JPWO2020145106A1 - Steam supply and drying system - Google Patents

Abstract

The steam supply device (1) of the present disclosure is a supply medium using a solar concentrating heat collecting unit (2) that collects and collects sunlight and directly heats a heat storage agent (X1), and a heated heat storage agent. A medium heating unit (3) for heating (Z1) and a steam supply unit (4) for separating and supplying steam from the heated supply medium are provided.

Description

The present disclosure relates to steam supply equipment and drying systems.
The present application claims priority based on Japanese Patent Application No. 2019-000689 filed in Japan on January 7, 2019, the contents of which are incorporated herein by reference.

In recent years, the use of renewable energy has been expanded in order to suppress the emission of carbon dioxide and nitrogen oxides, and the use of sunlight as a heat source is also attracting attention as one of them. For example, Patent Document 1 discloses a drying system in which steam is generated using the heat energy obtained by condensing sunlight as a heat source, and the high-humidity solid fuel is dried by the generated steam.

Japanese Patent Application Laid-Open No. 2016-099099

In the steam supply system described in Patent Document 1, steam is directly generated by the thermal energy obtained by condensing sunlight. However, the time required to obtain sufficient heat for steam generation from sunlight is limited, and depending on the weather, the amount of heat may be insufficient throughout the day. Therefore, in the steam supply system described above, it is difficult to stably supply steam.

The present disclosure has been made in view of the above-mentioned problems, and an object of the present disclosure is to stably supply steam in a steam supply device that collects sunlight and uses it as a heat source.

The steam supply device of one aspect of the present disclosure includes a sunlight condensing heat collecting unit that collects heat by condensing sunlight and directly heats a heat storage agent, and medium heating that heats a supply medium by the heated heat storage agent. A unit and a steam supply unit that separates and supplies steam from the heated supply medium are provided.

In the steam supply device of the above aspect, the steam supply device is provided in front of the medium heating unit, and stores the heat storage agent heated by the solar concentrating heat collecting unit, and the medium heating unit. A recovery heat storage agent storage unit which is provided after the unit and stores the heat storage agent used for heating the supply medium may be further provided.

In the steam supply device of the above aspect, the steam supply device stops the supply of the heat storage agent to the solar concentrating heat storage unit and the solar condensing heat collection unit during the time when sunshine cannot be obtained. A heat storage agent evacuation mechanism for retracting the heat storage agent staying in the unit to the supply heat storage agent storage unit or the recovery heat storage agent storage unit may be further provided.

In the steam supply device of the above aspect, the steam supply device has a second solar concentrating heat collecting unit that collects and collects sunlight and directly heats a second heat storage agent, and the heated first. A steam heating unit that further heats the steam supplied from the steam supply unit by the heat storage agent of 2 may be further provided.

In the steam supply device of the above aspect, the steam supplied by the steam heating unit may be superheated steam.

In the steam supply device of the above aspect, the operating temperature of the second heat storage agent may be higher than the operating temperature of the heat storage agent used for heating the supply medium.

In the steam supply device of the above aspect, the second heat storage agent used for heating the steam supplied from the steam supply unit in the steam heating unit may be used for heating the supply medium.

In the steam supply device of the above aspect, the steam supply device may further include an auxiliary boiler for heating the supply medium.

In the steam supply device of the above aspect, the steam supply device may further include an auxiliary superheater for heating the steam supplied from the steam supply unit.

In the steam supply device of the above aspect, the heat storage agent storage tank for storing the heat storage agent may be provided with a stirring device for stirring the heat storage agent.

The drying system of one aspect of the present disclosure includes the steam supply device and a fluidized bed drying device that uses the steam supplied from the steam supply device as a heat source and dries the high-humidity raw material while flowing it.

According to the present disclosure, the steam supply device heats the supply medium through the heat storage agent to generate steam while storing the heat energy obtained from sunlight in the heat storage agent. As a result, it is possible to generate steam by the heat energy stored in the heat storage agent even at night when the supply of heat energy obtained from sunlight is insufficient or when the weather is bad. In addition, fluctuations in the amount of heat collection due to temporal changes in sunshine are once leveled by being stored in the heat storage agent, and the supply medium can be heated under certain conditions, and as a result, steam can be stably supplied. ..

In the present disclosure, the heat storage agent is directly heated by the heat energy obtained by condensing sunlight, and moved to another heat exchange unit to heat the supply medium. As a result, the heat loss that occurs during heat transfer can be reduced as compared with the case where the heat energy obtained by condensing sunlight is transferred to the heat storage agent via another medium. Further, when the thermal energy obtained by condensing sunlight is transferred to the heat storage agent through another medium, there are restrictions on heat transfer, for example, restrictions on the temperature range that can be dealt with, which arise from the physical characteristics of the other medium. Can be eliminated. Therefore, the performance and operating range of the heat storage agent can be expanded.

It is a schematic diagram which shows the structure of the steam supply apparatus which concerns on 1st Embodiment of this disclosure. It is a perspective view of the condensing heat collector used in this disclosure. It is sectional drawing of the condensing heat collector used in this disclosure. It is a figure which shows the arrangement example of the solar condensing heat collecting part of this disclosure. It is a phase change characteristic diagram with respect to the composition and temperature of the heat storage agent used in this disclosure. It is a schematic diagram which shows the structure of the steam supply apparatus which concerns on 2nd Embodiment of this disclosure. It is a schematic diagram which shows the operation of the steam supply device which concerns on 2nd Embodiment of this disclosure in the daylight hours. It is a schematic diagram which shows the operation at the time of sunset of the steam supply device which concerns on 2nd Embodiment of this disclosure. It is a schematic diagram which shows the operation of the steam supply device which concerns on 2nd Embodiment of this disclosure at night. It is a schematic diagram which shows the structure of the steam supply apparatus which concerns on 3rd Embodiment of this disclosure. It is a schematic diagram which shows the structure of the steam supply apparatus which concerns on 4th Embodiment of this disclosure. It is a figure explaining the proper use of the working area of a heat storage agent in the 4th Embodiment of this disclosure. It is a schematic diagram which shows the structure of the drying system which concerns on 5th Embodiment of this disclosure.

[First Embodiment]
Hereinafter, the first embodiment of the steam supply device according to the present disclosure will be described with reference to the drawings.

The steam supply device 1 according to the present embodiment heats and supplies the supply medium Z1 to the application destination (supply destination). The supply medium Z1 is, for example, a fluid pressurized with respect to atmospheric pressure, and when heated, a part of the supply medium Z1 becomes steam. The steam is separated from the heated supply medium Z1 and supplied to the application destination as the steam medium Z1s. As shown in FIG. 1, the steam supply device 1 includes a sunlight condensing heat collecting unit 2, a medium heating unit 3, a steam supply unit 4, and a medium circulation unit 5.

The solar concentrating heat collecting unit 2 is a condensing heat collecting device 2a that efficiently condenses sunlight and collects heat energy, and a heat storage agent circulation for circulating the heat storage agent X1 in the condensing heat collecting device 2a. A piping system for circulating the heat storage agent X1 with the medium heating unit 3 including the pump 2b is provided. The configuration and operation of the condensing heat collector 2a will be described below with an example.

When sunlight is condensed by a lens or the like, the surface of an object placed near the focal point of the condensed light becomes hot, and for example, paper ignites. The same is true if a concave mirror is used instead of the lens, and a large amount of thermal energy can be obtained near the focal point. The device that condenses sunlight and heats the object to be heated is an application of the above phenomenon. By reflecting sunlight and placing the object to be heated near the focal point of the reflected light, the object to be heated is simply made. Compared to a heater that is only exposed to sunlight, it can be heated to a high temperature in a much shorter time.

Various devices have been proposed that condense sunlight and heat the fluid with the condensed sunlight. A device that guides the object to be heated to a straight pipe (heat transfer tube) and heats the heat transfer tube with the focused sunlight as a shape suitable for continuously heating the fluid with condensed sunlight. Proposed. Specifically, the reflector is made semi-cylindrical, and sunlight is reflected on the concave side of the semi-cylindrical reflector. The heat transfer tube is arranged parallel to the reflector so that the reflected light is focused in a straight line in the vicinity of the heat transfer tube. The actual curved surface shape is a shape close to an ellipse, and the curved surface shape is such that the reflected light gathers in a substantially straight line.
The object to be heated is heated while passing through the heat transfer tube. Considering the time required for heating, the heat transfer tube needs to have a certain length, and the reflector is generally in a horizontally long shape parallel to the heat transfer tube. An example of the condensing heat collector will be shown below, and the specific configuration and operation will be described below, but the condensing heat collector actually manufactured is not limited to the example shown below.

2A and 2B show a device used to collect sunlight and heat a fluid flowing through a pipe. In the following description, the name "condensing heat collector" will be used.
As shown in FIG. 2B, the condensing heat collector 200 is roughly divided into a condensing heating unit 210 and a support device 220. As shown in FIGS. 2A and 2B, the condensing heating unit 210 collects the condensing portion of sunlight having the main condensing mirror 211, the sub condensing mirror 212, and the connection fitting 213, and the condensing sunlight. A fluid heating tube 214 provided on a straight line is provided. The support device 220 not only has a role of supporting the condensing and heating unit 210, but also has a function of adjusting an azimuth angle (horizontal angle) and an elevation angle (vertical angle) so that sunlight can be reflected and condensed as much as possible. Have.

The configuration and function of the condensing heating unit 210 will be described.
The main condensing mirror 211 is a reflecting mirror having a semi-elliptical cross section by bending a flat plate, and has a concave curved surface shape so that the reflected light is collected in a straight line parallel to the reflecting mirror. As the material of the main condenser mirror 211, metal is often used in consideration of the reflectance of sunlight and the durability as a structure. However, when metal is used as the material of the main condensing mirror 211, the temperature of the main condensing mirror 211 rises due to exposure to the sun for a long time, and there is a possibility that the shape of the concave surface is distorted due to thermal expansion. Therefore, although not shown in the figure, a cooling mechanism may be provided in the main condenser mirror 211.

By arranging the fluid heating tube 214 on a straight line that is the focal point of the main condensing mirror 211, the fluid flowing through the fluid heating tube 214 is heated. The sub-condensing mirror 212 may be provided in consideration of the efficiency and stability of heating the fluid. In this embodiment, the sub-condensing mirror 212 is arranged so as to face the main condensing mirror 211 with the fluid heating tube 214 interposed therebetween.

The main condensing mirror 211 has a concave shape so that sunlight collects on a straight line. However, due to the manufacturing accuracy, the points where the reflected light gathers do not always match between the vicinity of the center line of the main condensing mirror 211 and the portions near both ends, and the reflected light does not concentrate on the surface of the fluid heating tube 214. In some cases. Further, the condensed sunlight hits only the surface of the fluid heating tube 214 on the main condenser mirror 211 side, and the opposite side of the fluid heating tube 214 is not exposed to the direct light of the sun, so that the surface of the fluid heating tube 214 The heat energy that reaches is different between the main condenser mirror 211 side and the opposite side, and a temperature difference may occur.

The sub-condensing mirror 212 is installed facing the main condensing mirror 211, and the reflecting surface is a semi-cylindrical-shaped reflecting mirror having a concave mirror surface like the main condensing mirror 211. The sub-condensing mirror 212 reflects the sunlight collected by the main condensing mirror 211 and passing through without hitting the fluid heating tube 214 to the fluid heating tube 214 side again, and focuses on the fluid heating tube 214. Will be placed. At this time, by arranging the fluid heating tube 214 at a position slightly closer to the focal point of the main condensing mirror 211, the amount of sunlight passing around the fluid heating tube 214 and reaching the sub condensing mirror 212. To make the heat energy reaching each of the surface of the fluid heating tube 214 on the main condensing mirror 211 side and the surface of the sub condensing mirror 212 side equal. As a result, the heating efficiency can be improved, and the occurrence of strain due to the temperature difference of the fluid heating pipe 214 itself can be suppressed.

Since the sub-condensing mirror 212 and the fluid heating tube 214 are installed at a certain interval from the main condensing mirror 211, they are connected to the main condensing mirror 211 by a connecting metal fitting 213 so as to maintain the interval. It is fixed.

The sub-condensing mirror 212 may be omitted. In that case, it is necessary to arrange the fluid heating tube 214 at a position where the sunlight focused by the main condensing mirror 211 just gathers, and to prevent the occurrence of a temperature difference on the surface of the fluid heating tube 214. However, the description here is omitted.

The support device 220 fixes the condensing heat collector 200 on the ground, and has a role of supporting the condensing heating unit 210. The support device 220 also has a role of adjusting the direction of the condensing heating unit 210 so that the sunlight is incident at right angles to the center line of the main condensing mirror 211 in order to efficiently condense the sunlight. There is. The support device 220 includes a main pillar 221 that fixes the condensing heating unit 210 at a constant height from the ground, an azimuth angle adjusting device 222 that adjusts an azimuth angle (horizontal angle) according to the direction of the sun, and the sun. It has an elevation angle adjusting device 223 that adjusts an elevation angle (vertical angle) according to an altitude. The azimuth adjusting device 222 and the elevation angle adjusting device 223 are generally program-controlled so as to follow the direction of the sun according to the season and the time of day.

Since the condensing heat collector 200 has a movable structure, there is a limit to the size of each unit. Therefore, since there are restrictions on the thermal energy obtained by condensing sunlight, generally, the required thermal energy is secured by arranging a plurality of condensing heat collectors 200.

