JP2013133766A - Solar energy gas turbine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a solar energy gas turbine capable of improving efficiency of power generation by leveling a temperature change of a heat medium caused by variation in an amount of solar radiation.SOLUTION: A solar energy gas turbine includes: a heat receiver 10 irradiated with sunlight to receive heat and having a heat receiving tube with compressed air WA circulated therein; a compressor 12 for compressing air and supplying the compressed air to the heat receiving tube; a turbine 11 rotationally driven by the compressed air WA heated by the heat receiver 10; turbine air supply piping 21 for taking out the compressed air WA heated by the heat receiver 10 and supplying the air to the turbine 11; and a heat reservoir 24 provided at an outer peripheral side of the turbine air supply piping 21 and for storing heat from the turbine air supply piping 21 or radiating heat to the turbine air supply piping 21 in accordance with a temperature difference between the heat reservoir and the turbine air supply piping 21.

Description

  The present invention relates to a solar gas turbine that uses heat energy obtained by collecting sunlight to drive a turbine to generate power.

  2. Description of the Related Art In recent years, solar thermal power generation facilities that generate power by converting thermal energy obtained by concentrating sunlight into electrical energy using, for example, a gas turbine, have been developed as environmentally friendly clean energy. As this solar thermal power generation facility, those using various methods such as a trough method, a tower method, and a beam down method are known.

  The trough method reflects sunlight by a semi-cylindrical reflector (trough), collects and collects heat on a pipe that passes through the center of the cylinder, and raises the temperature of the heat medium that passes through the pipe to obtain thermal energy. Is. And the tower system is a heat receiving pipe inside a heat receiver installed in the upper part of the tower by reflecting sunlight by a plurality of heliostats (for example, see Patent Documents 1 and 2) composed of reflecting mirrors provided on the ground. The solar light is intensively irradiated to heat a heat medium such as air or water that circulates in the heat receiving tube to obtain thermal energy. Furthermore, the beam-down method, like the tower method, reflects sunlight by a plurality of heliostats composed of reflecting mirrors provided on the ground. The reflected sunlight is reflected again by the secondary reflection mirror at the top of the tower. The heat energy is obtained by condensing on the ground and heating the heat medium.

  Each of these methods has advantages, but the trough method uses uniaxial control that changes the direction of the reflector so that it tracks the sun rays, and the reflector can only be adjusted in a two-dimensional direction. Is about 550 ° C. at the maximum, and so high heat collecting effect cannot be expected. Therefore, the tower method capable of controlling the reflecting mirror in three dimensions is advantageous as the heat collection efficiency. In addition, the beam down method has problems of heat resistance and cost of the secondary reflection mirror, and the tower method is more advantageous from these viewpoints. Furthermore, in the tower method, when the heat medium is air rather than when the heat medium is water, the heat medium can be heated to about 900 ° C. of the heat resistance temperature of the heat receiving pipe in the heat receiver. Higher heat collection efficiency can be expected when air is used as the heat medium.

JP 2002-98416 A JP-A-9-280664

  However, even with the tower system with relatively high heat collection efficiency as described above, the amount of solar radiation depends on the weather, so it fluctuates from day to day, and the heat collection efficiency fluctuates accordingly. To do. Furthermore, as shown in FIG. 5, even if the solar radiation is temporarily blocked by the clouds and the solar radiation amount suddenly decreases and then the solar radiation amount suddenly rises, the solar heat collecting equipment is completely affected by fluctuations in the solar radiation amount. Cannot be followed, and a time loss occurs until the power generation recovers. Therefore, the total amount of power generation throughout the day is reduced, and the capacity of the solar thermal power generation facility cannot be fully utilized, leading to a decrease in power generation efficiency.

  And, for example, if the capacity of the solar heat collection facility (the area of the heliostat, the heat resistance of the heat receiver, etc.) is set according to the state of maximum solar radiation in one day, in other time zones Since the amount of solar radiation does not reach the maximum amount of solar radiation, the capacity of the solar thermal power generation facility cannot be fully utilized, resulting in over-specification and reducing power generation efficiency.

