JP2014066517A - Ice heat storage device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an ice heat storage device which maintains good durability, improves IPF(Ice Packing Factor), and improves heat exchange characteristics.SOLUTION: An ice heat storage device 100 of this invention includes: a heat storage tank 130 in which water and ice are stored; an ice machine 120 which is located at a position higher than a water surface of the heat storage tank and makes block shaped ice; an ice transport pipeline 122 which flows the block shaped ice into water flow at a position higher than the water surface of the heat storage tank 130 and transports the block shaped ice by the water flow from the ice machine 120 to a lower part of the heat storage tank 130; one or multiple heat exchangers 148 which use water as a heat exchange medium and conduct heat exchange with the load side; a first water transport pipeline 140 which transports water from the heat storage tank 130 to the heat exchangers 148; and a second water transport pipeline 150 which returns the water used for the heat exchange from the heat exchangers 148 to the heat storage tank 130.

Description

  The present invention relates to an ice heat storage device, and more particularly, to an ice heat storage device that stores ice and water in a heat storage tank and uses the cold heat for a heat exchanger.

  In recent years, about 1/3 to 1/4 of the energy consumption of offices and buildings is used as a heat source, and most of the heat source demand is cooling demand. Therefore, the introduction of a heat storage device for cooling that can achieve energy saving effect, environmental protection, cost reduction, and disaster prevention safety is progressing.

  Among them, an ice storage device that can store a large amount of cold energy in a space-saving manner has attracted attention. Various types of ice heat storage devices are provided, ranging from small-scale devices intended for retail stores to medium-sized or larger devices used in buildings spanning multiple floors. These ice heat storage devices are roughly classified into a static type and a dynamic type. The static type is further classified into an inner melting type and an outer melting type.

  Patent Document 1 (inner melting type) and Patent Document 2 (outer melting type) disclose typical static type configurations. The static type has an ice making coil inside the heat storage tank, and the ice stored in the heat storage tank is cooled by this ice making coil to make ice. In the inner melting type, ice produced by passing a heat transfer medium (brine) etc. through the coil is defrosted from the inner side (coil contact side), and in the outer melting type, ice making is performed by hot water flowing into the heat storage tank. Thaw the ice from the outside (opposite side of the coil).

  According to the data published by the companies that manufacture static ice storage devices, IPF (Ice Packing Factor) of up to about 90% can be achieved with static internal melting type ice storage devices, It is said that an IPF of up to about 60% can be reached even with a static external melting type ice storage device. In general, the higher the IPF value, the smaller the heat storage tank.

  However, IPF is the amount of ice making relative to the amount of water in the heat storage tank, and this value cannot take into account the volume of the ice making coil installed inside in the static type. In other words, even if they have the same IPF value, the static type cannot reduce the size of the heat storage tank as compared with the dynamic type described later. Furthermore, in the static type, the heat transfer characteristic of the ice making coil decreases with an increase in the IPF, so that good (constant) operating efficiency cannot be maintained. In addition, the ice making coil has difficulty in expanding in the height direction for structural reasons such as strength, and cannot cope with a heat storage tank of a certain scale or more. For this reason, dynamic ice heat storage devices are currently attracting attention.

  Patent Documents 3 and 4 disclose typical dynamic type configurations. There are various types of dynamic types, but the heat storage tank and the ice making section that produces ice (or water) from the sherbet-like ice (or supercooled water) are separated. Is almost the same in that it flows. Even in the dynamic type, the higher the value of IPF, the smaller the heat storage tank can be achieved.

  In Patent Document 3, in order to prevent the sherbet-shaped ice from icing at the opening (spout port) of the heat storage tank while improving the IPF, the antifreeze liquid that is heavier than water and does not dissolve in water is cooled. And the technique of making the water which contacted by conveying this antifreeze liquid to the lower part of a thermal storage tank by a swirl flow is disclosed. On the other hand, in Patent Document 4, in order to effectively use the latent heat of sherbet-like ice (improve heat exchange characteristics), the return water warmed by the heat exchanger is evenly sprinkled from the top of the sherbet-like ice. Technology is disclosed.

  In addition, as in Patent Document 5, a technique in which a static type and a dynamic type are multiplied has been studied. In Patent Document 5, an ice maker is installed in a heat storage tank to generate block-shaped ice, and by improving the detachability of the ice, an ice heat storage device with a simple configuration and a high degree of design freedom is realized. It is supposed to be possible.