FIG. 3 shows an arrangement example of the condensing heat collector 200. A sunny and almost flat land is maintained as a condensing heat collecting zone 230, and a plurality of condensing heat collecting devices 200 are arranged in the condensing heat collecting zone 230 so as not to block sunlight from each other. The area of the condensing heat collecting zone 230 depends on the total amount of heat energy to be collected, but for industrial applications, an area of at least several hundred square meters, several thousand square meters, or more is required. In order to collect the heat energy collected by the condensing heat collector 200 in such a vast land and use it in the heat utilization facility 231, each condensing heat collection arranged in the heat utilization facility 231 and the condensing heat collection zone 230. A pipe is laid between the vessel 200 and a fluid for carrying heat is circulated through the pipe to collect heat energy.

The arrangement of the condensing heat collecting zone 230 and the heat utilization facility 231 in FIG. 3 is basic, and is optimally arranged depending on the scale of the heat energy to be collected, the shape of the land of the condensing heat collecting zone 230, and the like. Can be selected.

Next, regarding the heat storage agent used in the present embodiment, the characteristics and the mechanism for storing heat energy will be described. The heat storage agent is, for example, a mixture containing nitrate of an alkali metal element, specifically sodium nitrate (NaNO ₃ ), and has a temperature range in which a solid-liquid phase change occurs in the range of 150 ° C to 400 ° C. It is a mixed salt to be used. Further, the heat energy stored by the heat storage agent includes latent heat corresponding to the phase change between the solid and the liquid, and sensible heat corresponding to the temperature change of the heat storage agent.

An example of the temperature characteristics of the heat storage agent is shown in FIG. 4. There are a region in which all the heat storage agents are present in the liquid phase, a region in which the liquid phase and the solid phase coexist, and a region in which all the heat storage agents are present in the solid phase. The composition and temperature range of the heat storage agent actually used for heat storage are selected so that a liquid phase exists, the heat storage agent has a certain degree of fluidity, and the amount of heat that can be stored can be secured as much as possible.

The example of FIG. 4 is _{a system in which a mixed salt of sodium nitrate (NaNO 3} ) and potassium nitrate (KNO ₃ ) is used as a heat storage agent, and the mixing ratio shown on the horizontal axis is as shown by the curve in the figure. Indicates that the temperature at which the phase change occurs changes. As a range that satisfies the conditions suitable for the heat storage agent, in FIG. 4, _{a composition having a molar fraction of sodium nitrate (NaNO 3} ) of 0.786 was selected, and the temperature of the heat storage agent was changed in this composition. The temperature range to be used is selected in consideration of the phase change. In order to store as much heat energy as possible in the heat storage agent and ensure a stable vapor supply, the upper limit of the operating temperature (Tmax) must be in the region where the heat storage agent is all liquid, and the lower limit of the operating temperature (Tmin). ), The heat storage agent partially becomes a solid phase, but it must be in a region where a certain amount of fluidity can be secured because it becomes a slurry due to the presence of a certain amount of liquid phase. As the proportion of the solid phase in the heat storage agent increases, the viscosity increases and the fluidity is lost. Therefore, the composition of the heat storage agent and the temperature range to be used should be set within a range that does not interfere with the transfer of heat energy. ..

The specific operation will be described by limiting the composition of the mixed salt and the temperature range used. The broken line in the figure indicates a mixed salt having a molar fraction of sodium nitrate of 0.786, and Tmax was 400 ° C. and Tmin was 250 ° C. At 400 ° C., all heat storage agents are in the range present in the liquid phase. When the heat storage agent comes into contact with the object to be heated and gives the stored heat to the object to be heated, the heat storage agent releases sensible heat and the temperature gradually decreases.

When the temperature of the heat storage agent gradually decreases _{and reaches 274 ° C (this temperature is TL} ), the heat storage agent, which was all in the liquid phase until then, changes, and some of the components of the heat storage agent are solid phase. Begins to change to. A part of the heat storage agent, which was all in the liquid phase, releases latent heat and changes to the solid phase, so that the solid phase and the liquid phase coexist in the heat storage agent. In the case of a pure substance, when it reaches the solidification temperature, the solidification proceeds while maintaining the same temperature. When the heat storage agent is a mixed salt, the ratio of the solid phase in the heat storage agent increases as the temperature of the heat storage agent decreases within a certain temperature range. The temperature of the heat storage agent slowly drops from 274 ° C. while releasing latent heat with the phase change. During that time, the change from the liquid phase to the solid phase progresses in the heat storage agent, and the proportion of the solid phase in the heat storage agent increases. While maintaining the fluidity, the release of thermal energy and the decrease in the temperature of the heat storage agent proceed.

When the temperature of the heat storage agent is 274 ° C. or lower, the temperature of the heat storage agent changes very slowly as compared with the temperature change from 400 ° C. to 274 ° C. At this time, the proportion of the solid phase increases inside the heat storage agent. Temperature of the heat storage agent is 234 ° C. (hereinafter, this temperature is T _S) when it reaches, the heat storage agent is completely turned solid. When the heat storage agent is completely in the solid phase, the fluidity is lost and heat transfer becomes difficult, which is not preferable. In order to smoothly store heat and dissipate heat, Tmin should be set to a temperature with a certain margin with respect to the temperature at which the fluidity of the heat storage agent can be secured at the minimum.

In actual operation, the composition of the heat storage agent and the operating temperature range should be set according to the conditions of the steam to be supplied, and the specific operation is limited to the composition of the mixed salt, the upper limit temperature, and the lower limit temperature described above. is not it.

Further, in the example of FIG. 4, from Tmax to the temperature _TL (274 ° C.) at which the phase change starts, only the heat stored as sensible heat in the heat storage agent is used, so that the temperature increases as heat dissipation progresses. descend. On the other hand, from 274 ° C. to Tmin, latent heat associated with the phase change of the heat storage agent is mainly used. This region is characterized by a small temperature change even if heat dissipation progresses, and when viewed from the object to be heated, it receives heat under conditions where the temperature hardly changes, so it is easy to keep the heating conditions of the object to be heated constant and steam. Supply is also stable. The steam supply device preferably operates in a temperature range in which the phase change of the heat storage agent progresses. It is preferable to set Tmax and Tmin in consideration of the characteristics of such a heat storage agent. The temperature ranges of Tmax and Tmin are hereinafter referred to as "operating range of the heat storage agent" or simply "operating range".

From here, returning to FIG. 1, the first embodiment of the present disclosure will be described in detail with reference to the drawings.

The solar concentrating heat collecting unit 2 includes a condensing heat collecting device 2a and a heat storage agent circulation pump 2b, and the heat storage agent X1 circulates through the fluid heating tube of the condensing heat collecting device 2a. The condensing heat collector 2a condenses sunlight, collects it in a fluid heating tube, and heats the surface of the fluid heating tube. This heat is transferred to the heat storage agent X1 flowing in the fluid heating tube, and the heat storage agent X1 is heated.

The medium heating unit 3 includes a heat storage agent storage tank 3a in which the heat storage agent X1 is stored. That is, the heated heat storage agent X1 is stored in the heat storage agent storage tank 3a. In the heat storage agent storage tank 3a, there is a heat exchanger 3b that guides the supply medium Z1 and a heat storage agent discharger 3c for discharging heat energy and discharging the heat storage agent X1 that has settled on the bottom of the heat storage agent storage tank 3a. And are provided. The heat storage agent discharger 3c has a screw feeder-like discharge blade and a drive device in order to discharge the heat storage agent X1 which is partially changed to a solid and becomes a slurry and has an increased viscosity. The heat storage agent discharger 3c continuously discharges the heat storage agent X1 in the heat storage agent storage tank 3a.

The heat exchanger 3b may have a structure in which the heat exchanger 3b is arranged so as to be completely immersed in the heat storage agent X1 in the heat storage agent storage tank 3a, and the supply medium Z1 passes through the inside. As the heat exchanger 3b, the shape in which one pipe is bent is the most common, but a plate shape may also be used. The heat exchanger 3b is not particularly limited as long as it has a sufficient heat transfer surface and has a structure that does not prevent the solid content of the heat storage agent X1 adhering to the outer surface from peeling off.

The steam supply unit 4 includes a steam drum 4a. The supply medium Z1 is stored in the steam drum 4a. The steam drum 4a is connected to a heat exchanger 3b provided in the medium heating unit 3, whereby a path for the supply medium Z1 to circulate between the steam drum 4a and the heat exchanger 3b is formed. A pipe for taking out the steam (steam medium Z1s) generated by heating the supply medium Z1 and supplying the steam medium Z1s to the intended use is connected to the upper side of the steam drum 4a in the vertical direction. Further, the supply medium Z1 becomes steam and is supplied to the intended use, so that the amount of storage of the supply medium Z1 in the steam drum 4a is reduced. To replenish the supply medium Z1, the liquid replenishment medium Z is supplied from the medium circulation unit 5 to the steam drum 4a, and the stored amount of the supply medium Z1 in the steam drum 4a is maintained.

The medium circulation unit 5 is pressurized by the medium tank 5a for storing the liquid replenishment medium Z, the medium supply pump 5b for pressurizing the replenishment medium Z and sending it to the vapor supply unit 4, and the medium supply pump 5b. A medium preheater 5c for preheating the replenishment medium Z is provided. The steam medium Z1s recovered from the intended use is supplied to the primary side of the medium preheater 5c, and heat exchanges with the replenishment medium Z supplied to the steam supply unit 4 in the medium preheater 5c. After that, the steam medium Z1s becomes a liquid of about atmospheric pressure while passing through the pressure control valve 5d and the medium condenser 5e provided at the outlet on the primary side of the medium preheater 5c, and becomes a liquid of about atmospheric pressure in the medium tank 5a as the replenishment medium Z. It is stored and reused.

The operation of the steam supply device 1 of the present embodiment will be described.
In the steam supply device 1, first, the heat energy obtained by condensing sunlight is taken into the heat storage agent X1. The heat storage agent X1 stored in the heat storage agent storage tank 3a is discharged from the heat storage agent storage tank 3a by the heat storage agent discharger 3c. After that, the heat storage agent X1 is supplied to the condensing heat collector 2a by the heat storage agent circulation pump 2b, and is heated by the heat energy obtained by condensing sunlight. A plurality of condensing heat collectors 2a are arranged on a land (condensing heat collecting zone) having an appropriate area where sufficient solar radiation can be obtained. Piping is provided so that the heat storage agent X1 can be supplied to each of the plurality of condensing heat collectors 2a as evenly as possible. The heat storage agent X1 heated by the condensing heat collector 2a is collected by a pipe and sent to the heat storage agent storage tank 3a.

In the heat storage agent X1, as described with reference to FIG. 4 as an example, there is a temperature region in which a phase change between the solid phase and the liquid phase occurs in a temperature region suitable for heating the medium (supply medium Z1) and generating vapor by heating. exist. In this temperature range, the heat storage agent X1 has a liquid phase or a mixture of a liquid phase and a solid phase, but can be treated as a fluid because of the fluidity of the heat storage agent X1. Utilizing this, the operating range of the heat storage agent X1 is set in a temperature range in which the fluidity of the heat storage agent X1 can be maintained. In addition to the increase / decrease in sensible heat corresponding to the temperature of the heat storage agent X1 in this operating range, the heat storage / heat dissipation of the heat storage agent X1 is performed by the inflow and outflow of latent heat accompanying the phase change.

The heat storage agent X1 is heated by utilizing the heat energy obtained by condensing sunlight while passing through the condensing heat collector 2a. As a result, the solid phase of the heat storage agent X1 is completely changed to a liquid phase, and the heat storage agent X1 is further heated to become a high-temperature liquid. Actually, the specifications of the solar condensing heat collecting unit 2 are determined so that the temperature of the heat storage agent X1 reaches a preset Tmax. The number and arrangement of the condensing heat collectors 2a differ depending on the conditions of the installation location, and are preferably set arbitrarily in consideration of the degree of achievement of Tmax.

In the heat storage agent storage tank 3a, heat exchange is performed between the heat storage agent X1 and the supply medium Z1 passing through the heat exchanger 3b. As a result, the supply medium Z1 is heated, and a part of the supply medium Z1 becomes steam, which is guided to the steam drum 4a. During this period, the heat storage agent X1 gradually loses sensible heat by giving heat energy to the supply medium Z1, and the temperature drops. When the temperature of the heat storage agent X1 _{reaches the temperature TL} at which the phase change begins, the change from the liquid phase of the heat storage agent X1 to the solid phase begins, and latent heat is released. The temperature of the heat storage agent X1 drops slowly while the latent heat is released, and the supply medium Z1 is stably heated. With the release of latent heat, the proportion of the solid phase in the heat storage agent X1 gradually increases, and the solid content of the heat storage agent X1 is deposited on the surface of the heat exchanger 3b.

The solid content of the heat storage agent X1 adhering to the surface of the heat exchanger 3b is not a strong solid but a relatively fragile solid content containing a liquid phase. Therefore, in the process of growing the solid content of the heat storage agent X1, the heat storage agent X1 eventually peels off and falls to the bottom of the heat storage agent storage tank 3a. On the bottom of the heat storage agent storage tank 3a, the solid content of the heat storage agent X1 thus separated from the heat exchanger 3b is deposited. As for the solid content deposited on the bottom of the heat storage agent storage tank 3a, the liquid phase exists in the gaps between the crystal particles of the solidified heat storage agent X1, so that the heat storage agent X1 on the bottom of the heat storage agent storage tank 3a can be easily fluidized. It is in a state.

The solid content of the heat storage agent X1 adhering to the surface of the heat exchanger 3b is peeled off by its own weight. However, if the solid content of the heat storage agent X1 covers the surface of the heat exchanger 3b for a long time, heat transfer may be hindered. Further, when the temperature is further lowered in a state where the solid content of the heat storage agent X1 is attached to the surface of the heat exchanger 3b, the heat storage agent X1 becomes a strong solid, which may be difficult to remove. Therefore, it is necessary to peel off the solid content of the heat storage agent X1 and drop it in the shortest possible time. A stirring device 3d may be provided in the heat storage agent storage tank 3a for the purpose of promoting peeling of the solid content of the heat storage agent X1. The stirring device 3d creates a flow of the heat storage agent X1 in the heat storage agent storage tank 3a, and the flow promotes the peeling of the solid content of the heat storage agent X1 adhering to the surface of the heat exchanger 3b. Therefore, it is not necessary to generate a strong flow of the heat storage agent X1 by the stirring device 3d, and a gentle flow may be generated.