  On the other hand, if the capacity of the solar thermal power generation facility is set in accordance with the state of standard solar radiation throughout the day, it may exceed the standard solar radiation in other time zones. For this reason, it is necessary to reduce the operation rate by thinning out the heliostat or the like, and the power generation efficiency is also lowered including the equipment cost.

  The present invention has been made in view of such circumstances, and an object of the present invention is to provide a solar gas turbine capable of leveling the temperature change of the heat medium due to fluctuations in the amount of solar radiation and improving the power generation efficiency. .

In order to solve the above problems, the present invention employs the following means.
That is, the solar gas turbine according to the present invention receives heat by receiving sunlight and receives a heat and has a heat receiving pipe through which the heat medium flows, and a compression for compressing the heat medium and supplying the heat receiving pipe to the heat receiving pipe A turbine that is rotationally driven by the heat medium heated by the heat receiver,
A turbine heat medium supply pipe that takes out the heat medium heated by the heat receiver and supplies the heat medium to the turbine, and an outer peripheral side of the turbine heat medium supply pipe. And a heat storage body that stores heat from the turbine heat medium supply pipe or radiates heat to the turbine heat medium supply pipe.

  According to such a solar thermal gas turbine, the heat medium compressed by the compressor is supplied to the heat receiving pipe in the heat receiver, and is heated by the heat energy of sunlight. The heated heat medium is supplied to the turbine through the turbine heat medium supply pipe. When the heat medium flows through the turbine heat medium supply pipe, heat exchange is performed with the heat storage body. That is, when the amount of sunlight irradiated on the heat receiving pipe increases and the temperature of the heat medium flowing through the turbine heat medium supply pipe is relatively high, heat is stored in the heat storage body, and the amount of solar radiation decreases. In the case where the temperature of the heat medium is relatively low due to the decrease in the irradiation amount due to the heat dissipation, the heat is released to the heat storage body. Accordingly, it is possible to level the temperature of the heat medium.

  The solar gas turbine according to the present invention includes a cylindrical support tower that is erected on a support base surface and is provided with the heat receiver at an upper portion thereof, and the heat storage body and the turbine are provided inside the support tower. A heat medium supply pipe may be arranged.

  Since the heat storage body and the turbine heat medium supply pipe are arranged on the support tower, it is not necessary to separately provide a space for arranging the heat storage body and the turbine heat medium supply pipe, and space saving can be achieved.

  Furthermore, the exhaust gas discharged | emitted from the said turbine may distribute | circulate, and you may provide the discharge piping distribute | arranged to the outer peripheral side of the said thermal storage body.

  Thus, the exhaust heat of the exhaust gas can be stored in the heat storage body through the discharge pipe, and heat radiation from the heat storage body to the outside can be suppressed. Therefore, the exhaust heat can be reused without separately providing a heat exchange facility for exchanging the exhaust heat of the exhaust gas, and the power generation efficiency can be further improved while saving space and cost.

  The heat medium compressed by the compressor may be supplied to the heat receiver, and a heat receiver heat medium supply pipe arranged on the outer peripheral side of the discharge pipe may be provided.

  The heat receiver heat medium supply pipe supplies the heat medium to the heat receiver, exchanges heat with the discharge pipe, and collects exhaust heat and suppresses heat radiation from the discharge pipe to the outside. This can further improve the power generation efficiency.

  Further, the discharge pipe and the heat receiver heat medium supply pipe may be arranged coaxially with the central axis of the support tower and may have an annular shape when viewed in the central axis direction.

  By forming an annular shape, it is possible to arrange exhaust pipes and heat receiver heat medium supply pipes in the support tower, and it is possible to reliably achieve reuse of exhaust heat and suppression of heat radiation from the exhaust pipe to the outside. Efficiency can be improved.

  A plurality of the discharge pipes are arranged in a cylindrical shape at the same distance in the radial direction of the central axis of the support tower and spaced apart from each other in the circumferential direction of the central axis. The pipes may be arranged so as to cover the outer peripheral side of each of these discharge pipes in an annular shape.