JP-A-8-152162 JP-A-10-185250 Japanese Patent Laid-Open No. 6-201162 JP-A-6-300366 JP-A-10-002644

  However, each of the above-described dynamic ice heat storage devices also has problems. For example, in the technique of Patent Document 3, since the antifreeze liquid is used, the ice storage volume of the ice is reduced by the volume occupied by the antifreeze liquid in the heat storage tank. If the volume of this antifreeze liquid is reduced, the water stored in the heat storage tank will approach the opening (spout) of the heat storage tank, and the risk that the opening will freeze will increase. In addition, the use of antifreeze becomes a factor of cost increase. In addition, when antifreeze is used, the antifreeze may leak into the water in the heat storage tank at the time of a disaster, etc., and a thorough sealing structure for the antifreeze path and antifreeze leak detection must be provided. In the first place, sherbet-like ice is difficult to obtain a high IPF because there is almost no compression between the ices. In addition, the sherbet-like ice causes a sintering phenomenon to form a huge ice lump and forms a water supply (water path), and thus has difficulty in de-icing. If the ice melting is not performed smoothly, the heat exchange characteristics are deteriorated.

Moreover, in the technique of patent document 4, when returning water is sprinkled from the upper part of a sherbet-like ice, the air which exists in the upper part of a thermal storage tank is also taken in (air is introduce | transduced into the stored water). . Therefore, there is a possibility that corrosion of equipment (for example, in the case of iron: 2Fe + 2H ₂ O + O ₂ → 2Fe (OH) ₂ ) may be promoted. Therefore, it has a problem in terms of durability.

  Furthermore, in the technique of Patent Document 5, an ice making machine (having an underwater ice making ability) that makes ice in a heat storage tank has not been put into practical use at present. This is because it is not possible to completely control the ice making, and the opening provided in the heat storage tank is frozen to prevent the circulation of water or the like. Therefore, it is practically impossible to adopt the configuration of Patent Document 5. Even if such an ice making machine is put into practical use, it is necessary to install an ice making coil in water, so that the problem of the static type is not solved. Further, even if the above-mentioned Patent Document 3 to Patent Document 5 are combined, each problem cannot be complemented.

  The present invention has been made in view of the above-described problems, and provides an ice heat storage device capable of improving IPF (ice filling rate) and heat exchange characteristics while maintaining good durability. Objective.

  In order to solve the above problems, a typical configuration of an ice heat storage device according to the present invention is a heat storage tank in which water and ice are stored, and is installed at a position higher than the water surface of the heat storage tank. An ice making machine that makes ice, an ice transport pipe that transports block-shaped ice onto the water stream at a position higher than the water surface of the heat storage tank, and transports it from the ice making machine to the lower part of the heat storage tank using gravity, and water from the heat storage tank. A pump that extracts water and transports it to an ice making machine, one or more heat exchangers that use water as a heat exchange medium to exchange heat with the load side, and first water that transports water from the heat storage tank to the heat exchanger It is characterized by comprising a transport pipe and a second water transport pipe for returning the water used for heat exchange from the heat exchanger to the heat storage tank.

  According to such a configuration, in order to use block-shaped ice that is in a state where molecules are compressed compared to sherbet-shaped ice, and that can eliminate the possibility of the occurrence of sintering phenomenon and the formation of waterworks (water), The IPF and heat exchange characteristics can be improved. Further, by installing the ice making machine at a position higher than the water surface and utilizing gravity and water flow, block-shaped ice can be conveyed to the lower part of the heat storage tank against its buoyancy. By introducing the block-shaped ice from the lower part, it is possible to prevent the block-shaped ice from rising above the water surface, which may occur when introduced from above.

  The said ice conveyance piping is good to be installed in the exterior of a thermal storage tank. This is because if the ice transport pipe is installed in the heat storage tank, the capacity of the heat storage tank is reduced and the rise of ice in the heat storage tank may be hindered. That is, according to such a configuration, good controllability can be realized.

  The pipe diameter of the ice transport pipe is preferably 5 times or more the average value of the diameters of the block-shaped ice. According to this configuration, it is possible to prevent the ice transport pipe from being clogged with ice.

