JP2008088957A - Steam turbine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve the efficiency of a steam turbine to attain miniaturization by further increasing a jet speed from a nozzle to increase impulse force and viscous force. <P>SOLUTION: A heating surface 12 of a heat pump type heating means 13 is disposed between the nozzle 1 and a blade 3. Steam jetted from the nozzle 1 is thereby heated to a high temperature by the heating surface 12. Consequently, the steam enters a blade 3 at higher speed, which results in increasing impulse force to the blade 3 to increase torque of the turbine, that is, rotational torque generated by the same amount of steam is increased to improve efficiency as the steam turbine, and the steam turbine can be miniaturized and simplified. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a steam turbine mounted on a Rankine system using solar heat.

  Conventionally, in this type of steam turbine, the steam ejected from the nozzle flows from the outer periphery toward the shaft through a flat disk shape that is densely attached to the output shaft at narrow intervals. The disk is rotated (for example, see Patent Document 1).

There is also a Tesla turbine that uses only a viscosity using a flat disk.
JP 2002-174166 A

  However, in the prior art, high-pressure steam is guided to a tapered nozzle, a divergent nozzle, etc., and momentum is generated to make a high-speed flow. The steam flow is applied to a large number of rotating disks to generate torque, but the steam generated from the nozzle expands in an adiabatic state and thus becomes very low temperature (for example, from a pressure of 0.4 Mpa using air). At atmospheric pressure, -76 ° C).

  Therefore, as shown in the boiled charles, the volume contracted and did not increase to a sufficient speed. For this reason, the momentum obtained by mass × speed = becomes small, and there is a problem that the maximum output of the turbine output generated by the steam cannot be obtained.

  The present invention solves the above-described conventional problems and aims to improve the efficiency of a steam turbine.

  In order to solve the above-described conventional problems, a steam turbine according to the present invention includes a nozzle configured to superimpose a nozzle that ejects steam, and a plurality of blades that guide steam ejected from the nozzle, and the nozzle and the blade. And a casing which includes a rotating shaft of the blade and forms an inlet and an outlet for steam, and a heating means is added to the nozzle.

  As a result, the steam ejected from the nozzle can be heated by the heating means, the speed of the steam is accelerated by increasing its volume, and the impetus to the blades increases because the speed increases and enters the blades. The rotational torque generated by the amount increases, and the efficiency of the steam turbine is improved.

  In the steam turbine of the present invention, the temperature of the steam that has been lowered by adiabatic expansion ejected from the nozzle can be increased by the heating means. For this reason, the volume of the steam increases, and the steam flow velocity obtained by dividing the volume by the passage area becomes high speed. Therefore, the momentum increases and the torque applied to the turbine increases, so that the output of the steam turbine increases and the turbine performance for converting steam to driving force is improved, and the steam turbine can be made compact and simplified.

According to a first aspect of the present invention, there is provided a nozzle configured to superimpose a nozzle for ejecting steam, a plurality of blades for guiding steam ejected from the nozzle, the nozzle, the blade, and a rotating shaft of the blade, A casing having an inlet and an outlet was provided, and heating means for heating the steam ejected from the nozzle was disposed between the nozzle and the blade.

  Therefore, the steam ejected from the nozzle can be heated to high temperature by the heating means, and the steam flow rate is further increased because the volume of the steam is increased. Therefore, the torque applied to the blades of the turbine is increased, the output of the steam turbine is increased, and the turbine performance for converting steam into driving force is improved.

  That is, in order to rotate the blades of the turbine by converting the pressure to speed, to obtain the momentum from the high pressure to the low pressure with the nozzle, even if the steam that is as hot as possible is spouted from the nozzle, Since the generated steam expands in an adiabatic state, the temperature is very low (for example, −76 ° C. when the pressure is changed from 0.4 Mpa to atmospheric pressure using air).

  Therefore, the volume contracts as shown by the boiled charles and enters the blades at a speed corresponding to the volume reduction. Therefore, the momentum obtained by mass × speed = is small, and the turbine output generated by the steam is also small.

  Therefore, the temperature is lowered by adiabatic expansion, and the steam ejected from the nozzle at a high speed is heated by the heating means to make the temperature higher. Heating increases the volume of the steam, and the steam flow rate divided by the passage area is faster. Therefore, the momentum represented by the flow rate × speed increases, the torque applied to the turbine increases, the output of the steam turbine increases, and the turbine performance for converting steam to driving force is improved. Then, the improved performance can be used to make the steam turbine compact and simple.