  A heat receiver heat medium supply pipe covers the outer peripheral side of each cylindrical discharge pipe. That is, the discharge pipe and the heat receiver heat medium supply pipe form a cylindrical shape as a whole to form a heat medium flow path, and a plurality of the flow paths are provided at intervals in the circumferential direction of the central axis. Will be. Accordingly, since each of the flow passages can be formed with a small diameter, the thickness can be reduced while maintaining the pressure resistance performance. For this reason, the heat transfer effect of the heat medium can be improved, and the power generation efficiency can be further improved.

  Furthermore, you may further provide the outer side heat storage body distribute | arranged to the outer peripheral side of the said heat receiver heat carrier supply piping.

  In this way, heat is exchanged between the heat storage medium and the heat medium flowing through the turbine heat medium supply pipe by the heat storage body, the temperature of the heat medium is leveled, and heat radiation from the heat medium to the outside is suppressed by the outer heat storage body. The effect can be improved, and the power generation efficiency can be further improved.

  According to the solar heat gas turbine of the present invention, the heat input / radiation between the turbine heat medium supply pipe and the heat storage body can equalize the temperature change of the heat medium due to the fluctuation of the amount of solar radiation and improve the power generation efficiency. .

It is the whole schematic figure which looked at the solar thermal gas turbine concerning a first embodiment of the present invention from the side. It is a side view which shows typically the mode of the heat carrier distribution in a tower about the solar thermal gas turbine concerning a first embodiment of the present invention. It is a figure which shows the cross section of a tower regarding the solar gas turbine which concerns on 1st embodiment of this invention, Comprising: (a) is an AA cross section of FIG. 2, (b) is a BB cross section of FIG. ) Shows the CC cross section of FIG. It is a figure which shows the cross section of a tower regarding the solar gas turbine which concerns on 2nd embodiment of this invention, Comprising: (a) is the same position as the AA cross section of FIG. 2, (b) is the BB cross section of FIG. (C) shows the same position as the CC cross section of FIG. It is the graph which illustrated the relationship between the time of a day, solar radiation amount, and electric power generation amount.

Hereinafter, the solar gas turbine 1 according to the embodiment of the present invention will be described.
The solar thermal gas turbine 1 is a power generation facility that generates power by collecting sunlight WL to obtain thermal energy and converting the thermal energy into electric energy by the gas turbine 2.

  As shown in FIG. 1, the solar gas turbine 1 includes a heat receiver 10 that is irradiated with sunlight WL, and a tower (support tower) that is erected from the ground (support base surface) and fixed to the upper part. 4, a plurality of heliostats 3 that reflect sunlight WL and irradiate the heat receiver 10, a gas turbine 2 connected to the heat receiver 10 via an air circulation part 5 inside the tower, and power generation by the gas turbine 2 And a generator 13 to be used.

  The gas turbine 2 is provided on the ground and compresses air taken from outside to generate compressed air (heat medium) WA, and is supplied from the compressor 12 to the heat receiver 10 through the air circulation unit 5. And a turbine 11 that is rotationally driven by the heated compressed air WA.

  The heliostat 3 includes a reflecting mirror 3a that reflects sunlight WL and a support leg 3b that supports the reflecting mirror 3a. The plurality of heliostats 3 are arranged in a scattered manner on a heliostat field G that extends around the tower 4 so as to surround the entire 360 ° circumference of the tower 4.

  As shown in FIG. 2, the tower 4 is a support structure having a cylindrical shape centering on an axis P standing upward from the ground at the center of the heliostat field G. A vessel 10 is provided, and an air circulation part 5 is provided therein.

  The heat receiver 10 is provided in the upper part of the tower 4 and has a heat receiving pipe (not shown) through which the compressed air WA flows. The heat receiving pipe is irradiated with sunlight reflected by the heliostat 3, Compressed air WA that circulates is heated.