A heat storage agent discharger 3c is provided at the bottom of the heat storage agent storage tank 3a, and the solid content of the heat storage agent X1 deposited on the bottom of the heat storage agent storage tank 3a is discharged. The solid content of the heat storage agent X1 contains a liquid phase, and is easily fluidized by the rotation of the screw feeder-like discharge blade of the heat storage agent discharger 3c, becomes a slurry, and is sequentially discharged. The slurry of the heat storage agent X1 discharged from the heat storage agent storage tank 3a flows in the pipe, is supplied to the solar concentrating heat collecting unit 2 again, and is repeatedly used.

The supply medium Z is supplied from the medium circulation unit 5. The medium circulation unit 5 is provided with a medium tank 5a, and the replenishment medium Z is stored at a temperature of about room temperature and a pressure of about atmospheric pressure. The replenishment medium Z is pressurized by the medium supply pump 5b so as to correspond to the pressure of the steam supplied from the steam supply device 1 to the application destination. The pressurized replenishment medium Z is preheated by the medium preheater 5c. The steam medium Z1s (the replenishment medium Z is pressurized and heated to form steam) recovered from the intended use is guided to the primary side of the medium preheater 5c, and the replenishment medium is utilized by utilizing the exhaust heat of the steam medium Z1s. Heat Z to the extent possible. As a result, heat energy is effectively used.

The replenishment medium Z preheated by the medium preheater 5c is supplied to the steam drum 4a. The shape of the steam drum 4a is generally a horizontally long cylinder with both ends closed. However, the shape of the steam drum 4a is not limited as long as it satisfies the following functions. The steam drum 4a stores the supply medium Z1 (the supply medium Z is pressurized and heated). In the steam drum 4a, when the supply medium Z1 is heated and a part of the vapor becomes vapor, the vapor supply medium Z1 (referred to as "vapor medium Z1s" to distinguish it from the liquid) and the liquid supply medium Z1 Has a function to separate from. The steam drum 4a is separated and stored in the form of a supply medium Z1 (liquid) on the lower side in the vertical direction of the steam drum 4a and a vapor medium Z1s on the upper side in the vertical direction of the steam drum 4a.

The lower side of the steam drum 4a in the vertical direction is connected to the heat exchanger 3b installed in the heat storage agent storage tank 3a by a pipe, and the supply medium Z1 is supplied from the steam drum 4a to the heat exchanger 3b by gravity. The supply medium Z1 heated by the heat exchanger 3b expands due to an increase in temperature, and a part of the supply medium Z1 evaporates to generate bubbles. Due to these expansions and partial evaporation, the specific gravity of the supply medium Z1 becomes lighter, and an upward flow is generated. As a result, the flow of the supply medium Z1 from the heat exchanger 3b to the steam drum 4a is generated. That is, a circulating flow of the supply medium Z1 is formed between the steam drum 4a and the heat exchanger 3b. The circulation of the supply medium Z1 is basically based on the natural convection as described above, but smooth natural convection may not be obtained due to the installation conditions such as the piping route. In this case, a circulation pump for forced circulation of the supply medium Z1 may be provided.

In the steam drum 4a, the supply medium Z1 stored inside circulates between the heat exchanger 3b and becomes a part of steam (steam medium Z1s), and is separated from the liquid supply medium Z1 in the steam drum 4a. It is stored vertically above. The steam medium Z1s is guided to the outside by a pipe connected above the steam drum 4a in the vertical direction and supplied to the intended use. The liquid supply medium Z1 is stored in the lower side of the steam drum 4a in the vertical direction, and is continuously heated while circulating with the heat exchanger 3b. As a result, the supply medium Z1 is heated to become steam, which is taken out as the steam medium Z1s to the outside, and thus decreases. A considerable amount of the supply medium Z1 reduced by evaporation is applied by the supply medium Z supplied from the medium circulation unit 5.

The steam supply device 1 may be provided with an auxiliary boiler 4b. The auxiliary boiler 4b is activated in the following cases to assist the supply of steam (steam medium Z1s) to the intended use. The operation and operation of the auxiliary boiler 4b will be described.

First, the auxiliary boiler 4b is used for the purpose of shortening the time required for the steam supply device 1 to reach a steady operating state when the steam supply device 1 is started or restarted. When the steam supply device 1 is started, the temperature of the heat storage agent X1 is low and the heat energy obtained by the solar concentrating heat collecting unit 2 is not stable, so that the supply medium Z1 may not be sufficiently heated. During that time, the auxiliary boiler 4b is activated to heat the supply medium Z1 and generate steam. Further, by using the auxiliary boiler 4b for keeping the entire steam supply device 1 warm or warming up, the time required for the steam supply device 1 to reach the steady operation state can be shortened.

Even during steady operation of the steam supply device 1, if a situation in which sufficient heat energy cannot be obtained from the solar condensing heat collecting unit 2 continues for a long time, such as when the weather is bad, the steam of the supply medium Z1 is supplied. There is a continuous shortage of heat energy for this. Therefore, in order to secure the steam amount of the supply medium Z1, the shortage of the steam amount can be covered by the steam generated by the auxiliary boiler 4b. Further, the temperature of the heat storage agent X1 decreases, the proportion of the solid phase in the heat storage agent X1 increases, and the fluidity of the heat storage agent X1 decreases, which may hinder the circulation of the heat storage agent X1. In this case, a steam trace may be provided in the path through which the heat storage agent X1 passes, and the auxiliary boiler 4b may be used as the steam source of the steam trace. Since the auxiliary boiler 4b has specifications that match the operating range of the heat storage agent X1 in its role, it is suitable for maintaining the temperature within the operating range (Tmin or more) of the heat storage agent X1.

In the steam drum 4a, the liquid supply medium Z1 and the vapor medium Z1s separated from the supply medium Z1 into vapor by heating the supply medium Z1 are stored in a coexisting state. Therefore, the steam medium Z1s in the steam drum 4a is saturated steam. The temperature of the saturated steam corresponds to the pressure in the steam drum 4a. Pressure adjustment is performed to keep the supply temperature of the vapor medium Z1s constant. The pressure is generally adjusted by the medium circulation unit 5, but the pressure may be adjusted at the application destination depending on the usage conditions at the application destination.

The steam supply device 1 according to the present embodiment shown in FIG. 1 recovers and reuses the used steam medium Z1s from the intended use, and includes a medium circulation unit 5. The medium circulation unit 5 is provided with a mechanism for supplying the replenishment medium Z to the vapor supply unit 4 and returning the vapor medium Z1s recovered from the intended use to a liquid for reuse. The medium preheater 5c recovers the exhaust heat of the used steam medium Z1s as much as possible, and heats the supply medium Z supplied to the steam drum 4a by the exhaust heat of the recovered steam medium Z1s.

The used steam medium Z1s whose exhaust heat has been recovered by the medium preheater 5c subsequently reaches the pressure control valve 5d. The pressure control valve 5d has a role of holding the pressure of the steam medium Z1s supplied to the application destination, thereby keeping the pressure of the steam drum 4a at a constant value. The temperature of the steam medium Z1s is maintained corresponding to the pressure of the steam drum 4a. When the pressure is adjusted at the application destination, the pressure adjustment valve 5d may not be provided, or the pressure adjustment valve 5d may be used for back pressure adjustment at the application destination.

The used vapor medium Z1s that has passed through the pressure control valve 5d is depressurized to about atmospheric pressure, and then cooled by the medium condenser 5e to be recovered as a liquid and stored in the medium tank 5a as a replenishment medium Z.
Up to this point, the case where the used vapor medium Z1s from the intended use is recovered has been described. However, depending on the configuration of the application destination, the entire amount of the vapor medium Z1s may be consumed and the vapor medium Z1s may not be recovered. Therefore, the configuration of the medium circulation unit 5 differs depending on the configuration of the application destination.

Next, the operation of the steam supply device 1 will be described in a time zone in which heat energy cannot be acquired from sunlight such as at night or when it is insufficient.

In the present embodiment, the heat storage agent X1 continuously circulates between the solar condensing heat collecting unit 2 and the heat storage agent storage tank 3a. When the circulation of the heat storage agent X1 is stopped, the heat storage agent X1 is rapidly cooled, especially in a place where heat is easily dissipated, such as a pipe, and the fluidity of the heat storage agent X1 is lost due to an increase in the solid phase in the heat storage agent X1. There is a possibility of being damaged. Therefore, the circulation of the heat storage agent X1 is basically not stopped even in the time zone when the heat energy cannot be acquired from the sunlight or is insufficient, and the heat storage agent X1 can be subjected to heat retention and tracing along the path through which the heat storage agent X1 passes. Keep above the temperature at which fluidity is maintained (lower limit temperature Tmin in the operating range).

On the other hand, regarding steam supply, while the heat storage agent X1 stores sufficient heat energy, the supply medium Z1 is continuously heated in the heat exchanger 3b, and the steam medium Z1s separated by the steam drum 4a is used. It will continue to be supplied to the intended use. During this period, the temperature of the heat storage agent X1 gradually decreases, and the phase change from the liquid phase to the solid phase in the heat storage agent X1 progresses, so that the amount of solid content of the heat storage agent X1 deposited at the bottom of the heat storage agent storage tank 3a. Also gradually increases.

Stable steam supply is continued from the steam supply device 1 even while sufficient heat energy from sunlight is not obtained. After that, when the acquisition of heat energy from sunlight is restored, the heat storage agent X1 is heated, the phase change of the heat storage agent X1 from the solid phase to the liquid phase, and the temperature of the heat storage agent X1 rises due to the heat storage in the liquid phase. do. As a result, the solid content of the heat storage agent X1 deposited on the bottom of the heat storage agent storage tank 3a is also reduced.
As described above, the heat storage agent X1 repeats heat storage and heat dissipation in response to the repetition of daytime and nighttime, and the supply medium Z1 can be continuously heated, so that steam can be continuously supplied.

The above is the basic operation of the first embodiment according to the present disclosure, but in order to realize a more stable steam supply, a more preferable operation can be realized by adding the following.

One is a stirring device 3d installed in the heat storage agent storage tank 3a.
Since the solid content of the heat storage agent X1 adhering to the surface of the heat exchanger 3b may hinder heat transfer, it is not preferable that the solid content of the heat storage agent X1 continues to adhere to the surface of the heat exchanger 3b for a long time. .. Further, the temperature of the solid content of the heat storage agent X1 adhering to the surface of the heat exchanger 3b is lowered to become a strong solid, which may make it difficult to remove the solid content of the heat storage agent X1. Therefore, it is necessary to peel off the solid content of the heat storage agent X1 and drop it in the shortest possible time. In order to promote the peeling of the solid content of the heat storage agent X1, a stirring device 3d may be provided in the heat storage agent storage tank 3a. The stirring device 3d brings a gentle flow to the heat storage agent X1 in the heat storage agent storage tank 3a, and promotes the peeling of the solid content of the heat storage agent X1 adhering to the surface of the heat exchanger 3b.

Next, there is an auxiliary heater 3e provided at the bottom of the heat storage agent storage tank 3a.
The solid content of the heat storage agent X1 deposited on the bottom of the heat storage agent storage tank 3a may further lose its fluidity due to the heat dissipation, which further lowers the temperature and increases the proportion of the solid phase. In view of such a situation, an auxiliary heater 3e may be provided at the bottom of the heat storage agent storage tank 3a. The auxiliary heater 3e may heat the heat storage agent X1 to a temperature at which the fluidity of the heat storage agent X1 is kept to a minimum. Further, as the heating method by the auxiliary heater 3e, an electric heating type may be adopted, or a part of the steam medium Z1s supplied from the steam supply unit 4 is guided to the auxiliary heater 3e and used for heating the heat storage agent X1. You may.

As described above, the heat energy obtained by condensing sunlight by the steam supply device 1 of the present embodiment is stored by using the heat storage agent X1 during the daytime, and the heat energy stored by the heat storage agent X1 is stored. It can be used to heat the supply medium Z1 and stably supply the generated steam of the supply medium Z1 (steam medium Z1s) to the application destination day and night continuously.

[Second Embodiment]
A modification of the steam supply device 1 of the first embodiment will be described as the second embodiment. For the same configuration, the reference numerals are the same, and the description thereof will be omitted.

As shown in FIG. 5, the steam supply device 1A according to the present embodiment supplies the solar light condensing heat collection unit 2, the medium heating unit 3, the steam supply unit 4, and the medium circulation unit 5. A heat storage agent storage unit 6 and a recovery heat storage agent storage unit 7 are further provided.

_{The solar concentrating heat collecting unit 2 further includes a purging gas supply device 2c and a path switching valve 2d (2d 1 to 2d 4} ) in addition to the condensing heat collecting device 2a and the heat storage agent circulation pump 2b. The purge gas supply device 2c and the path switching valve 2d function as the heat storage agent evacuation mechanism of the present disclosure. The heat storage agent X1 is sent out by the heat storage agent circulation pump 2b, heated by the condensing heat collector 2a, and then supplied to the supply heat storage agent storage unit 6. During this period, a plurality of path switching valves 2d are provided for path switching, and the path of the heat storage agent X1 is changed according to the state of heat collection in the condensing heat collector 2a. Further, when the route of the heat storage agent X1 is changed, the heat storage agent X1 in the condensing heat collector 2a and the front and rear pipes is pumped to the supply heat storage agent storage unit 6 and the recovery heat storage agent storage unit 7, so that the purge gas supply device 2c Supply the purge gas G. Since the use of the purge gas G is limited at the time of switching the route of the heat storage agent X1, the amount of the purge gas G used is limited. However, since the purge gas G comes into direct contact with the heat storage agent X1, it is selected from components that do not have a risk of deterioration of the heat storage agent X1.