  The water flow may be formed as a swirling flow by being injected off the axis of the ice carrying pipe. According to such a configuration, since the ice transported by the water flow is also swirled and sent, it is possible to avoid clogging the ice transport piping. Note that the swirl flow disclosed in Patent Document 3 is for increasing the contact with water and improving the ice making amount of sherbet-like ice, and the meaning differs from the swirl flow here.

  The said ice conveyance piping is arrange | positioned on the same horizontal surface in a thermal storage tank, and it is good to have a some discharge port which distributes block-shaped ice in one thermal storage tank, and discharge | releases. According to such a configuration, ice can be stored substantially evenly with respect to the heat storage tank plane, so that the IPF can be improved.

  The first water transfer pipe has a plurality of water discharge outlets arranged at different heights for extracting water from the heat storage tank, and a path for extracting water from the water outlet closest to the heat exchanger and conveying it to the heat exchanger. The ice storage device can also be used as a water storage device with a route selection valve that selects or selects the route for extracting water from the water outlet located at the bottom of the heat storage tank and transporting it to this heat exchanger It is good to be. According to this configuration, when the cold energy can be supplied without storing ice, it can be operated as a water heat storage device. Therefore, an energy saving effect can be achieved.

  It is preferable to further include a water level measuring unit that measures the water level of the heat storage tank, and a device control unit that estimates the approximate ice filling rate in the heat storage tank from the measured water level and controls the ice heat storage device. According to this configuration, it is possible to optimally operate the ice heat storage device (particularly the ice making machine) in consideration of the ice filling rate. In addition, since block-shaped ice may protrude from the water surface, the estimated value of the ice filling rate is approximate. However, since the water level at the end of ice melting is always constant, it can be an accurate index for switching from operation as an ice heat storage device to operation as a water heat storage device.

  Other typical configurations of the ice heat storage device according to the present invention to solve the above problems are a heat storage tank in which water and ice are stored, an ice maker that ices and supplies the ice to the heat storage tank, One or more heat exchangers that use water as a heat exchange medium to exchange heat with the load side, a first water conveyance pipe that conveys water from the heat storage tank to the heat exchanger, and heat from the heat exchanger to the heat storage tank A second water transfer pipe for returning the water used for the exchange, and the second water transfer pipe supplies the water used for the heat exchange from below the water surface toward the ice that can float above the heat storage tank. It has one or more water discharge ports to discharge.

  With this configuration, the heat exchange characteristics can be improved.

  The first water transport pipe may transport water at a position deeper than a predetermined depth from the water discharge port to the heat exchanger. According to such a configuration, at least when ice remains (IPF> 0%), water at a certain temperature or less can be always supplied to the heat exchanger.

  ADVANTAGE OF THE INVENTION According to this invention, the ice heat storage apparatus which can improve an IPF (ice filling rate) and an improvement of a heat exchange characteristic can be provided, maintaining favorable durability.

It is a figure which shows typically one Embodiment of the ice thermal storage apparatus of this invention. It is a schematic functional block diagram of the ice thermal storage apparatus shown in FIG. It is a figure which shows the discharge port of the ice conveyance piping shown in FIG. It is a figure which shows the water discharge outlet of the 2nd water conveyance piping shown in FIG. It is a figure which shows typically the application example of the ice thermal storage apparatus shown in FIG. It is a figure which shows the verification conditions in water discharge port verification. It is a figure which shows the outline | summary of the experimental apparatus in virtual load verification. It is a figure which shows the verification conditions and result in virtual load verification.

  Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. The dimensions, materials, and other specific numerical values shown in the embodiment are merely examples for facilitating understanding of the invention, and do not limit the present invention unless otherwise specified. In the present specification and drawings, elements having substantially the same function and configuration are denoted by the same reference numerals, and redundant description is omitted, and elements not directly related to the present invention are not illustrated. To do.

