 7,
Claim 1, characterized in that a plurality of small spherical heat storage bodies 29 are closely housed, each of which is filled with a heat storage medium whose main liquid is a eutectic mixture of potassium chloride (KCl) aqueous solution. The described latent heat utilization heat storage device. 13 Inside the stationary horizontal cylindrical heat storage tank 7,
Claim 1, characterized in that a plurality of small spherical heat storage bodies 29 are closely housed, each of which is filled with a heat storage medium whose main liquid is a eutectic mixture of ammonium chloride (NH ₄ Cl) aqueous solution. The latent heat utilization heat storage device according to item 1. 14 In the stationary horizontal cylindrical heat storage tank 7,
Claim 1, characterized in that a plurality of small spherical heat storage bodies 29 are closely housed, each of which is filled with a heat storage medium whose main liquid is a eutectic mixture of ammonium nitrate (NH ₄ NO ₃ ) aqueous solution. The latent heat utilization heat storage device according to item 1. 15 In the stationary horizontal cylindrical heat storage tank 7,
Claim 1, characterized in that a plurality of small spherical heat storage bodies 29 are closely housed, each of which is filled with a heat storage medium whose main liquid is a eutectic mixture of sodium nitrate (NaNO ₃ ) aqueous solution. A heat storage device using latent heat as described in . 16 In the stationary horizontal cylindrical heat storage tank 7,
Claim 1, characterized in that a plurality of small spherical heat storage bodies 29 are closely housed, each of which is filled with a heat storage medium whose main liquid is a eutectic mixture of an aqueous sodium chloride (NaCl) solution. The described latent heat utilization heat storage device. 17 In the stationary horizontal cylindrical heat storage tank 7,
Claim 1 characterized in that a plurality of small spherical heat storage bodies 29 are closely housed, each of which is filled with a heat storage medium whose main liquid is a eutectic mixture of an aqueous sodium bromide (NaBr) solution. A heat storage device using latent heat as described in . 18 In the stationary horizontal cylindrical heat storage tank 7,
Claim 1, characterized in that a plurality of small spherical heat storage bodies 29 are closely housed, each of which is filled with a heat storage medium whose main liquid is a eutectic mixture of magnesium chloride (MgCl ₂ ) aqueous solution. A heat storage device using latent heat as described in . 19 In the stationary horizontal cylindrical heat storage tank 7,
Claims characterized in that a plurality of small spherical heat storage bodies 29 are closely housed, each of which is filled with a heat storage medium whose main liquid is a eutectic mixture of potassium carbonate (K ₂ CO ₃ ) aqueous solution. The latent heat utilization heat storage device according to item 1. 20 In the stationary horizontal cylindrical heat storage tank 7,
A small spherical heat storage body 2 filled with a heat storage medium whose main liquid is an aqueous sodium hydroxide (NaOH) solution.
9. A heat storage device utilizing latent heat according to claim 1, wherein a plurality of latent heat storage devices 9 are closely housed. 21 Inside the stationary horizontal cylindrical heat storage tank 7,
It is noted that a plurality of small spherical heat storage bodies 29 are tightly housed, each of which is filled with a heat storage medium whose main liquid is water (H ₂ O) to which a small amount of sulfuric acid (H ₂ SO ₄ ) is added. A heat storage device using latent heat according to claim 1. 22 Magnesium oxide (MgO), magnesium hydroxide (Mg(OH) ₂ ), magnesium carbonate (MgCO ₃ ), magnesium sulfate (MgSO ₄ ), and magnesium chloride are added to the main liquid filled inside the small spherical heat storage body. (MgCl ₂ ), magnesium bromide (MgBr ₂ ), calcium oxide (CaO), calcium hydroxide (Ca(OH) ₂ ), calcium carbonate (CaCO ₃ ),
Calcium sulfate (CaSO ₄ ), copper sulfate (CuSO ₄ ), nickel sulfate (NiSO ₄ ), zinc sulfate (ZnSO ₄ ), strontium hydroxide (Sr(OH) ₂ ), strontium carbonate (SrCO ₃ ), barium hydroxide ( Ba(OH) ₂ ),
Barium oxide (BaO), barium carbonate (BaCO ₃ ),
Sodium sulfate (Na ₂ SO ₄ ), sodium tetraborate (Na ₂ B ₄ O ₇ ), sodium silicate (Na ₂ SiO ₃ ), potassium hydroxide (KOH), potassium nitrate (KNO ₃ ),
Claims 9, 10, 11, 12, and 12 contain a trace amount of at least one nucleating agent selected from nickel chloride (NiCl ₂ ). Section 13, Section 14, Section 15
Section 16, Section 17, Section 18, Section 19,
The latent heat utilization heat storage device according to item 20 or 21.