The supply heat storage agent storage unit 6 includes a supply heat storage agent storage tank 6a and a supply heat storage agent transfer pump 6b. The heat storage agent X1 heated by the condensing heat collector 2a is supplied to the supply heat storage agent storage tank 6a. The supply heat storage agent storage tank 6a is a container whose periphery is covered with a heat insulating material or the like, and stores the heat storage agent X1 in a heat-retaining state. The bottom of the supply heat storage agent storage tank 6a is connected to the supply heat storage agent transfer pump 6b, and the heat storage agent X1 stored inside the supply heat storage agent storage tank 6a (heat storage agent X1 heated by the condensing heat collector 2a). Is sent out by the supply heat storage agent transfer pump 6b and supplied to the medium heating unit 3. As the supply heat storage agent transfer pump 6b, a pump having a screw-shaped rotor suitable for transferring the slurry may be used. However, the heat storage agent X1 passing through the supply heat storage agent transfer pump 6b has a high temperature, and all of them are in a liquid phase and have a relatively low viscosity. Therefore, the heat storage agent transfer pump 6b is adaptable to a high temperature. , Other types of pumps may be used.

The heat storage agent X1 stored in the supply heat storage agent storage tank 6a is heated by the condensing heat collector 2a and is in the temperature range ( _{TL to} Tmax) in which all the components are present in the liquid phase. Therefore, the fluidity of the heat storage agent X1 is maintained even if the stirring operation is not performed. However, if there is a possibility that the temperature of the heat storage agent X1 may decrease for some reason, a stirring device 6c may be provided as a device for promoting the fluidization of the heat storage agent X1. The stirring device 6c has a stirring blade and a driving device, and by rotating the stirring blade, the heat storage agent X1 inside the supply heat storage agent storage tank 6a is stirred as needed. As a result, it is possible to prevent a part of the heat storage agent X1 stored in the supply heat storage agent storage tank 6a from solidifying and settling, and to maintain the fluidity of the heat storage agent X1.

The medium heating unit 3 is installed in the heat storage agent storage tank 3a in which the heat storage agent X1 is stored, the heat storage agent storage tank 3a, the heat exchanger 3b for guiding and heating the supply medium Z1, and the heat storage agent storage. In addition to the heat storage agent discharger 3c for discharging the solid content of the heat storage agent X1 deposited on the bottom of the tank 3a, the slurry-like heat storage agent X1 discharged by the heat storage agent discharger 3c is collected as the heat storage agent storage unit. A recovery heat storage agent transport pump 3f for sending to No. 7 is provided. Similar to the first embodiment, the medium heating unit 3 may include a stirring device 3d and an auxiliary heater 3e. The stirring device 3d promotes the peeling of the solid content of the heat storage agent X1 generated on the surface of the heat exchanger 3b by giving a gentle flow to the heat storage agent X1. The auxiliary heater 3e prevents the heat storage agent X1 from solidifying at the bottom of the heat storage agent storage tank 3a. The stirring device 3d and the auxiliary heater 3e prevent troubles associated with the solidification of the heat storage agent X1, and are not limited to the above-mentioned devices as long as they have a function to replace them.

The recovery heat storage agent storage unit 7 includes a recovery heat storage agent storage tank 7a for temporarily storing the heat storage agent X1 after heat exchange in the medium heating unit 3, a recovery heat storage agent discharger 7b, and a recovery heat storage agent stirring device 7c. And. In the recovery heat storage agent storage tank 7a, the heat storage agent X1 having an increased viscosity due to an increase in the proportion of the solid phase is stored because the temperature is lowered by heat exchange in the medium heating unit 3. The flow of the heat storage agent X1 stored in the recovery heat storage agent storage tank 7a is extremely slow. Therefore, the recovery heat storage agent stirring device 7c helps the flow of the high-viscosity heat storage agent X1 by slowly stirring the entire inside of the recovery heat storage agent storage tank 7a. As the recovery heat storage agent stirring device 7c, it is preferable to use a stirring device having a rotary blade having a shape in which several spiral, propeller-shaped or paddle-shaped stirring blades are arranged in the vertical direction and having a relatively slow rotation speed.

The recovery heat storage agent storage tank 7a is a container whose periphery is covered with a heat insulating material or the like. In order to prevent the temperature of the heat storage agent X1 from dropping and losing its fluidity, a recovery heat storage agent auxiliary heater 7d may be provided. The recovery heat storage agent auxiliary heater 7d may be able to heat the heat storage agent X1 so that the temperature does not fall below Tmin. As for the heating method by the recovery heat storage agent auxiliary heater 7d, a steam trace, an electric heater, or any other method may be used as long as the temperature of the heat storage agent X1 can be controlled. Further, the shape of the recovery heat storage agent auxiliary heater 7d may be any shape such as a pipe shape or a plate shape as long as it satisfies the function of heating so that the temperature of the heat storage agent X1 does not fall below Tmin. The temperature around the recovery heat storage agent discharger 7b provided at the bottom of the recovery heat storage agent storage tank 7a needs to be within a range capable of maintaining the fluidity of the heat storage agent X1. The recovery heat storage agent auxiliary heater 7d can effectively control the ambient temperature of the recovery heat storage agent discharger 7b.

The operation of the steam supply device 1A of the present embodiment will be described.
In the steam supply device 1A, in the condensing heat collector 2a, the heat storage agent X1 obtains heat energy from sunlight and is heated until the temperature is higher than the _{temperature TL in the operating range, preferably Tmax.} As a result, the heat storage agent X1 is sent to the supply heat storage agent storage tank 6a in a state where all of the heat storage agent X1 is in the liquid phase. After the heat storage agent X1 is temporarily stored in the supply heat storage agent storage tank 6a, the heat storage agent storage tank 3a is provided by the supply heat storage agent transfer pump 6b according to the state of heat transfer to the supply medium Z1 by the medium heating unit 3. Will be sent to. In the heat storage agent storage tank 3a, heat exchange is performed between the heat storage agent X1 and the supply medium Z1 passing through the heat exchanger 3b. The heated supply medium Z1 is sent to the steam drum 4a. The heat storage agent X1 whose temperature has dropped by releasing thermal energy becomes a solid content and adheres to the surface of the heat exchanger 3b.

The solid content of the heat storage agent X1 adhering to the surface of the heat exchanger 3b is peeled off from the surface of the heat exchanger 3b and settles to the bottom of the heat storage agent storage tank 3a due to the difference in specific gravity. During this time, the stirring device 3d provided in the heat storage agent storage tank 3a generates a gentle flow in the liquid heat storage agent X1 filled in the heat storage agent storage tank 3a, thereby promoting the peeling of the solid content of the heat storage agent X1. As a result, the surface of the heat exchanger 3b returns to a state in which it comes into direct contact with the liquid heat storage agent X1, so that heat transfer to the supply medium Z1 is promoted. Further, by promoting the peeling of the solid content of the heat storage agent X1, the solid content of the heat storage agent X1 can be quickly moved to the bottom of the heat storage agent storage tank 3a.

The heat storage agent X1 which has become a solid content due to a decrease in temperature is deposited on the bottom of the heat storage agent storage tank 3a. While the temperature of the heat storage agent X1 is kept above the lower limit temperature (Tmin) of the operating range, the heat storage agent X1 is in a slurry shape including the liquid phase, so that it is easy to operate the heat storage agent discharger 3c. It is discharged from the heat storage agent storage tank 3a and sent to the recovery heat storage agent storage tank 7a by the recovery heat storage agent transport pump 3f. In the recovery heat storage agent storage tank 7a, the heat storage agent X1 is temporarily stored, and then sent from the bottom of the recovery heat storage agent storage tank 7a to the heat storage agent circulation pump 2b through the recovery heat storage agent discharger 7b, and is collected again by sunlight. It is supplied to the heat unit 2 and reused.

Next, the operation of the steam supply device 1A will be described in a time zone in which heat energy cannot be acquired or is insufficient from sunlight such as at night.

There are several causes of thermal energy deficiency from sunlight, and the response differs depending on the duration of the thermal energy deficiency state. For example, it is possible that there is a temporary shortage of thermal energy due to the sunlight being blocked by clouds during sunny days. In this case, the movement of the clouds that block the sunlight causes the sunshine to return and heat energy to be obtained again, so unless the temperature of the path through which the heat storage agent X1 passes falls below Tmin and tends to drop further. , There is no need to switch routes.

On the other hand, if it is expected that the temperature of the heat storage agent X1 will drop to a temperature below Tmin due to the long hours of sunshine being blocked by clouds even during sunny days, the sunshine will be restored as a temporary measure. In order to maintain the fluidity of the heat storage agent X1, the operation of keeping all the paths through which the heat storage agent X1 passes is performed at Tmin or more. Specifically, the heat storage agent X1 may be heated by the auxiliary heater while monitoring the temperature of the heat storage agent X1. An electric heater or a steam trace can be considered as the heat source of the auxiliary heater, and a part of the steam supplied from the steam supply device 1A to the application destination may be used as the steam source of the steam trace.

When sunshine cannot be obtained for a long time due to nighttime and weather, if heating by the auxiliary heater is continued in order to maintain the fluidity of the heat storage agent X1 passing through the solar condensing heat collecting unit 2, energy consumption increases. Not preferable. Therefore, during the time when the sunlight cannot be obtained for a long time, the path switching valve 2d (1st to 4th valves 2d) is connected to the path of the heat storage agent X1 so that the operation of the solar condensing heat collecting unit 2 can be stopped. _{1 to} 2d ₄ ) are provided. _{Three path switching valves 2d (1st to 3rd valves 2d 1 to 2d 3} ) are installed at the outlet of the heat storage agent circulation pump 2b, and are in the middle of the path from the condensing heat collector 2a to the supply heat storage agent storage tank 6a. One path switching valve 2d (fourth valve 2d ₄ ) is installed in the vehicle. By combining the opening and closing of the path switching valve 2d, the path of the heat storage agent X1 is arbitrarily switched. The specific operation method will be described below.

Table 1 shows the relationship between the open / closed state of the path switching valve 2d of the heat storage agent X1 and the operation of the solar concentrating heat collecting unit 2. In Table 1, the operation of the operating state (1) is performed while the solar condensing heat collecting unit 2 is operating, such as during the sunshine hours. In the operating state (1), the heat storage agent circulation pump 2b is in operation, and the first, second, and fourth valves 2d ₁ , 2d ₂ , and 2d ₄ of the path switching valves are opened, and the third valve is in the open state. The valves 2d ₃ are closed. The heat storage agent X1 delivered from the heat storage agent circulation pump 2b is supplied to the concentrating heat collector 2a, and the heat storage agent X1 heated by the concentrating heat collector 2a is continuously supplied to the heat storage agent storage tank 6a. ..

The operations of the operating states (2) and (3) are performed in the time zone for switching the driving state of the solar condensing heat collecting unit 2 such as at sunset. At sunset, the heat storage agent X1 cannot be heated in the concentrating heat collector 2a, so the supply of the heat storage agent X1 to the concentrating heat collector 2a is stopped. At that time, the heat storage agent circulation pump 2b is stopped. The heat storage agent X1 remains in the path from the heat storage agent circulation pump 2b through the condensing heat collector 2a to the supply heat storage agent storage tank 6a, and if left as it is, the heat storage agent X1 changes to a solid phase due to a temperature drop. Flow can be difficult. Therefore, an operation is performed to evacuate all the heat storage agent X1 remaining in the path from the heat storage agent circulation pump 2b through the condensing heat collector 2a to the supply heat storage agent storage tank 6a to the nearest storage tank. This operation is the operating states (2) and (3) in Table 1. The path switching valve 2d is opened and closed as shown in Table 1, and the heat storage agent X1 remaining in the pipe is pumped by the purge gas G supplied from the purge gas supply device 2c.

The operating states (2) and (3) shown in Table 1 will be specifically described.
The operating state (2) is an operation of retracting the heat storage agent X1 remaining in the pipe from the heat storage agent circulation pump 2b to the condensing heat collector 2a to the recovery heat storage agent storage tank 7a. The heat storage agent circulation pump 2b is stopped, the first valve 2d ₁ of the path switching valve is closed, the second valve 2d ₂ is left open, and the third valve 2d ₃ is opened. A pipe connected to the upper part of the recovery heat storage agent storage tank 7a in the vertical direction is connected to the third valve 2d _3. Moreover, closing the fourth valve 2d ₄ located downstream of the condensing heat absorption unit 2a, pumped in this state, by supplying a purge gas G, a heat storage agent X1 remaining in the path to the recovery heat storage agent reservoir 7a do. A pipe for discharging the purge gas G (not shown) is provided in the upper part of the recovery heat storage agent storage tank 7a in the vertical direction, and the supplied purge gas G is discharged to the atmosphere from the pipe (not shown).

In the operating state (2), _{after the evacuation of the heat storage agent X1 between the first valve 2d 1} of the path switching valve and the condensing heat collector 2a is completed, the supply of the purge gas G is stopped and the operating state (3) is performed. .. _{By closing the second valve 2d 2} of the path switching valve and opening the fourth valve 2d ₄ to supply the purge gas G, the heat storage agent X1 remaining between the heat storage agent storage tank 6a is supplied from the concentrating heat collector 2a. It is retracted to the heat storage agent storage tank 6a. Similar to the operating state (2), a pipe for releasing to the atmosphere (not shown) is connected to the upper part of the supply heat storage agent storage tank 6a in the vertical direction, and the purge gas G used for pumping the heat storage agent X1 is It is released to the atmosphere from the supply heat storage agent storage tank 6a.