  FIG. 1 is a diagram schematically showing an embodiment of the ice heat storage device of the present invention. FIG. 2 is a schematic functional block diagram of the ice heat storage device shown in FIG. The ice heat storage device 100 according to the present embodiment includes a cooling tower 110, a cooling water transfer pipe 112, a brine turbo 114, a brine transfer pipe 116, an ice making machine 120, an ice transfer pipe 122, a heat storage tank 130, an emergency water tap 132, and a water level measurement. A water level gauge 134, a first water transfer pipe 140, a heat exchanger 148, a second water transfer pipe 150, a third water transfer pipe 158, a device control unit 160, and an emergency power generator 162 are included as means. A pump 170 is installed in the cooling water transfer pipe 112, the brine transfer pipe 116, the first water transfer pipe 140, and the third water transfer pipe 158. Hereinafter, each of the above-described elements will be described in order.

  The cooling tower 110 generates cooling water and supplies the cooling heat of the cooling water to the brine turbo 114 through the cooling water transfer pipe 112. The brine turbo 114 transports the supplied cold heat from the brine transport pipe 116 to the ice making machine 120.

  The ice making machine 120 uses the cold heat of the brine conveyed from the brine turbo 114 to make the block-shaped ice 120a. By using the block-shaped ice 120a, it is possible to eliminate the drawbacks of the prior art such as the generation of a sintering phenomenon and the formation of water (the water), and to improve the IPF. In this embodiment, sherbet-like ice is defined as having air permeability (water permeability), and block-shaped ice is defined as having almost no air permeability (water permeability).

  The ice making machine 120 is installed at a position higher than the water surface of the heat storage tank 130. In other words, the heat storage tank 130 is installed at a position higher than its height in consideration of the filling (maximum water level). From this position, the block-shaped ice 120a that has been made into ice is dropped into the ice transport pipe 122 together with water. The ice transfer pipe 122 is connected to the heat storage tank 130, and gravity always acts so that the water surface of the ice transfer pipe 122 and the water surface of the heat storage tank 130 are equal. Therefore, if a water flow of 0.2 m / sec (preferably 1.0 m / sec) or more can be injected into the ice transport pipe 122, the block-shaped ice 120 a can be transported to the lower part of the heat storage tank 130. .

  A swirling flow can be generated by injecting the water flow with the axis of the ice conveying pipe 122 removed. By using the swirl flow, the block-shaped ice 120a can be transported while swirling, and the ice transport pipe 122 can be prevented from being clogged with the block-shaped ice 120a.

  The ice transfer pipe 122 is installed outside the heat storage tank 130 and transfers the block-shaped ice 120a from the ice making machine 120 to the lower part of the heat storage tank 130 by a water flow as described above. This is because when the ice transfer pipe 122 is installed in the heat storage tank 130, the capacity of the heat storage tank 130 is reduced and the rise of the block-shaped ice 120a in the heat storage tank 130 may be hindered. That is, good controllability can be realized by adopting such a configuration. In addition, it is possible to improve maintainability and workability by installing the ice transfer pipe 122 outside.

  The pipe diameter of the ice transfer pipe 122 is set to be five times or more the average value of the diameters of the block-shaped ice 120a. By defining the pipe diameter in this way, the block-shaped ice 120a can be transported without clogging the ice transport pipe 122.

  Normally, the ice immediately after ice making (block-shaped ice 120a) may stick due to refreezing of the surrounding water due to the low temperature. However, in this embodiment, the sensible heat of the ice is treated with water during the transfer of the ice transfer pipe 122 to become ice close to 0 ° C., so re-freezing does not occur, and fluidity is secured even in the heat storage tank 130. It has been demonstrated that

  FIG. 3 is a view showing a discharge port of the ice transport pipe shown in FIG. As shown in FIG. 3, the ice transport pipe 122 has a plurality of outlets 124 a and 124 b arranged on the same horizontal plane, and the block-shaped ice 120 a is distributed almost evenly in the heat storage tank 130 (upward). And release. Thereby, it can prevent that block-shaped ice 120a is unevenly distributed and stored in the heat storage tank 130, and can improve IPF. In the present embodiment, the number of the outlets 124a and 124b is two, but the present invention is not limited to this, and the number of the outlets 124 may be further increased.

  The heat storage tank 130 is a vertical heat storage tank installed along the outer wall of the building, in which water and block-shaped ice 120a are stored. Since this form does not require underground excavation unlike the underground heat storage tank that has been frequently used conventionally, the cost can be reduced and the construction period can be shortened.

  The emergency water tap 132 supplies water stored in the heat storage tank 130 to the outside. That is, the heat storage tank 130 is a community tank that can discharge water stored inside in an emergency as fire-fighting water or emergency-use water through the emergency water tap 132.