Next, the air circulation unit 5 will be described.
As shown in FIG. 3, the air circulation unit 5 is provided inside the tower 4, and includes a turbine air supply pipe (turbine heat medium supply pipe) 21 disposed in the center of the tower 4, and a turbine air supply pipe 21. A heat storage body 24 provided on the outer peripheral side, a discharge pipe 22 disposed on the outer peripheral side of the heat storage body 24, and a heat receiver air supply pipe (heat receiver heat medium supply pipe) 20 disposed on the outer peripheral side of the discharge pipe 22. And the outer side heat storage body 25 distribute | arranged to the outer peripheral side of the heat receiver air supply piping 20, and the outer cylinder 23 which covers the outer peripheral side of the outer side heat storage body 25 are provided.

  The turbine air supply pipe 21 is a cylindrical member that is arranged coaxially with the axis P at the center of the tower 4 and connects the heat receiver 10 and the turbine 11. Then, the compressed air WA can flow from the heat receiver 10 toward the turbine 11.

  The heat storage body 24 is arranged in an annular shape so as to cover the outer peripheral side of the turbine air supply pipe 21, and is made of a heat storage material having a large heat capacity, for example, a refractory brick, and the turbine air supply pipe 21 through the turbine air supply pipe 21. Heat exchange is performed with the compressed air WA that circulates, and heat storage or heat dissipation is enabled by a relative temperature difference.

  The discharge pipe 22 is arranged coaxially with the axis P so as to cover the outer peripheral side of the heat storage body 24 in an annular shape, and communicates the turbine 11 and the outside of the outer cylinder 23. Then, the exhaust E from the turbine 11 circulates inside, and the exhaust E can be discharged to the outside of the tower 4.

  The heat receiver air supply pipe 20 is arranged coaxially with the axis P so as to cover the outer peripheral side of the heat storage body 24 in an annular shape, and connects the compressor 12 and the heat receiver 10. The compressed air WA can flow from the compressor 12 toward the heat receiver 10.

  The outer heat storage body 25 is a member that is provided so as to cover the outer peripheral side of the heat receiver air supply pipe 20 in an annular shape and can suppress heat radiation to the outside. And this outer side heat storage body 25 may use heat storage materials, such as a refractory brick, like heat storage body 24 with large heat capacity, for example, and may use the heat insulation which has heat resistance, the ceramic fiber etc. which are heat insulation materials. .

  The outer cylinder 23 is a cylindrical member made of iron or the like that covers the outer peripheral side of the outer heat storage body 25, and forms the outer shape of the tower 4.

  In such a solar thermal gas turbine 1, the compressed air WA generated by being compressed by the compressor 12 is supplied to the heat receiving pipe in the heat receiver 10 through the heat receiver air supply pipe 20, and circulates inside the heat receiving pipe. It is heated by the thermal energy of sunlight WL irradiated to the heat receiving tube. The heated compressed air WA is supplied to the turbine 11 through the turbine air supply pipe 21.

  Here, in the heat receiver 10, the irradiation amount of sunlight WL fluctuates within one day as the heating amount of the compressed air WA according to the fluctuation of the solar irradiation amount. For this reason, the heating amount of the compressed air WA in the heat receiver 10 varies, and the temperature of the compressed air WA varies.

  In this respect, since the heat storage body 24 is disposed on the outer peripheral side of the turbine air supply pipe 21, heat exchange is possible between the compressed air WA flowing through the turbine air supply pipe 21 and the heat storage body 24. It becomes.

  That is, when the irradiation amount of sunlight WL to the heat receiving pipe is increased and the temperature of the compressed air WA flowing through the turbine air supply pipe 21 is relatively high during the day, the turbine air supply pipe Heat storage to the heat storage body 24 is performed by a temperature difference between the heat storage body 24 and the heat storage body 24. Since the heat storage body 24 has a large heat capacity as described above, the heat storage body 24 stores heat for a time during which the temperature of the compressed air WA is relatively high during the day, and thereby the temperature of the compressed air WA flowing through the turbine air supply pipe 21. Can be lowered.