The operation of the operating state (4) is performed while the sunlight condensing and heat collecting unit 2 is stopped, such as at night. As a result of the operations of the operating states (2) and (3), heat is stored in the piping _{from the second valve 2d 2 of} the path switching valve to the fourth valve 2d _{4 of the path switching valve via the condensing heat collector 2a.} The agent X1 is evacuated and is filled with the purge gas G. On the other hand, since the heat storage agent circulation pump 2b and the heat storage agent X1 in the pipes before and after the heat storage agent circulation pump 2b cannot be retracted, the flow state is maintained as the operating state (4). Specifically, the first valve 2d ₁ of the path switching valve is opened, the heat storage agent circulation pump 2b is operated, and the recovery heat storage agent discharger 7b, the heat storage agent circulation pump 2b, and the path switching valve are operated from the recovery heat storage agent storage tank 7a. It circulates through the first valve 2d ₁ and the third valve 2d ₃ of the above, and returns to the recovery heat storage agent storage tank 7a.

As described above, in the second embodiment of the present disclosure, the heat storage agent X1 is collected by the condensing heat collector 2a so as not to cause a problem that the heat storage agent X1 loses fluidity due to a temperature drop and the circulation system of the heat storage agent X1 is blocked. The path of the heat storage agent X1 is changed according to the heat state. Further, when the route of the heat storage agent X1 is changed, the heat storage agent X1 in the condensing heat collector 2a and the front and rear pipes is pumped to the supply heat storage agent storage unit 6 and the recovery heat storage agent storage unit 7, so that the purge gas supply device 2c Purge gas G can be supplied. Since the use of the purge gas G is limited when the path of the heat storage agent X1 is switched, the amount of the purge gas G used is also limited. However, since the purge gas G comes into direct contact with the heat storage agent X1, it is selected from components that do not have a risk of deterioration of the heat storage agent X1. Further, the purge gas G is supplied by preheating to a temperature equal to or higher than the lower limit temperature (Tmin) of the operating range of the heat storage agent X1 in order to prevent the heat storage agent X1 from being cooled and solidified.

The operation of switching the route of the heat storage agent X1 will be described with reference to Table 1 and FIGS. 6A to 6C.
The solar concentrating heat collecting unit 2 includes a plurality of condensing heat collecting devices 2a, and the heat storage agent X1 is basically sent from one heat storage agent circulation pump 2b and branched by a pipe to form a plurality of heat storage agents. It is distributed to the condensing heat collector 2a. The heat storage agent X1 heated by the condensing heat collector 2a is integrated into one by a pipe and supplied to the supply heat storage agent storage tank 6a. The path switching valve 2d is located at a position close to the storage tank in which the flow of the heat storage agent X1 is integrated and the heat storage agent X1 is retracted, that is, the outlet of the heat storage agent circulation pump 2b and the supply heat storage agent storage tank 6a. It may be installed in two places with the entrance of. The supply position of the purge gas G is preferably in the immediate vicinity of the condensing heat collector 2a, which is arranged in large numbers. Since the heat storage agent X1 is not sufficiently evacuated if the purge gas G is supplied from only one place, the purge gas G is supplied from as many places as possible. It is preferable that the purge gas G is not supplied from many locations at once, but is supplied in stages from one location to several locations.

When the scale of the heat energy to be collected is very large and the area where the condensing heat collector 2a is arranged is very large, one pump 2b is equal to all the condensing heat collectors 2a. It may be difficult to supply the heat storage agent X1 to the heat storage agent X1. In such a case, a large number of condensing heat collectors 2a may be divided into several groups, and one heat storage agent circulation pump 2b may be provided in each group. The heat storage agent X1 is branched from the recovery heat storage agent discharger 7b to a plurality of groups, and the heat storage agent X1 is supplied and heated to the condensing heat storage device 2a for each group, and finally one supply heat storage agent is finally supplied. It is supplied to the storage tank 6a and stored. As a result, the supply of the heat storage agent X1 to a large number of condensing heat collectors 2a can be equalized as much as possible, and the heating of the heat storage agent X1 can be made more efficient. In such a case, it is preferable to install the path switching valve 2d of the heat storage agent X1 and supply the purge gas G on a group basis.

As described above, the path through which the heat storage agent X1 passes is switched between the sunshine hours when the solar concentrating heat collecting unit 2 operates and the time when the solar condensing heat collecting unit 2 stops operating. .. The operation in each time zone will be described with reference to FIGS. 6A to 6C.

FIGS. 6A to 6C schematically show a path through which the heat storage agent X1 circulates, which is composed of a solar concentrating heat collecting unit 2, a supply heat storage agent storage tank 6a, a heat storage agent storage tank 3a, and a recovery heat storage agent storage tank 7a. It is represented as. Further, in FIGS. 6A to 6C, a valve for switching the circulation path of the heat storage agent X1 is described in the circulation path of the heat storage agent X1. FIG. 6A shows the operating state (1) in the sunshine hours (from sunrise to sunset) when the solar condensing heat collecting unit 2 is operating. FIG. 6B shows the operating states (2) and (3) at sunset (that is, the time zone for switching the route) when the collection of sunlight is stopped. FIG. 6C shows an operating state (4) in a time zone when no sunshine is obtained, such as at night when the collection of sunlight is stopped. Further, FIGS. 6A to 6C also include figures showing the storage amount (tank level) of the heat storage agent X1 in each storage tank.

In the heat storage agent storage tank 3a, heat energy corresponding to the amount of heat of heating of the supply medium Z1 is continuously released from the heat storage agent X1. As a result, the temperature of the heat storage agent X1 that has released heat energy and whose temperature has decreased gradually decreases, and a part of the heat storage agent X1 changes to a solid phase. As a result, the solid content of the heat storage agent X1 is deposited on the surface of the heat exchanger 3b. The solid content of the heat storage agent X1 eventually peels off and settles on the bottom of the heat storage agent storage tank 3a and accumulates. As a result, the heat storage agent X1 which has become a solid content is deposited one after another on the bottom of the heat storage agent storage tank 3a. However, by operating the heat storage agent discharger 3c installed at the bottom of the heat storage agent storage tank 3a, the accumulated heat storage agent X1 is sequentially discharged. The heat storage agent X1 that peels off from the heat exchanger 3b and settles at the bottom of the heat storage agent storage tank 3a is discharged at any time by the heat storage agent discharger 3c, so that the deposited layer of the heat storage agent X1 that has become a solid content is almost constant. It is kept at the thickness of.

In order to heat the supply medium Z1, the heat storage agent storage tank 3a is supplied with the heat storage agent X1 heated from the supply heat storage agent storage tank 6a via the heat storage agent discharger 3c. In the heat storage agent reservoir 3a, the heated heat storage agent X1 is supplied at a flow rate Q _1, the heat storage agent X1 became solid from the bottom is discharged at a flow rate Q _1. Therefore, the tank level of the heat storage agent storage tank 3a shows a constant value at all time zones. That is, the total amount of the heat storage agent X1 stored inside the heat storage agent storage tank 3a is kept constant. In FIGS. 6A to 6C, the figure showing the tank level of each storage tank is divided into a hatched part and a white part, and the white part represents a time zone to be explained. ..

The flow rate of the heat storage agent X1 supplied from the recovery heat storage agent storage tank 7a to the solar concentrating heat collection unit 2 is set as follows. That is, the steam supply device 1A in the present disclosure is designed to cover the total heat energy required to heat the supply medium Z1 continuously for 24 hours by the total heat energy obtained from sunlight during the daylight hours. .. Specifically, the thermal energy supply side is limited to the operating hours per day during the sunshine hours (for example, 8 to 12 hours), and the thermal energy user side has the operating hours per day for 24 hours continuously. .. Therefore, the amount of heat energy collected by the sunlight condensing heat collecting unit 2 per hour is 2 to 3 times the amount of heat energy required for heating the supply medium Z1. Further, considering the margin of heat energy for temporarily blocking the sunlight, the amount of heat energy collected by the solar condensing heat collecting unit 2 per hour is the amount of heat energy required for heating the supply medium Z1. It needs to be 3 to 4 times as much as. This is the ratio of the sizes of Q ₂ (flow rate of the heat storage agent X1 passing through the solar condensing heat collecting unit 2) and Q ₁ (supply amount to the heat storage agent storage tank 3a) in FIGS. 6A to 6C.

Specifically, the total amount of heat required for heating from the lower limit temperature Tmin of the operating range of the heat storage agent X1 in the solar concentrating heat collecting unit 2 to the upper limit temperature Tmax of the operating range of the heat storage agent X1 in the sunshine time zone is integrated. The amount is represented by the following formula (1). It is assumed that the amount of heat required to heat 1 kg (kilogram) of the heat storage agent X1 from Tmin to Tmax is H _X1, and the amount of heat obtained from sunlight during the sunshine hours (for example, 8 hours) is constant.

Total calorific value = H _{X 1} x Q ₂ x [sunshine hours (8 hours)] (1)
On the other hand, when the amount of heat per hour required to heat the supply medium Z1 is H _Z1 , the total amount of heat required for heating the supply medium Z1 per day is as shown in the equation (2).
Total heat = H _Z1 x 24 (2)

Since the total calories of Equation 1 and Equation 2 are equal, Q ₂ needs to be three times Q _{1 when the sunshine duration is 8 hours.} Furthermore, the sunshine hours, or situation clouds block the sun, the sunshine in bad weather to consider an allowance or the like for the case of not sufficiently obtained, Q ₂ whereas Q _1, needs to be further larger value be.

_{As mentioned above, Q 2} is larger than _{Q 1} in the daylight hours shown in FIG. 6A. For supplying heat storage agent reservoir 6a, a flow rate of the heat storage agent X1 from sunlight condensing heat absorption unit 2 is supplied to the supply heat storage agent reservoir 6a is Q _2, it is withdrawn from the bottom of the supply heat storage agent reservoir 6a a flow rate to Q ₁ heat storage agent X1 supplied to the heat storage agent reservoir 3a. Therefore, during the sunshine hours shown in FIG. 6A, the heat storage agent storage tank 6a is oversupplied with the heat storage agent X1, and the tank level of the heat storage agent storage tank 6a rises significantly. On the other hand, the recovered heat storage agent reservoir 7a, is withdrawn from the bottom of the heat storage agent reservoir 3a, the flow rate of the heat storage agent X1 supplied to the recovery heat storage agent reservoir 7a from the recovered heat storage agent transport pump 3f is by Q ₁ , the flow rate of the heat storage agent X1 supplied withdrawn from the bottom of the recovery heat storage agent reservoir 7a by the sunlight condensing heat absorption unit 2 is Q _2. Therefore, during the sunshine hours shown in FIG. 6A, the heat storage agent X1 is excessively discharged in the recovery heat storage agent storage tank 7a, so that the tank level of the recovery heat storage agent storage tank 7a is greatly reduced.

Subsequently, the time zone (at sunset) of the route switching operation of the heat storage agent X1 shown in FIG. 6B will be described.
The supply is stopped to sunlight condensing heat absorption section 2 of the heat storage agent X1, the flow rate Q ₂ of the heat storage agent X1 is zero. However, in order to continue the heating of the feed medium Z1, and the supply amount of the heat storage agent X1 to the heat storage agent reservoir 3a, emissions from the heat storage agent reservoir 3a are both maintained in Q _1. As a result, at the time of sunset shown in FIG. 6B, since the discharge excessive as the emissions Q ₁ with respect to the supply amount zero in feed heat storage agent reservoir 6a, tank level of the supply heat storage agent reservoir 6a is reduced Turn to. Further, at the time of sunset shown in FIG. 6B, since the excess supply of the emissions zero for supply quantity Q ₁ is in the recovery heat storage agent reservoir 7a, tank level of the recovered heat storage agent reservoir 7a to increase the Turn around.

After that, the heat storage agent X1 remaining in the path (pipe) from the heat storage agent circulation pump 2b of the solar concentrating heat storage unit 2 to the supply heat storage agent storage tank 6a via the concentrating heat storage device 2a is supplied and stored. An operation of purging toward the tank 6a or the recovery heat storage agent storage tank 7a is performed. This is to prevent the heat storage agent X1 from solidifying and blocking the path. All the heat storage agent X1 in the path through which the heat storage agent X1 passes is evacuated, and in this state, the process waits until the next heat collection start (sunshine hours). The heat storage agent X1 flowing in the pipe is pressure-fed by the purge gas G. The heat storage agent X1 flowing in the upstream pipe is retracted to the recovery heat storage agent storage tank 7a, and the heat storage agent X1 flowing in the downstream pipe is retracted to the supply heat storage agent storage tank 6a. Therefore, the tank level of each storage tank is slightly increased by the purge operation.

Subsequently, a time zone for the route switching operation of the heat storage agent X1 shown in FIG. 6C (a time zone in which sunshine cannot be obtained such as at night) will be described.
FIG. 6C shows changes in the passage path and tank level of the heat storage agent X1 at night (time zone when no sunshine is obtained). Since the heat storage agent X1 is not supplied to the solar concentrating heat collecting unit 2, the flow rate Q2 of the heat storage agent X1 supplied to the solar concentrating heat collecting unit ₂ is zero. On the other hand, the medium heating unit 3, since the heating of the feed medium Z1 is continuously performed, the heat storage agent reservoir 3a, always heated heat storage agent X1 is supplied at a flow rate Q _1. Further, the same amount of the heat storage agent X1 as the supplied heat storage agent X1 is extracted from the bottom of the heat storage agent storage tank 3a as a solid content and settles. That is, the supply amount of the heat storage agent X1 to the heat storage agent reservoir 3a, emissions from the heat storage agent reservoir 3a are both maintained in Q _1. As a result, at night shown in FIG. 6C, the tank level of the supply heat storage agent storage tank 6a continues to decrease, and the tank level of the recovery heat storage agent storage tank 7a continues to increase.