The water level meter 134 measures the water level in the heat storage tank 130 by various methods such as using ultrasonic waves and detecting pressure. In general, since the density of water is 1.00 g / cm ³ and the density of ice (block-shaped ice 120a) is 0.92 g / cm ^3, it is assumed that almost all of the water stored in the heat storage tank 130 becomes ice. Then, the water level in the heat storage tank 130 will increase by about 10%. Therefore, if the amount of water in the heat storage tank 130 is constant, the IPF at that time can be estimated by measuring the water level. In the present embodiment, the measurement value of the water level gauge 134 is sent to the device control unit 160 as needed.

  The first water transfer pipe 140 includes a plurality of drain outlets 142 that are arranged at different heights for extracting water from the heat storage tank 130 and a path selection valve 144 that selects a path for transporting water to the heat exchanger 148. And water is transferred from the heat storage tank 130 to the heat exchanger 148. The route selection valve 144 is controlled by the device controller 160 described later.

  As a preferred example, when the ice in the heat storage tank 130 remains, the path selection valve 144 selects the transport path closest to the target heat exchanger 148 when transporting water to the heat exchanger 148. That is, the water extracted from the nearest water outlet 142 is conveyed to the target heat exchanger 148. This is because, when ice remains, the same cooling effect can be obtained even if water is extracted from any part of the heat storage tank 130 and conveyed. Thereby, the load applied to the pump 170 can be reduced.

  In addition, when deicing, the path selection valve 144 extracts water from the water outlet 142 located at the lower part of the heat storage tank 130 and transports the water to the target heat exchanger 148 when conveying water to the heat exchanger 148. Is selected. This is because water having a temperature of 4 ° C. or higher (required as a water temperature to be transported to the heat exchanger 148 is 7 ° C. or lower) has a higher specific gravity as it is cooled and tends to stay downward. In addition, it is because the water heated by the heat exchanger 148 mentioned later is discharge | released to upper part. That is, according to such a configuration, cold water can be conveyed to the target heat exchanger 148.

  In addition, when excessive cooling is not required (for example, cooling used in an environment having a small difference in temperature), the water from the lower part of the heat storage tank 130 described above can be stored without storing the block-shaped ice 120a in the heat storage tank 130. Can be handled by extracting. More specifically, the cooling of the ice making machine 120 can be reduced to such an extent that it does not require ice making. In other words, it can be operated as a water heat storage device, and an energy saving effect can be achieved by improving the efficiency of the brine turbo 114.

  The heat exchanger 148 uses the water conveyed from the heat storage tank 130 as a heat exchange medium, and performs heat exchange with the load side. As the load side, for example, an air conditioner (AHU: Air Handling Unit) that performs air conditioning can be connected.

  The second water conveyance pipe 150 returns the water used for heat exchange from the heat exchanger 148 to the heat storage tank 130. Specifically, water is returned into the heat storage tank 130 from a water discharge port 152 formed near the tip. In addition, since the water utilized for heat exchange is warmed, specific gravity is small and can raise preferentially.

  FIG. 4 is a view showing a water discharge port of the second water conveyance pipe shown in FIG. As shown in FIG. 4, the water discharge port 152 is disposed below the water surface of the heat storage tank 130, and discharges water used for heat exchange toward the block-shaped ice 120 a floating above. Thereby, since the water used for heat exchange can exchange heat with the block-shaped ice 120a with high efficiency, the heat exchange characteristics can be improved. Further, since water is discharged from below the surface of the water, air is not involved and the risk of accelerating the corrosion of the device is eliminated. Preferably, the water discharge port 152 is disposed at a position about 10 cm below the water surface at the end of the deicing (at the time of complete deicing) when the water level is the lowest.

  The third water conveyance pipe 158 extracts water required for making the block-shaped ice 120 a from the heat storage tank 130 and conveys it to the ice making machine 120. The extraction position of the third water conveyance pipe 158 is arranged near the ice making machine 120, and the load of the installed pump 170 is reduced. At this time, since the ice making machine 120 is installed at a position higher than the water surface, the third water transfer pipe 158 is arranged near the water surface, but the low temperature water in the region filled with the ice 120a is extracted. By using it for ice making, the ice making speed can be improved.