  On the other hand, when the temperature of the compressed air WA flowing through the turbine air supply pipe 21 is relatively low during the day, the turbine air supply pipe is reduced due to a decrease in the amount of sunlight WL applied to the heat receiving pipe. Heat release to the heat storage body 24 is performed by a temperature difference between the heat storage body 24 and the heat storage body 24. Similarly, since the heat storage body 24 has a large heat capacity, the heat storage body 24 radiates heat during the day when the temperature of the compressed air WA is relatively low, thereby reducing the temperature of the compressed air WA flowing through the turbine air supply pipe 21. Can be raised.

  In this way, the temperature of the compressed air WA flowing through the turbine air supply pipe 21 can be leveled.

  Since the compressed air WA whose temperature is leveled in this way is supplied to the turbine 11, for example, even if the solar radiation is blocked by clouds or the like, and the solar radiation amount suddenly decreases, the power generation amount decreases. There is no end. Further, it is possible to avoid a decrease in power generation efficiency due to a time loss until the power generation amount recovers when the solar radiation amount suddenly increases after such a decrease in the solar radiation amount.

  Further, the heat storage body 24 can similarly cope with fluctuations in the amount of solar radiation within a day. The temperature of the compressed air WA is leveled, and the compressed air WA in a temperature range that matches the specifications of the turbine 11 can be obtained. Supplying to the turbine 11 makes it possible to always operate the turbine 11 in an optimum state.

  Then, the compressed air WA supplied to the turbine 11 is rotated and driven by the turbine 11 to generate power by the generator, and then becomes exhaust E and flows into the exhaust pipe 22. The exhaust pipe 22 is connected to the outer periphery of the heat storage body 24. Since the side is covered, the exhaust heat of the exhaust gas can be stored in the heat storage body 24 through the discharge pipe 22, and heat radiation from the heat storage body 24 to the outside of the tower 4 can be suppressed. Therefore, the exhaust heat can be reused without separately providing a heat exchange facility for exchanging the exhaust heat of the exhaust gas E, and the cost due to space saving can be suppressed.

  Further, since the heat receiver air supply pipe 20 covers the outer peripheral side of the discharge pipe 22, heat exchange with the discharge pipe 22 is possible, and the exhaust heat of the exhaust E in the discharge pipe 22 can be recovered. In addition, heat radiation from the discharge pipe 22 to the outside of the tower 4 can be suppressed.

  Moreover, since the outer side heat storage body 25 is provided in the outer peripheral side of the heat receiver air supply piping 20, the outer side heat storage body 25 can further improve the heat radiation suppression effect to the outside of the tower 4.

  And since these heat receiver air supply piping 20, turbine air supply piping 21, discharge piping 22, the heat storage body 24, and the outer side heat storage body 25 are provided in the inside of the tower 4, it is necessary to provide the space which arrange | positions these separately. Eliminates and can save space.

  According to the solar gas turbine 1 of the present embodiment, the temperature of the compressed air WA can be leveled by the heat storage body 24 regardless of variations in the amount of solar radiation, and the turbine 11 can always be operated in an almost optimal state. It is possible to improve.

  Further, the heat receiver air supply pipe 20, the turbine air supply pipe 21, the discharge pipe 22, the heat storage body 24, and the outer heat storage body 25 are arranged inside the tower 4 to recover the exhaust heat of the exhaust E, At the same time, heat radiation to the outside of the tower 4 can be suppressed, and further, power generation efficiency can be improved and cost reduction by space saving can be achieved.

Next, a solar gas turbine according to the second embodiment of the present invention will be described.
In addition, the same code | symbol is attached | subjected to the component similar to 1st embodiment, and detailed description is abbreviate | omitted.
In the present embodiment, the shapes of the discharge pipe 42 and the heat receiver air supply pipe 40 in the air circulation part 35 inside the tower 4 are different from those in the first embodiment.

  As shown in FIG. 4, in the present embodiment, the discharge pipe 42 is a cylindrical member. In addition, a plurality of the exhaust pipes 42 are arranged on the outer peripheral side of the heat storage body 24 in a ring shape with the axis P as a center at a predetermined interval. And the exhaust E from the turbine 11 distribute | circulates the inside like the discharge piping 42 of 1st embodiment, and it enables it to discharge | emit the exhaust E to the exterior of the tower 4. FIG.