The heat storage agent X1 cannot be purged in a part of the passage path of the heat storage agent X1 including the heat storage agent circulation pump 2b. Therefore, during the time period when the solar concentrating heat collecting unit 2 is stopped, the circulation is continued in the path where the heat storage agent X1 cannot be purged, and the heat storage agent X1 is prevented from cooling and solidifying. Specifically, the path switching valve 2d is operated so that the first and third valves 2d ₁ , 2d ₃ are opened and the second and fourth valves 2d ₂ , 2d _{4 are closed.} Thus, the heat storage agent X1 taken out from the bottom of the recovery heat storage agent reservoir 7a, via the heat storage agent circulating pump 2b, a path back to the top of the recovery heat storage agent reservoir 7a, continued circulation with minimal flow rate Q ₃ do.
In this way, the heat storage agent X1 that has sufficiently stored heat energy is always supplied to the heat storage agent storage tank 3a, and heat exchange between the heat storage agent X1 and the supply medium Z1 is performed in the heat exchanger 3b even at night. be able to.

That is, at night when the heat energy is not supplied by the solar concentrating heat collecting unit 2, the flow rate of the heat storage agent X1 stored in the heat storage agent storage tank 6a, which has sufficiently stored the heat energy, is the same as that in the sunshine time zone. Can be supplied to the medium heating unit 3 and heated in the supply medium Z1 under the same conditions as the sunshine time zone to generate steam in the supply medium Z1. Further, the temperature is lowered by applying heat to the supply medium Z1, and the heat storage agent X1 which has become a solid content is extracted from the bottom of the heat storage agent storage tank 3a, and the level of the heat storage agent storage tank 3a is kept constant. Is done. Therefore, the heat transfer conditions in the heat exchanger 3b are kept constant. Further, the heat storage agent X1 used for heat transfer in the heat exchanger 3b is stored in the recovery heat storage agent storage tank 7a, and is stored while maintaining the fluidity. During the time when sunshine is obtained, the heat storage agent X1 stored in the recovery heat storage agent storage tank 7a is consumed by heating the supply medium Z1 at a flow rate that greatly exceeds the amount of the heat storage agent X1. Is supplied to the heat storage agent X1 and heated to obtain a heat storage agent X1 that sufficiently stores heat energy, and is supplied to the supply heat storage agent storage tank 6a. As a result, the inventory amount of the heat storage agent X1 stored in the supply heat storage agent storage tank 6a is increased to prepare for the consumption of the heat storage agent X1 at night.

Further, when shifting from the sunshine hours to the night (time when no sunshine can be obtained), the purge gas G is supplied from the vicinity of the concentrating heat collector 2a (preferably the piping on the downstream side of the condensing heat collector 2a). .. The purge gas G may be a component that does not physically or chemically change the heat storage agent X1, and is, for example, an inert gas such as nitrogen or dry air (air from which water has been removed). The purge gas G is heated to at least the lower limit temperature Tmin in the operating range of the heat storage agent X1. By supplying the purge gas G, the heat storage agent X1 staying in the solar concentrating heat collecting unit 2 is retracted to the supply heat storage agent storage tank 6a and the recovery heat storage agent storage tank 7a.

According to this embodiment, the steam supply device 1A heats the supply medium Z1 with the heat storage agent X1 heated by the heat energy obtained by condensing sunlight to partially convert it into steam and supply it. The steam (steam medium Z1s) of the supply medium Z1 separated from the medium Z1 is supplied to the application destination. As a result, the supply medium Z1 is heated by the heat storage agent X1 even at night when the heat energy obtained from sunlight is insufficient, such as at night, and the steam (steam medium Z1s) of the supply medium Z1 is stabilized. It is possible to supply.
Further, by storing the heat energy obtained by condensing sunlight with the heat storage agent X1, the amount of heat transferred to the supply medium Z1 becomes constant, and the vapor medium Z1s can be supplied under stable conditions. Is.

Further, a supply heat storage agent storage tank 6a is provided in front of the heat storage agent storage tank 3a. As a result, the heat storage agent X1 heated by the solar condensing heat collecting unit 2 and storing sufficient heat energy can be stored in the supply heat storage agent storage tank 6a. As a result, the heat energy required for heating the supply medium Z1 can be supplied even in a time zone such as nighttime when the heat energy from sunlight cannot be obtained. Therefore, the vapor medium Z1s can be continuously supplied to the intended use regardless of the presence or absence of sunshine.

Further, a recovery heat storage agent storage tank 7a is provided after the heat storage agent storage tank 3a. As a result, heat is exchanged in the medium heating unit 3, and a part of the heat storage agent X1 solidifies as a solid phase and is deposited on the bottom of the heat storage agent storage tank 3a. Instead of staying in the storage tank 3a, it can be continuously discharged and supplied to the recovery heat storage agent storage tank 7a. The heat storage agent X1 supplied to the recovery heat storage agent storage tank 7a can be stored in the recovery heat storage agent storage tank 7a while maintaining fluidity in a slurry state until the next sunshine hours. As a result, heating of the supply medium Z1 can be continued while keeping the state of the heat storage agent X1 in the heat storage agent storage tank 3a (tank level, ratio of solid content deposited on the bottom of the heat storage agent storage tank 3a, etc.) constant. .. Therefore, the vapor medium Z1s can be continuously supplied to the intended use regardless of the presence or absence of sunshine.

Further, before and after the heat energy cannot be obtained from the sunlight by the purge gas supply device 2c and the path switching valve 2d provided in the sunlight concentrating heat storage unit 2, the condensing heat collector 2a and the condensing heat collector 2a and the condensing heat collector It is possible to remove the heat storage agent X1 remaining in the pipe that guides the heat storage agent X1 to 2a. As a result, it is possible to prevent the piping from being blocked due to the heat storage agent X1 being cooled and completely solidified in the path (piping) through which the heat storage agent X1 passes in the solar concentrating heat collecting unit 2.

In FIGS. 6A to 6C, the condensing heat collector 2a is installed on the gantry, and the heat storage agent storage tank 3a, the supply heat storage agent storage tank 6a, the recovery heat storage agent storage tank 7a, etc. A member for storing the heat storage agent X1 of the above is arranged. With this arrangement, the heat storage agent X1 staying in the piping before and after the condensing heat collector 2a and the condensing heat collector 2a can be effectively pumped to the storage tank by a purge operation. In addition, this arrangement is also preferable in terms of effective use of land.

[Third Embodiment]
A modification of the steam supply device 1A of the second embodiment will be described as the third embodiment. For the same configuration, the reference numerals are the same, and the description thereof will be omitted.

In the steam supply device 1B of the present embodiment, in addition to the solar condensing heat collecting unit 2, the medium heating unit 3, the steam supply unit 4, and the medium circulation unit 5, the steam medium superheating unit 8 (steam heating unit) ) Is further provided. The configuration of the steam supply device 1B is shown in FIG. In the drawing, only the main part is described, and the circulation system of the heat storage agent X1 described in the second embodiment is omitted. Similar to the second embodiment, the medium heating unit 3 in the present embodiment includes a circulation system of the heat storage agent X1 (not shown). Further, the steam medium superheating unit 8 also has a system for circulating the superheating heat storage agent X2 (second heat storage agent), similarly to the medium heating unit 3. Since the circulation system of the heat storage agent X2 for superheat is the same as the circulation system of the heat storage agent X1 except for the setting of the operating range of the heat storage agent X2, the description thereof will be omitted and the description of the reference numerals will be omitted.

The steam medium superheating unit 8 includes a heat storage agent storage tank 8a for superheat, a heat exchanger 8b for superheat, and a heat storage agent discharger 8c for superheat. In the superheat heat storage agent storage tank 8a, the superheat heat storage agent X2 (second heat storage agent) is stored inside. The steam medium Z1s (steam obtained by heating the supply medium Z1) supplied from the steam supply unit 4 is guided to the superheat heat exchanger 8b. Similar to the heat storage agent storage tank 3a, the superheat heat storage agent X2 heated to the upper limit temperature Tmax of the operating range is supplied to the upper portion of the superheat heat storage agent storage tank 8a in the vertical direction. The superheat heat storage agent X2 gives heat energy to the steam medium Z1s guided to the superheat heat exchanger 8b. A part of the superheat heat storage agent X2 becomes a solid phase by releasing heat energy and lowering the temperature, and adheres to the surface of the superheat heat exchanger 8b as a solid content. The superheat heat storage agent X2, which has become a solid content, eventually peels off and settles on the bottom of the superheat heat storage agent storage tank 8a. In order to prevent the superheat heat storage agent X2, which has become a solid content, from staying on the surface of the superheat heat exchanger 8b without peeling for a long time, thereby hindering the superheat of the steam medium Z1s, the stirring device 8d is further added. You may prepare. By giving a gentle flow to the superheat heat storage agent X2 using the stirring device 8d, the peeling of the superheat heat storage agent X2 is promoted.

The operating range of the mixed salt used as the heat storage agent can be changed by arbitrarily adjusting the composition. With respect to the heat storage agent X1 and the heat storage agent X2 for superheat shown in the present embodiment, it is possible to obtain an operating range suitable for the operating conditions by changing the composition of the mixed salt. However, the heat storage agent X2 for superheat does not necessarily have to have a higher temperature range in which a phase change occurs than the heat storage agent X1. By properly using the operating range of the heat storage agent X1 and the superheat heat storage agent X2, even if the heat storage agent X1 and the superheat heat storage agent X2 are mixed salts having the same composition, the operation satisfying the conditions of the steam supply device 1B is performed. Is possible. That is, there is a temperature range exceeding 100 ° C. in the example of FIG. 4 from the lower limit of the temperature range in which all the heat storage agents are present in the liquid phase (the temperature at which the change from the liquid phase to the solid phase begins: T _{L) to Tmax.} For heating the supply medium Z1 in the medium heating unit 3, the region on the low temperature side of Tmin to Tmax shown in the example of FIG. 4 is used, and the steam medium Z1s generated from the supply medium Z1 (saturated steam of the supply medium Z1) is used. ) Overheat uses the region on the high temperature side of Tmin to Tmax. As a result, the operating range can be properly used between the heat storage agent X1 and the superheat heat storage agent X2.

The superheat heat storage agent X2 releases heat energy by itself by heating the steam medium Z1s, and the temperature drops to settle at the bottom of the superheat heat storage agent storage tank 8a. Therefore, the superheat heat storage agent discharger 8c guides the superheat heat storage agent X2 to the outside of the superheat heat storage agent storage tank 8a. In FIG. 7, the upstream side (supply side of the heat storage agent X2 for overheating) and the downstream side (discharge side of the heat storage agent X2 for overheating) of the steam medium superheating unit 8 are not shown, but are with the supply heat storage agent storage unit 6. Two types of heat storage agent storage units for overheating corresponding to the recovery heat storage agent storage unit 7, and a second solar collection unit corresponding to the solar condensing heat storage unit 2 for heating the heat storage agent X2 for overheating with sunlight. It is equipped with a light heat storage unit. The operation of these devices is almost the same as that of the system in which the heat storage agent X1 circulates as described in the second embodiment, except for the temperature conditions.

Depending on the composition of the mixed salt used for the heat storage agent X2, the temperature of the heat storage agent X2 _{does not drop to TL} even after the heat storage agent X2 is used for heating the vapor medium Z1s, and therefore the solid-phase heat storage agent. X2 may not occur. In that case, the liquid phase heat storage agent X2 whose temperature has decreased is supplied to a solar concentrating heat collector (not shown) that heats the heating heat storage agent X2, and the temperature of the heat storage agent X2 is heated to near Tmax. And reuse it. That is, in this case, the vapor supply device 1B is operated in a state where the entire circulation system is filled with only the liquid phase heat storage agent X2.

The medium circulation unit 5 includes a medium tank 5a, a medium supply pump 5b, a medium preheater 5c, a pressure control valve 5d, and a medium condenser 5e. Used steam (steam medium Z1s and superheated steam medium Z2s) recovered from the intended use is supplied to the primary side of the medium preheater 5c. A liquid replenishment medium Z is supplied to the secondary side of the medium preheater 5c. The medium condenser 5e cools the used steam that has passed through the primary side of the medium condenser 5e with outside air, cold water, or the like. The vapor condensed by the medium condenser 5e is stored in the medium tank 5a as a liquid replenishment medium Z.

The auxiliary boiler 4b is an auxiliary heater when the heat energy from sunlight is not supplied for a long time. That is, the auxiliary boiler 4b operates only when the need arises. The liquid of the supply medium Z1 on the lower side in the vertical direction of the steam drum 4a is supplied to the auxiliary boiler 4b. The auxiliary boiler 4b heats the liquid supply medium Z1 by burning electric power or fossil fuel, and supplies the liquid supply medium Z1 to the steam drum 4a as a supply medium Z1 containing steam. The circulation of the supply medium Z1 between the steam drum 4a and the auxiliary boiler 4b is basically natural convection. However, if necessary, a pump for forcibly circulating the supply medium Z1 may be provided. The auxiliary boiler 4b may be used to supply steam for heat retention in the path through which the heat storage agent X1 and the superheat heat storage agent X2 pass.

In such a steam supply device 1B, while the supply medium Z1 stored in the steam drum 4a circulates with the heat exchanger 3b installed in the heat storage agent storage tank 3a, the heat storage agent X1 and the heat storage agent X1 are circulated. Heat is exchanged and part of it becomes steam. As a result, in the steam drum 4a, the liquid supply medium Z1 on the lower side in the vertical direction and the steam supply medium Z1 (steam medium Z1s) on the upper side in the vertical direction are separated. Then, the steam medium Z1s in the steam drum 4a is taken out from the upper side in the vertical direction of the steam drum 4a and guided to the superheat heat exchanger 8b in the superheat heat storage agent storage tank 8a. The steam medium Z1s is further heated by the superheat heat storage agent X2 in the superheat heat exchanger 8b to become superheated steam (superheated steam medium Z2s), which is supplied to the application destination requiring superheated steam. A part of the saturated steam (steam medium Z1s) taken out from the upper part of the steam drum 4a in the vertical direction is supplied to the application destination requiring the saturated steam.