  The device control unit 160 is a computer system that includes a central processing unit (CPU), and controls the ice heat storage device 100 as a whole. Specifically, the IPF is estimated from the measured value sent from the water level gauge 134 and the operation of the ice making machine 120 is adjusted, or the water is circulated through each pipe by the control of the path selection valve 144 and the pump 170. To do.

  For the device control unit 160, for example, an existing BEMS (Building Energy Management System) can be used. That is, the ice heat storage device 100 has an advantage that the same design as that of a normal ice heat storage device can be applied.

  The emergency power generator 162 supplies electricity to a predetermined electrical device connected at the time of a power failure or the like. Since the ice making of the ice making machine 120 is generally performed at a time when the electricity charge at night is low, ice can be obtained simply by supplying electricity from the emergency power generator 162 to a minimum power source such as the pump 170. The heat storage device 100 can operate.

  As an effect brought about by the emergency power generator 162, for example, maintenance of air conditioning to the server room at the time of a power failure can be mentioned. When the air conditioning is stopped in the server room, the temperature in the room can reach 60 ° C. to 70 ° C. in a few minutes. According to the ice heat storage device 100 of the present embodiment, air conditioning can be continued even during a power failure, so that time for backing up information can be earned. That is, business continuity can be improved.

  The pump 170 applies pressure to the fluid and sends it out by various methods. In the present embodiment, the pump 170 is controlled by the device control unit 160.

  In the present embodiment, the pump 170 is assigned to each heat exchanger 148 and installed. Therefore, for example, when each heat exchanger 148 is installed on each floor of a tenant building or the like, it is possible to easily cope with business types with different work systems. Therefore, it can contribute to improving the quality of the building itself.

  In addition, since the amount of cold usage on each floor can be divided, billing can be made for each tenant. Since the amount of electric power of the primary pump 170 that has been shared in the past can also be maintained at each floor, it can be handled in the same way as small-scale district heating and cooling. Therefore, clear billing is possible.

In addition, since the amount of cold energy used in each floor can be determined, it is possible to collect information that contributes to energy conservation diagnosis of buildings that can be implemented to comply with the revised Energy Conservation Law. This information can be used as accurate information even when it is required to grasp the CO ₂ emission amount for each business operator in the future.

  The ice heat storage device 100 according to the present embodiment is configured by the elements described above. One of the features of this configuration is that the block-shaped ice 120a cannot be introduced from above the heat storage tank 130. More specifically, when a certain amount or more of block-shaped ice 120a is introduced from above, the ice rises beyond the water surface, and the ice exposed to the air can form ice blocks due to a sintering phenomenon. The rise from the water surface reaches about 10% of the introduced ice, and this effect becomes more prominent as the heat storage tank 130 becomes larger and the introduction amount of the block-shaped ice 120a increases. Even if an attempt is made to push the raised portion by pressing, the block-shaped ice 120a is harder than the sherbet-like ice, and this ice is arranged densely, so that it is difficult to push it. Ice above the surface of the water is unlikely to contribute to cooling of the water, leading to a decrease in the function as ice heat storage.

  That is, as a result of intensive studies, the present inventors have proposed a gravitational force as described above as a method capable of suitably storing (conveying) block-shaped ice 120a in order to solve problems that can be contained in sherbet-shaped ice. And the composition using water flow was found. The block-shaped ice 120a has a relatively high buoyancy and thus has difficulty in transporting in the depth direction, but this configuration can solve the problem. On the other hand, even if the ice making machine 120 is disposed at a position lower than the water surface of the heat storage tank 130 and the block-shaped ice 120a is pulled by the pump without following the present invention, the power only increases. Further, in this case, if the scale of the heat storage tank 130 is a certain level or more, the pump itself that can pull the block-shaped ice 120a is limited. Therefore, the technical contribution of the ice heat storage device 100 according to the present embodiment is clear, and the effects that can be achieved with the following application examples are further leap forward.

  FIG. 5 is a diagram schematically showing an application example of the ice heat storage device shown in FIG. 1. The difference between the ice heat storage device 200 shown in FIG. 5 and the above-described configuration (ice heat storage device 100) is that it further includes a heat storage tank 230 (a heat exchanger 148 and the like are connected similarly to the heat storage tank 130). .