  Further, as shown in FIG. 4 (c), the height direction position of the tower 4 where the exhaust E flows from the turbine 11 to the exhaust pipe 42 is formed in an annular shape with the axis P as the center. A communication portion 42a is formed which is connected to and communicates with each of a plurality of discharge pipes 42 arranged in a ring shape as a diameter, and the exhaust E is distributed to each discharge pipe 42 so as to be circulated.

  Further, as shown in FIG. 4A, the height direction position of the tower 4 from which the exhaust E is discharged from the discharge pipe 42 to the outside of the tower 4 is similarly formed in an annular shape around the axis P. A communication portion 42b that is connected to and communicates with each of the plurality of discharge pipes 42 arranged in a ring shape around P is formed, and the exhaust E that flows through each of the discharge pipes 42 can be joined and discharged.

  The heat receiver air supply pipe 40 is arranged so as to cover the outer peripheral side of each discharge pipe 42 in an annular shape, and is centered on the central axis of each discharge pipe 42 when viewed from the direction of the axis P. And like the heat receiver air supply piping 40 of the first embodiment, the compressed air WA can flow from the compressor 12 toward the heat receiver 10 inside.

  Further, as shown in FIG. 4 (c), the height direction position of the tower 4 where the compressed air WA flows from the compressor 12 to the heat receiver air supply pipe 40 is formed in an annular shape around the axis P. A communication portion 40a is formed which is connected to and communicates with each of the heat receiver air supply pipes 40 arranged in a ring shape around P, and the compressed air WA can be distributed and distributed to each of the heat receiver air supply pipes 40. It is said.

  Further, as shown in FIG. 4A, the height direction position of the tower 4 where the compressed air WA is supplied from the heat receiver air supply pipe 40 to the heat receiver 10 is similarly formed in an annular shape around the axis P. A communication portion 40b that is connected to and communicates with each of the heat receiver air supply pipes 40 arranged in a ring shape around the axis P is formed, and the compressed air WA that flows through each of the heat receiver air supply pipes 40 is formed. It can be supplied by joining.

  In such a solar gas turbine, the compressed air WA generated by being compressed by the compressor 12 is supplied to the heat receiver 10 through the heat receiver air supply pipe 40 and heated. The heated compressed air WA is supplied to the turbine 11 through the turbine air supply pipe 21.

  And when compressed air WA distribute | circulates the turbine air supply piping 21, this thermal storage body 24 can heat-store and heat-radiate similarly to 1st embodiment, and it becomes possible to achieve the leveling of the temperature of compressed air WA. .

  Further, the exhaust pipe 42 and the heat receiver air supply pipe 40 cover the outer peripheral side of each cylindrical discharge pipe 42 with the heat receiver air supply pipe 40. That is, the discharge pipes 42 and the heat receiver air supply pipes 40 are formed in a cylindrical shape as a whole and are arranged in the circumferential direction of the axis P. For this reason, each discharge pipe 42 and the heat receiver air supply pipe 40 can be formed in a small diameter, and the thickness can be reduced while maintaining the pressure resistance performance, and the heat transfer effect of the compressed air WA can be improved. .

  Therefore, heat exchange between the heat storage body 24 and the heat receiver air supply pipe 40, between the heat receiver air supply pipe 40 and the discharge pipe 42, and between the heat receiver air supply pipe 40 and the outer heat storage body 25 is smoothly performed. Therefore, the temperature of the compressed air WA can be further leveled and the exhaust heat of the exhaust E can be recovered.

  According to the solar gas turbine of this embodiment, the temperature of the compressed air WA can be leveled by the heat accumulator 24 regardless of variations in the amount of solar radiation, and the turbine 11 can always be operated in an almost optimal state. The heat transfer effect of the compressed air WA can be improved by the small-diameter discharge pipes 42 and the heat receiver air supply pipes 40 provided in the circumferential direction. Therefore, the power generation efficiency can be further improved.