Further, the used vapor recovered from each application destination is heat-exchanged with the liquid replenishment medium Z in the medium preheater 5c, then cooled in the medium condenser 5e and returned to the liquid replenishment medium Z. The pressure control valve 5d provided between the medium preheater 5c and the medium condenser 5e holds the pressure until the steam medium Z1s is recovered as used steam from the steam drum 4a. The temperature of the saturated steam (steam medium Z1s) is affected by the adjustment of the pressure control valve 5d. The liquid replenishment medium Z is guided to the medium tank 5a. The medium tank 5a is filled with the shortage of supply medium Z. The replenishment medium Z is pressurized by the medium supply pump 5b, preheated by the medium preheater 5c, and supplied to the steam drum 4a.

According to the present embodiment, the steam medium Z1s (saturated steam of the supply medium Z1) obtained by heating the supply medium Z1 can be reheated by the superheat storage agent X2 to be in a superheated state. Therefore, it is possible to supply the superheated steam medium Z2s (superheated steam) having a temperature higher than that of the steam medium Z1s (saturated steam) to the intended use.

According to the steam supply device 1B of the present embodiment as described above, it is possible to supply steam of a plurality of temperatures to the application destination.

[Fourth embodiment]
A modification of the steam supply device 1B of the third embodiment will be described as the fourth embodiment. The same components as those in the third embodiment have the same reference numerals, and the description thereof will be omitted.

The steam supply device 1C in the present embodiment includes a solar condensing heat collecting unit 2, a supply heat storage agent storage unit 6, a medium heating unit 3, a steam supply unit 4, a medium circulation unit 5, and a recovery heat storage agent storage. A unit 7 and a steam medium heating unit 8 are provided. In the present embodiment, the steam medium superheating unit 8 does not have its own circulation system of the heat storage agent, and receives the supply of the heated heat storage agent X1 from the supply heat storage agent storage unit 6. Further, the heat storage agent X1 is supplied to the medium heating unit 3 after heat exchange with the vapor medium Z1s in the vapor medium superheating unit 8. The configuration of the steam supply device 1C is shown in FIG.

The steam supply device 1C in the present embodiment uses one type of heat storage agent X1 to both heat the supply medium Z1 and superheat the steam medium Z1s (steam generated by heating the supply medium Z1). The heat storage agent X1 heated by the solar condensing heat collecting unit 2 moves in the order of the supply heat storage agent storage tank 6a, the overheating heat storage agent storage tank 8a, the heat storage agent storage tank 3a, and the recovery heat storage agent storage tank 7a. , Dissipates thermal energy for the purpose of overheating the steam medium Z1s and heating the supply medium Z1. As a result, the heat storage agent X1 forms a solid phase, changes into a slurry, and is temporarily stored in the recovery heat storage agent storage tank 7a. During the sunshine hours, the heat storage agent X1 stored in the recovery heat storage agent storage tank 7a is guided to the solar concentrating heat collection unit 2, heated, and reused.

The operation of the steam supply device 1C in the present embodiment will be described in detail with reference to FIG. In the present embodiment, only one type of heat storage agent is used (heat storage agent X1), and both saturated steam and superheated steam of the supply medium Z1 can be supplied to the intended use. The heat storage agent X1 is guided to a plurality of condensing heat collectors 2a by the heat storage agent circulation pump 2b, and the heat energy obtained by condensing sunlight is used to target the upper limit temperature Tmax of the operating range of the heat storage agent X1. It is heated. Taking a heat storage agent having a typical composition as an example, the heat storage agent X1 supplied at the lower limit temperature Tmin of the operating range of the heat storage agent X1 is heated by the condensing heat collector 2a on the phase change characteristic diagram of FIG. By doing so, the state changes to the state indicated by the upper limit temperature Tmax of the operating range of the heat storage agent X1 through the "heat storage" process of FIG.

The heat storage agent X1 having reached the upper limit temperature Tmax is temporarily stored in the supply heat storage agent storage tank 6a. The supply heat storage agent storage tank 6a has a heat retention structure, and the heat storage agent X1 is stored in the supply heat storage agent storage tank 6a while maintaining the state of the upper limit temperature Tmax. Heated from the bottom of the supply heat storage agent storage tank 6a, the heat storage agent X1 which has become a liquid phase is discharged at a constant flow rate, and is guided to the superheat heat storage agent storage tank 8a by the supply heat storage agent transfer pump 6b.
The steam medium Z1s generated in the steam supply unit 4 is guided to the superheat heat exchanger 8b installed inside the superheat heat storage agent storage tank 8a, and heat exchange is performed with the heat storage agent X1. FIG. 9 shows an example of a state change at that time. The heat storage agent X1 releases a part of its own sensible heat (“superheat of steam medium Z1s” process in FIG. 9), and the heat energy causes the steam medium. Z1s is overheated. In the heat storage agent storage tank 8a for superheat, the heat storage agent X1 is supplied from the upper part in the vertical direction and discharged from the lower part in the vertical direction. In the superheat heat storage agent storage tank 8a, the flow path of the superheat heat exchanger 8b is arranged so that the steam medium Z1s flows from the lower side in the vertical direction to the upper side in the vertical direction of the tubular heat exchanger 8b. do. As a result, the temperature at the outlet of the superheat heat exchanger 8b of the steam medium Z1s can be superheated to a temperature close to the upper limit temperature Tmax of the operating range of the heat storage agent X1.

In the heat storage agent storage tank 8a for superheat in the present embodiment, since the heat storage agent X1 only releases sensible heat, basically no phase change from the liquid phase to the solid phase of the heat storage agent X1 occurs. In FIG. 8, a stirring device 8d is provided in the heat storage agent storage tank 8a for superheat. However, since it is not necessary to stir the heat storage agent X1 in normal operation, the stirrer 8d may be omitted. However, due to lack of sunshine for a long time, the heat storage agent X1 may dissipate heat and form a solid phase. When the steam supply device 1C is started from such a situation, a stirring device 8d is provided in order to smoothly flow the heat storage agent X1.

The heat storage agent X1 that has released a part of the sensible heat is discharged from the bottom of the heat storage agent storage tank 8a for superheat by the heat storage agent discharger 8c for superheat, and further to the heat storage agent storage tank 3a via the heat storage agent transfer pump 8f. Be supplied. In the heat storage agent storage tank 3a, as described in the first to third embodiments, the heat storage agent X1 changes from the liquid phase to the solid phase due to heat exchange between the heat storage agent X1 and the supply medium Z1, and reaches the lower limit temperature Tmin. The temperature drops to a close position, forming a slurry, and settling at the bottom of the heat storage agent storage tank 3a. The settled slurry-like heat storage agent X1 is discharged by the heat storage agent discharger 3c, and is supplied to the recovery heat storage agent storage tank 7a via the recovery heat storage agent transport pump 3f.

The heat energy released by the heat storage agent X1 in the heat storage agent storage tank 3a is used for heating the supply medium Z1 passing through the heat exchanger 3b installed in the heat storage agent storage tank 3a, and is one of the supply media Z1 by heating. The part becomes steam (steam medium Z1s). During this period, the state of the heat storage agent X1 changes to the lower limit temperature Tmin in the operating range, as shown in the process of “heating the supply medium Z1” in FIG. Since the operation of the heat storage agent X1 is the same as that described in the first to third embodiments, detailed description thereof will be omitted.

According to the steam supply device 1C of the present embodiment as described above, it is possible to supply steam of a plurality of temperatures to an application destination by using one kind of heat storage agent. In the time zone when sunshine cannot be obtained, the route of the heat storage agent X1 is switched according to the presence or absence of sunshine as described with reference to Table 1 and FIGS. 6A to 6C in the second embodiment. As a result, steam can be continuously supplied to the intended use and can be stored without losing the fluidity of the heat storage agent X1.

In the present embodiment, as shown in FIG. 9, the supply medium Z1 is efficiently heated by properly using sensible heat and latent heat among the heat energies held by the heated heat storage agent X1. In the overheating of the steam medium Z1s, the sensible heat of the heat storage agent X1 is used to contribute to the overheating of the steam medium Z1s, that is, the increase of the sensible heat. In the heating of the supply medium Z1, the latent heat when the heat storage agent X1 changes from the liquid phase to the solid phase is mainly used to provide the latent heat for changing the liquid of the supply medium Z1 into vapor. The sensible heat of the heat storage agent X1, which has a relatively small amount of heat but a relatively high temperature, contributes to overheating of steam, that is, an increase in sensible heat. The latent heat of the heat storage agent X1, which has a relatively large amount of heat but a relatively low temperature, contributes to the heat required for the supply medium Z1 to evaporate, that is, the latent heat of vaporization. This enables efficient steam supply.

[Fifth Embodiment]
The drying system S including the steam supply device 1B used in the third embodiment of the present disclosure will be described as the fifth embodiment. For the same configuration, the reference numerals are the same, and the description thereof will be omitted.

As shown in FIG. 10, the drying system S of the present embodiment includes one of the steam supply device 1B, the steam supply device 1C, and the drying device 100. The drying system S dries the high-humidity raw material Mw (solid fuel such as high-moisture coal typified by biomass, palm slag, and lignite).

The drying device 100 includes a fluidized gas air box 103, a drying chamber 104, a drying chamber partition wall 105, a steam pipe 110 for heating, a superheated steam pressure reducing valve 111, a fluidized gas heater 120, and a fluidized gas blower 130. And. A plurality of heating steam pipes 110 are provided in the layer of the high-humidity raw material Mw forming the fluidized bed inside the drying chamber 104 so as to be orthogonal to the flow of the fluidized gas. Either the steam medium Z1s (saturated steam) or the superheated steam medium Z2s is passed through the inside of the heating steam pipe 110. Used steam that has passed through the heating steam pipe 110 is passed through the primary side of the fluidized gas heater 120, and is used for fluidizing the high-humidity raw material Mw on the secondary side of the fluidized gas heater 120. A part of the generated gas is guided as the circulating gas R via the fluidized gas blower 130. The gas used for fluidizing the high-humidity raw material Mw is heated by heat exchange with used steam and supplied to the fluidized gas air box 103 as fluidized gas N. The inert gas P is supplied to the inlet side of the fluidized gas blower 130. The inert gas P is supplied to the fluidized gas blower 130 as needed, mainly when the drying device 100 is started. Further, a part of the superheated steam medium Z2s is supplied to the fluidized gas air box 103 via the superheated steam pressure reducing valve 111.

In the steam supply device 1B, the steam medium Z1s, which is saturated steam obtained by heating and separating the supply medium Z1 in the steam supply unit 4, is guided to the overheating heat exchanger 8b and further heated by the overheating heat storage agent X2. The superheated steam medium Z2s is used. The superheated steam medium Z2s is supplied to the drying device 100. The steam supply device 1B can also supply saturated steam (steam medium Z1s) to the drying device 100. Either the steam medium Z1s or the superheated steam medium Z2s is supplied to the heating steam pipe 110 according to the operating conditions of the drying system S. Only the superheated steam medium Z2s is supplied to the fluidized gas air box 103.

The operation of the drying system S in this embodiment will be described with reference to FIG.
In the drying apparatus 100, the high-humidity raw material Mw is dried while forming a fluidized bed. Circulating gas R circulating in the system is used for fluidization of the high-humidity raw material Mw. The fluidized gas blower 130 is activated and a part of the gas discharged from the drying chamber 104 is supplied to the fluidized gas blower 130 as circulating gas R. The gas delivered from the fluidized gas blower 130 is heated by the fluidized gas heater 120 as fluidized gas N and then supplied to the fluidized gas air box 103. The drying chamber 104 provided above the fluidized gas air box 103 in the vertical direction and the fluidized gas air box 103 are separated by a dispersion mechanism (not shown). The gas supplied to the fluidized gas air box 103 is dispersed by the dispersion mechanism and injected into the drying chamber 104. Further, the high-humidity raw material Mw supplied into the drying chamber 104 falls into the fluidized gas air box 103 by the dispersion mechanism. The fluidized gas N used for fluidizing the high-humidity raw material Mw in the drying chamber 104 is discharged from the upper part of the drying chamber 104.

The fluidized gas N discharged from the drying chamber 104 contains a large amount of water evaporated from the high-humidity raw material Mw. An atmospheric release valve 112 is provided in the pipe connecting the drying chamber 104 and the fluidized gas blower 130, and a part of the fluidized gas N is discharged to the outside of the system (in the atmosphere), so that the fluidized gas N circulates in the system. Adjust the amount of water in the. The remaining fluidized gas N partially released to the atmosphere from the outlet of the drying chamber 104 is guided to the fluidized gas blower 130 as circulating gas R and reused. Further, the atmospheric release valve 112 is provided with a pressure adjusting function to keep the pressure in the drying device 100 constant. Further, while the high-humidity raw material Mw forms a fluidized bed and is dried, a part of the high-humidity raw material Mw may be crushed to generate fine powder. When this fine powder is discharged from the drying chamber 104 together with the fluidized gas N, the fine powder may affect the atmospheric release valve 112 and the fluidized gas blower 130. Therefore, a dust remover 113 for removing fine powder may be provided at the outlet of the drying chamber 104.