  Specifically, the block-shaped ice 120 a made by the ice making machine 120 is transported by the ice transport pipe 122 branched to the two heat storage tanks 130 and 230. The heat storage tanks 130 and 230 of the transfer destination are selected by a path selection valve 144 attached to the ice transfer pipe 122. Then, the water level adjustment pipe 232 adjusts the water level fluctuation accompanying the conveyance of the block-shaped ice 120a.

  In other words, the ice heat storage device 200 that can supply cold heat (block-shaped ice 120a) from one ice making machine 120 or the like to the plurality of heat storage tanks 130 and 230 that are located apart by the above configuration is possible. It becomes.

  Hereinafter, in order to promote understanding of the present invention, examples will be shown and described in more detail.

(Verify water outlet)
As a method of positively exposing the water warmed by the heat exchanger 148 to the block-shaped ice 120a accumulated on the upper part of the heat storage tank 130, an examination focusing on the shape of the water discharge port 152 was performed.

  FIG. 6 is a diagram illustrating verification conditions in water discharge port verification. As shown in FIG. 6, a total of seven examples of Comparative Example 1 and Examples 1 to 6 in which different conditions were set for the number, position, diameter, and water discharge direction of the water discharge ports were examined. As Comparative Example 1, unlike the water discharge port 152 described above, a water discharge port 153 that discharges water in the horizontal direction is employed.

In the experiment, a 0.04 m ³ (W450 × D300 × H300 mm) water tank 330 was used, and about 13 ° C. tap water was discharged from the water discharge ports 152 and 153 as a pseudo load. In the examination, the time until the ice in the water tank 330 was completely melted (dissipation of heat) was measured to find a condition for increasing the direct heat exchange rate between ice and water. Hereinafter, water extracted from the water tanks 330 and 430 is referred to as outgoing water, and water introduced to the water tanks 330 and 430 is referred to as ring water.

  As a result of the study, it was confirmed that in Examples 1 to 6 in which the return water was discharged upward (toward the ice that can float upward), complete defrosting was confirmed to be faster by about 1 minute than in Comparative Example 1 in which it was discharged horizontally. It was. That is, it was confirmed that the water discharge direction is preferably upward. Further, in Example 2 with a diameter of 25A (PVC pipe standard), it was confirmed that it is desirable that the diameter is large because the ice-melting time is earlier than in Example 1 with a diameter of 13A. In addition, the fourth example in which the water discharge port 152 is located in the center of the water tank has a faster ice-melting time than the third example in which the water discharge port 152 is close to the discharge side, and the fifth example has four water discharge ports 152. In Example 6, in which the number of water discharge ports 152 is six, the ice melting time is faster, so the return water is evenly exposed to the ice in the water tank, and the number of water discharge ports 152 is increased to slow the discharge speed. It was confirmed that it was advantageous in terms of the ice melting speed.

(Virtual load verification)
For the purpose of confirming stability against load fluctuation and peak load assuming actual work, an experiment was conducted using the water discharge port 152 (disposed at a water depth of 100 mm) of Example 6 above.

  FIG. 7 is a diagram showing an outline of an experimental device in virtual load verification. The experimental apparatus 400 employs a system in which heat is exchanged between the hot water from the boiler 448 and the outgoing water from the heat storage tank 130 by the heat exchanger 148 in order to simulate the actual working load. The block-shaped ice 120a used was W28 × D28 × H30 mm. The return water temperature is set to 13 ° C. by exchanging heat between 0 ° C. to 7 ° C. extracted from the water tank 430 and 70 ° C. to 80 ° C. hot water produced by the boiler 448 in the heat exchanger 148. Adjusted. Further, a plurality of loggers 454 were arranged in each return water pipe and in the outgoing water pipe, and the temperature was measured.

  FIG. 8 is a diagram illustrating verification conditions and results in virtual load verification. The de-icing process of the ice stored in the water tank 430 was examined under the conditions of Cases 1 to 5 shown in FIG. That is, cases 1 to 3 were verified as steady loads, and cases 4 and 5 were verified as unsteady loads. In addition, as a result of comparing the case 1 that started the experiment from the IPF close to full storage and the case 2 that started from a low IPF state (about 13%), it was confirmed that the ice melting process was almost the same. Experiments 2 to 5 were experiments from an initial IPF of 13%.