Although the embodiment of the present invention has been described in detail above, some design changes can be made without departing from the technical idea of the present invention.
For example, in the above-described embodiment, the heat receiver air supply pipes 20 and 40 are disposed on the outer peripheral side of the discharge pipes 22 and 42, but conversely, the discharge pipe 22 is disposed on the outer peripheral side of the heat receiver air supply pipes 20 and 40. , 42 may be arranged. In this case, since the exhaust E in the discharge pipes 22 and 42 has a higher temperature than the compressed air WA in the heat receiver air supply pipes 20 and 40, it is possible to further suppress heat radiation from the tower 4 to the outside. More preferred.

  In the above-described embodiment, the exhaust pipes 22 and 42 are communicated with the outside of the tower 4 to exhaust the exhaust E. For example, even if a part of the exhaust E is recirculated to the heat receiver 10, the exhaust E is exhausted. Since the pipes 22 and 42 are arranged in the tower 4, the flow volume of the exhaust E can be sufficiently secured. For this reason, the operating efficiency of the turbine 11 is not lowered, and the exhaust heat is recirculated in this way, so that the exhaust heat can be used more effectively and the power generation efficiency can be improved.

DESCRIPTION OF SYMBOLS 1 ... Solar thermal gas turbine 2 ... Gas turbine 3 ... Heliostat 3a ... Reflector 3b ... Support leg 4 ... Tower 5 ... Air distribution part 10 ... Heat receiver 11 ... Turbine 12 ... Compressor 13 ... Generator 20 ... Heat receiver air supply Pipe (heat receiver heat medium supply pipe) 21 ... Turbine air supply pipe (turbine heat medium supply pipe) 22 ... Discharge pipe 23 ... Outer cylinder 24 ... Heat storage body 25 ... Outer heat storage body 35 ... Air circulation part 40 ... Heat receiver air supply Piping 40a, 40b ... Communication portion 42 ... Exhaust piping 42a, 42b ... Communication portion WA ... Compressed air P ... Axis G ... Heliostat field WL ... Sunlight E ... Exhaust

Claims (7)

A heat receiver having a heat receiving pipe through which a heat medium flows while receiving heat by receiving sunlight; and
A compressor that compresses the heat medium and supplies the heat medium to the heat receiving pipe;
A turbine that is rotationally driven by the heat medium heated by the heat receiver;
A turbine heat medium supply pipe that takes out the heat medium heated by the heat receiver and supplies the heat medium to the turbine;
It is provided on the outer peripheral side of the turbine heat medium supply pipe and stores heat from the turbine heat medium supply pipe or dissipates heat to the turbine heat medium supply pipe due to a temperature difference between the turbine heat medium supply pipe and the turbine heat medium supply pipe. The solar-heat gas turbine characterized by including the thermal storage body to perform. Standing on the support base surface, comprising a cylindrical support tower provided with the heat receiver on the upper part,
The solar thermal gas turbine according to claim 1, wherein the heat storage body and the turbine heat medium supply pipe are arranged inside the support tower.   3. The solar gas turbine according to claim 2, wherein exhaust gas discharged from the turbine circulates and includes an exhaust pipe disposed on an outer peripheral side of the heat storage body. 4.   4. The solar gas turbine according to claim 3, further comprising a heat receiver heat medium supply pipe arranged on an outer peripheral side of the discharge pipe for supplying the heat medium compressed by the compressor to the heat receiver. .   The solar gas turbine according to claim 4, wherein the discharge pipe and the heat receiver heat medium supply pipe are arranged coaxially with a central axis of the support tower and have an annular shape when viewed from the central axis direction. A plurality of the discharge pipes are arranged at intervals in the circumferential direction of the central axis at positions that are cylindrical and have the same distance in the radial direction of the central axis of the support tower,
The solar heat gas turbine according to claim 4, wherein the heat receiver heat medium supply pipe is arranged so as to annularly cover the outer peripheral side of each of the discharge pipes.   The solar thermal gas turbine according to any one of claims 4 to 6, further comprising an outer heat storage body disposed on an outer peripheral side of the heat receiver heat medium supply pipe.

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