The heat source for drying the high-humidity raw material Mw is steam (steam medium Z1s or superheated steam medium Z2s) supplied to the heating steam pipe 110 and fluidized gas N. Either the steam medium Z1s or the superheated steam medium Z2s is selected and supplied to the heating steam pipe 110 according to the temperature required for the drying operation. The steam supplied to the heating steam pipe 110 heats the high-humidity raw material Mw by exchanging heat with the high-humidity raw material Mw supplied to the drying chamber 104, and promotes the evaporation of the water content of the high-humidity raw material Mw. The fluidized gas N fluidizes the high-humidity raw material Mw and promotes drying by removing the evaporated water from the high-humidity raw material Mw. Further, by preheating the fluidized gas N (circulating gas R) and supplying it to the drying chamber 104, the degree of drying of the fluidized gas N is increased, and the moisture evaporated from the high humidity raw material Mw by the fluidized gas N is increased. More can be taken away and drying is promoted more. The steam supplied to the heating steam pipe 110 is used for heating the high-humidity raw material Mw, and then is supplied to the primary side of the fluidized gas heater 120 to heat the fluidized gas N by heat exchange.

The drying chamber 104 basically has a rectangular parallelepiped shape. The drying chamber partition wall 105 is arranged so as to cross the horizontal long side of the drying chamber 104. A raw material supply unit 101 for supplying a high-humidity raw material Mw is provided at one end in the long side direction of the rectangular parallelepiped drying chamber 104. A raw material discharge unit 102 for discharging the dried raw material Md is provided at an end of the drying chamber 104 opposite to the raw material supply unit 101 in the long side direction. When the high-humidity raw material Mw supplied from the raw material supply unit 101 moves in the drying chamber 104 while forming a fluidized bed and reaches the raw material discharge unit 102, it overflows from the upper part of the fluidized bed to the outside of the drying chamber 104. Is discharged to. The raw material discharge unit 102 is provided in the upper part of the drying chamber 104 in the vertical direction. The height of the fluidized bed of the high-humidity raw material Mw in the drying chamber 104 is determined by the position of the raw material discharge unit 102.

The high-humidity raw material Mw is supplied after being crushed in advance to a size suitable for fluidization in order to form a fluidized bed in the drying chamber 104. The crushed high-humidity raw material Mw is continuously supplied from the raw material supply unit 101 at a constant flow rate. The high-humidity raw material Mw supplied into the drying chamber 104 forms a fluidized bed in the drying chamber 104. The drying chamber 104 is divided into a plurality of compartments by the drying chamber partition wall 105, and fluidized gas N is supplied to each compartment from the bottom. An opening is provided in the lower part or the upper part of the drying chamber partition wall 105 so that the high-humidity raw material Mw can be sequentially moved to the adjacent section.

The drying chamber partition wall 105 is a flat plate that partitions the drying chamber 104. Since the fluidized gas N passes through, the upper part of the drying chamber 104 in the vertical direction is not partitioned by the drying chamber partition wall 105. The drying chamber partition wall 105 is installed so that the lower side of the drying chamber partition wall 105 in the vertical direction reaches the dispersion mechanism of the fluidized gas N that separates the fluidized gas air box 103 and the drying chamber 104. Since a passage for the high humidity raw material Mw to move is required, an opening is provided in the upper part or the lower part of the drying chamber partition wall 105. In the adjacent drying chamber partition walls 105, it is desirable that the openings are alternately arranged at the upper part and the lower part. However, the arrangement of the openings is not limited to this, and the arrangement of the openings is arbitrarily determined depending on the flow conditions of the high-humidity raw material Mw. When the position of the opening is on the lower side, the opening is formed by notching the portion of the drying chamber partition wall 105 in contact with the dispersion mechanism. When the position of the opening is on the upper side, the portion of the drying chamber partition wall 105 in contact with the dispersion mechanism is completely closed, a notch is provided on the upper side of the drying chamber partition wall 105, and the upper end of the drying chamber partition wall 105 is a fluidized bed. It will be near the top surface. The shape of the opening is not particularly limited as long as it does not hinder the movement of the high-humidity raw material Mw (a shape in which a fluidized bed of the high-humidity raw material Mw can be formed in the entire drying chamber 104). ..

The high-humidity raw material Mw supplied from the raw material supply section 101 is gradually dried while forming a fluidized bed in a plurality of sections provided in the drying chamber 104, and reaches the section provided with the raw material discharge section 102. In the meantime, drying proceeds to a predetermined water content. After that, the high-humidity raw material Mw dried to a predetermined water content is discharged from the raw material discharge unit 102 as a dry raw material Md to the outside of the drying chamber 104 by overflow.

The pressure inside the drying chamber 104 is approximately atmospheric pressure. In order to promote the evaporation of water from the high humidity raw material Mw, the temperature in the drying chamber 104 is controlled so as to sufficiently exceed 100 ° C. Since many of the high-humidity raw materials Mw have the property of easily spontaneously igniting as the drying progresses, such as biomass and lignite, it is not preferable that the fluidized gas N contains oxygen or the like having flammability. Therefore, the use of air as the fluidized gas N should be avoided, for example, the use of an inert gas as the fluidized gas N. Nitrogen is a typical example of an inert gas, but the cost of producing the gas becomes an issue for continuous use. In this embodiment, superheated steam (dry steam) is used as the fluidized gas N. However, when the drying system S is started, the temperature inside the drying chamber 104 may be 100 ° C. or lower, and water vapor may condense. Therefore, an inert gas such as nitrogen gas is used as the fluidized gas N until the temperature in the drying chamber 104 becomes sufficiently high.

The steam supply device 1B further includes an auxiliary superheater 9. The auxiliary superheater 9 is activated when the heat energy supply by the heat storage agent X2 is insufficient in the steam medium superheater section 8 and the superheat of the steam medium Z1s is insufficient, and superheated steam is generated in place of the steam medium superheater section 8. Supply.

In the present embodiment, the inside of the drying chamber 104 is divided into four sections, and after the high-humidity raw material Mw is supplied to the first section, the drying chamber partition wall 105 is moved in the order of upper side, lower side, and upper side. , It is configured to be discharged from the upper part of the most downstream section (fourth section). However, the number of compartments, the position where the high-humidity raw material Mw passes through the drying chamber partition wall 105 (upper side, lower side), and the like are arbitrarily set and are not limited to FIG.

According to the present embodiment, the steam medium Z1s, which is saturated steam obtained by heating the supply medium Z1 with the thermal energy obtained by condensing sunlight, and the superheated steam obtained by further heating the steam medium Z1s. A certain superheated steam medium Z2s is supplied to the drying device 100. As a result, the high-humidity raw material Mw can be continuously and stably dried even at night. When the superheated steam medium Z2s is directly supplied to the fluidized bed formed by the high-humidity raw material Mw for drying, the replenishment medium Z is used as water and the superheated steam medium Z2s is supplied as superheated steam (dry steam). May be done. As a result, the drying of the high-humidity raw material Mw proceeds in the atmosphere of dry steam, so that spontaneous combustion is prevented and the high-humidity raw material Mw can be safely dried.

Although the preferred embodiments of the present disclosure have been described above with reference to the drawings, the present disclosure is not limited to the above embodiments. The various shapes and combinations of the constituent members shown in the above-described embodiment are examples, and can be variously changed based on design requirements and the like without departing from the spirit of the present disclosure.

When the superheated steam medium Z2s, which is the superheated steam of the supply medium Z1 (replenishment medium Z), is directly supplied into the fluidized bed of the high humidity raw material Mw of the drying apparatus 100, it is preferable to use water as the replenishment medium Z. .. However, when the superheated steam medium Z2s is not directly supplied into the fluidized bed of the high humidity raw material Mw, a fluid other than water may be heated and supplied as the supply medium Z1 (replenishment medium Z).

Further, the shape of the condensing heat collector 2a is shown in FIGS. 2A and 2B, and the arrangement of the condensing heat collector 2a is shown in FIG. However, the shape of the condensing heat collector 2a is not limited to the above embodiment as long as it can condense sunlight to obtain heat energy and heat the heat storage agent X1 and the heat storage agent X2 to a predetermined temperature. The arrangement may be set arbitrarily.

In the drying system S of the fifth embodiment, saturated steam and superheated steam were supplied from the steam supply device 1B according to the third embodiment, but for simplification of the system, one heat storage agent circulation system was used. The steam supply device 1C according to the fourth embodiment capable of supplying both saturated steam and superheated steam may be used for the drying system S.

Further, in the drying system S, the medium supplied to the heating steam pipe 110 is mainly the superheated steam medium Z2s which is superheated steam, but the medium supplied to the heating steam pipe 110 is the steam medium Z1s which is saturated steam. May be good.

Further, the steam supply device heats the supply medium Z1 (replenishment medium Z) and supplies one kind of saturated steam (steam medium Z1s), or further adds one kind of saturated steam (steam medium Z1s) and saturated steam. The configuration is not limited to supplying one type of superheated steam (superheated steam medium Z2s) obtained by heating. For example, a second medium heating unit is provided separately from the medium heating unit 3, and a heat storage agent having a different operating range from the heat storage agent X1 is used as an independent second sunlight separate from the solar concentrating heat collection unit 2. The supply medium Z1 (replenishment medium Z) may be heated under different conditions by heating and supplying the heat by the condensing heat collecting unit. In this case, it is possible to supply the second saturated steam having a temperature and pressure condition different from that of the steam medium Z1s, and further to the application destination a second superheated steam medium having a temperature and pressure condition different from that of the superheated steam medium Z2s. ..

The present disclosure can be applied to a steam supply device that collects sunlight and uses it as a heat source.

1 Steam supply device 1A Steam supply device 1B Steam supply device 1C Steam supply device 2 Solar concentrating heat collector 2a Concentrating heat collector 2b Heat storage agent circulation pump 2c Purge gas supply device 2d Path switching valve 3 Medium heating unit 3a Heat storage agent Storage tank 3b Heat exchanger 3c Heat storage agent discharger 3d Stirrer 3e Auxiliary heater 3f Recovery heat storage agent transport pump 4 Steam supply unit 4a Steam drum 4b Auxiliary boiler 5 Medium circulation unit 5a Medium tank 5b Medium supply pump 5c Medium preheater 5d Pressure control valve 5e Medium condenser 6 Supply heat storage agent storage 6a Supply heat storage agent storage tank 6b Supply heat storage agent transfer pump 6c Stirrer 7 Recovery heat storage agent storage 7a Recovery heat storage agent storage tank 7b Recovery heat storage agent discharger 7c Recovery heat storage agent Stirrer 7d Recovery heat storage agent Auxiliary heater 8 Steam medium overheating part (steam heating part)
8a Heat storage agent storage tank for overheating 8b Heat exchanger for overheating 8c Heat storage agent for overheating discharger 8d Stirrer 9 Auxiliary heater 100 Drying device 101 Raw material supply part 102 Raw material discharge part 103 Fluidized gas air box 104 Drying room 105 Drying room Partition 110 Heating steam tube 111 Superheated steam pressure reducing valve 112 Atmospheric release valve 113 Dust remover 120 Fluidized gas heater 130 Fluidized gas blower 200 Condensing heat collector 210 Condensing heating unit 211 Main condensing mirror 212 Sub condensing mirror 213 Connection bracket 214 Fluid heating tube 220 Support device 221 Main pillar 222 Direction angle adjustment device 223 Elevation angle adjustment device 230 Condensing heat collection zone Md Drying raw material Mw High humidity raw material N Fluidized gas P Inactive gas R Circulating gas S Drying system X1 Heat storage Agent X2 Heat storage agent for overheating (second heat storage agent)
Z Replenishment medium Z1 Supply medium Z1s Steam medium Z2s Superheated steam medium

Claims (11)

A solar concentrating heat collecting unit that collects and collects sunlight and directly heats the heat storage agent,
A medium heating unit that heats the supply medium with the heated heat storage agent, and
A steam supply unit that separates and supplies steam from the heated supply medium,
A steam supply device equipped with. A supply heat storage agent storage unit provided in front of the medium heating unit and storing the heat storage agent heated by the solar condensing heat collection unit, and a heat storage agent storage unit.
A recovery heat storage agent storage unit provided after the medium heating unit and storing the heat storage agent used for heating the supply medium, and a recovery heat storage agent storage unit.
The steam supply device according to claim 1, further comprising. During the time when sunlight cannot be obtained, the supply of the heat storage agent to the solar concentrating heat storage unit is stopped, and the heat storage agent staying in the solar concentrating heat storage unit is stored in the supply heat storage agent. The steam supply device according to claim 2, further comprising a heat storage agent evacuation mechanism for retracting the heat storage agent to the unit or the recovery heat storage agent storage unit. A second solar concentrating heat collecting unit that condenses and collects sunlight and directly heats the second heat storage agent,
A steam heating unit that further heats the steam supplied from the steam supply unit by the heated second heat storage agent, and a steam heating unit.
The steam supply device according to any one of claims 1 to 3. The steam supply device according to claim 4, wherein the steam supplied by the steam heating unit is superheated steam. The steam supply device according to claim 4 or 5, wherein the operating temperature of the second heat storage agent is higher than the operating temperature of the heat storage agent used for heating the supply medium. The steam supply device according to claim 4 or 5, wherein in the steam heating unit, the second heat storage agent used for heating the steam supplied from the steam supply unit is used for heating the supply medium. The steam supply device according to any one of claims 1 to 7, further comprising an auxiliary boiler for heating the supply medium. The steam supply device according to any one of claims 1 to 8, further comprising an auxiliary superheater for heating the steam supplied from the steam supply unit. The steam supply device according to any one of claims 1 to 9, wherein a stirring device for stirring the heat storage agent is provided in the heat storage agent storage tank for storing the heat storage agent. The steam supply device according to any one of claims 1 to 10.
A fluidized bed drying device that uses the steam supplied from the steam supply device as a heat source to dry the high-humidity raw material while flowing it.
A drying system equipped with.

Images