  FIG. 8B shows the verification result of the steady load, and FIG. 8C shows the verification result of the unsteady load. As a result of the experiment, it was confirmed that when the IPF was 5% or less in all cases, the temperature of the incoming water taken at a water depth of 750 mm at the end of heat radiation was around 7 ° C or higher than 7 ° C. However, it was confirmed that the water at the water depth of 1650 mm and the water depth of 2550 mm was maintained at 7 ° C. or lower until the end of heat dissipation. From this, it was confirmed that it was possible to secure a water flow of 7 ° C. or less until the end of heat dissipation by lowering the water intake position, which is the highest position, to about 1650 mm (a position deeper than a predetermined depth) from the water surface (water discharge port). . Furthermore, no abnormalities in the water temperature were confirmed even during unsteady loads, and it was proved that such a configuration can be applied to actual operation.

  As mentioned above, although preferred embodiment and the Example of this invention were described in detail, it cannot be overemphasized that this invention is not limited to the embodiment and the example which concern. It will be apparent to those skilled in the art that various changes and modifications can be made within the scope of the claims, and these are naturally within the technical scope of the present invention. Understood.

  According to the configuration described above, an IPF of up to about 50% can be realized with 2.5 cm square block-shaped ice 120a, and a maximum of about 80% with small block-shaped ice 120a.

  INDUSTRIAL APPLICATION This invention can be utilized for the ice thermal storage apparatus which stores ice and water in a thermal storage tank, and utilizes the cold heat for a heat exchanger.

DESCRIPTION OF SYMBOLS 100, 200, 300 ... Ice thermal storage apparatus, 110 ... Cooling tower, 112 ... Cooling water carrying piping, 114 brine turbo, 116 ... Brine conveyance piping, 120 ... Ice making machine, 120a ... Block-shaped ice, 122 ... Ice conveyance piping, DESCRIPTION OF SYMBOLS 124 ... Discharge port, 130, 230 ... Thermal storage tank, 132 ... Emergency faucet, 134 ... Water level meter, 140 ... First water conveyance piping, 142 ... Drain outlet, 144 ... Path selection valve, 148 ... Heat exchanger, 150 ... Second water transfer pipe, 152, 153 ... Water discharge port, 158 ... Third water transfer pipe, 160 ... Device control unit, 162 ... Emergency power generator, 170 ... Pump, 232 ... Water level adjustment pipe, 330, 430 ... Water tank , 400 ... Experimental equipment, 448 ... Boiler, 454 ... Logger

Claims (6)

A heat storage tank in which water and ice are stored;
An ice making machine that is installed at a position higher than the water surface of the heat storage tank and makes block-shaped ice;
An ice carrying pipe for carrying the block-shaped ice on a water stream at a position higher than the water surface of the heat storage tank and carrying the gravity from the ice maker to the lower part of the heat storage tank using a water flow;
A pump for extracting water from the heat storage tank and transporting it to the ice making machine;
One or more heat exchangers that use water as a heat exchange medium and exchange heat with the load side;
A first water transfer pipe for transferring water from the heat storage tank to the heat exchanger;
A second water transfer pipe for returning the water used for the heat exchange from the heat exchanger to the heat storage tank;
An ice heat storage device comprising:   The ice heat storage device according to claim 1, wherein the ice transfer pipe is installed outside the heat storage tank.   The ice heat storage device according to claim 1, wherein a pipe diameter of the ice transport pipe is five times or more an average value of a diameter of the block-shaped ice.   The ice transport pipe is disposed on the same horizontal plane in the heat storage tank, and has a plurality of outlets for distributing and discharging the block-shaped ice in one heat storage tank. The ice heat storage device according to 1. A plurality of water outlets arranged at different heights for extracting water from the heat storage tank;
Select a route for extracting water from the drain outlet that is closest to the heat exchanger and transporting it to the heat exchanger, or extracting water from the drain outlet located at the bottom of the heat storage tank and transporting it to the heat exchanger A route selection valve for selecting a route to be
The ice heat storage device according to claim 1, wherein the ice heat storage device can also be used as a water heat storage device. Water level measuring means for measuring the water level of the heat storage tank;
The ice heat storage device according to claim 1, further comprising: a device control unit that estimates an approximate ice filling rate in the heat storage tank from the measured water level and controls the ice heat storage device. .

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