  In the second aspect of the invention, in particular, the nozzle of the first aspect of the invention is constituted by a throttle part, a throat part, and a diffuser part, and the heating surface of the heating means is constituted by the diffuser part. Heating without interruption is possible, and the steam flow rate can be maximized, leading to the blades, and the turbine output can be increased.

  That is, the high-pressure steam flows from the throttle part to the throat part, and the flow rate is increased by significantly reducing the cross-sectional area of the flow path. At this time, the steam enters an adiabatic compression state and the temperature of the steam rises. Thereafter, the cross-sectional area of the flow path is gradually increased at the diffuser portion to lower the static pressure and further increase the dynamic pressure to increase the flow velocity. However, the steam becomes a very low temperature in the adiabatic expansion state.

  By heating the steam by supplying heat from the heating surface, it is possible to increase the speed while maintaining the temperature without once decreasing the temperature of the steam.

  In addition, the distance between the heating surface and the steam is short, and heat transfer is easy to the center of the steam. Therefore, the temperature difference between the heating surface and the steam is reduced, and the temperature of the steam is uniformly high, so the volume of the steam is maximized, the momentum represented by the flow rate x speed is increased, and the torque applied to the turbine is increased. The output of the steam turbine is increased, and the performance of the turbine that converts steam into driving force is improved.

  Furthermore, since the steam flow rate is high in the diffuser and the heating surface and the steam exchange heat easily, the heating device can be made small.

  The third invention, in particular, as the heating means of the first or second invention, comprises a heat exchanger that exchanges heat with atmospheric air outside the steam turbine, a heat transfer unit that transfers this heat, and a heating surface, It was set as the structure heated from the said heating surface.

This makes it easy to receive heat. That is, the heating means for heating the steam receives the amount of heat for heating the steam ejected from the nozzle from the ambient air outside the turbine by the heat exchanger. The heat transfer unit that transfers this heat transfers the heat to the heating surface and radiates heat from the heating surface to the steam. Therefore, a heat receiving heat exchanger of a heat exchanger for exchanging heat in the atmospheric air outside the steam turbine is provided, and a heat dissipating heat exchanger that is a heating surface for receiving heat between the nozzle and the blades and dissipating to the steam is provided, The heat transfer part which heat-transfers a heat receiving heat exchanger and a heat radiation heat exchanger is comprised.

  The temperature of the atmosphere air of the turbine is warmed by the heat from the turbine in addition to the normal temperature. For this reason, since it becomes possible to heat the vapor | steam which came out of the nozzle even if there was no special heating source, turbine efficiency improves with a simple structure.

  In addition, the heat exchanger has a simpler configuration when heated by exchanging heat with the casing. That is, the casing rises in temperature by receiving conduction heat from the place where the hot steam enters the nozzle.

  The heating means exchanges heat with the casing and receives this heat to heat the steam emitted from the nozzle, so that the steam emitted from the nozzle becomes faster due to being heated, and the momentum is converted into torque by the blades. Therefore, the turbine output can be increased with a simpler configuration.

  The fourth aspect of the invention is, in particular, as a heating means of any one of the first and second aspects of the invention, a heat exchanger that exchanges heat with the steam at the outlet of the steam, a heat transfer unit that transfers this heat, and a heating surface The heating performance from the heating surface makes it possible to supply the steam heat from the turbine to the steam from the nozzle, increase the temperature of the steam from the nozzle to increase the momentum of the steam, and improve the turbine performance. Can be improved.

  That is, the steam emitted from the nozzle is discharged from the steam outlet by rotating the blade while flowing in the blade, but cannot be converted to 100% torque when the steam generates torque by pushing the blade. This converting turbine efficiency is generally 20 to 80%, and this loss becomes heat and raises the steam temperature. Therefore, the temperature of steam when it exits the blade is higher than when it exits the nozzle and enters the blade.

  Therefore, heat is received by the heat exchanger that exchanges heat with the steam at the steam outlet, and this heat is transported by the heat transport section to heat the heating surface. Can increase the steam temperature.

  Since the steam emitted from the nozzle becomes heated at a higher speed and the momentum can be converted into torque by the blades, the turbine output can be increased with a simpler configuration, and the steam emitted from the steam outlet is used as a heat source. The device can be simplified without the need for a special heat source, and the parts can be simplified and the durability can be ensured.

  The fifth aspect of the invention is particularly compact and simple because the heat pipe is used as the heat transfer section of the heating means of any one of the third to fourth aspects of the invention.

  In other words, the heat pipe performs heat transfer with a gas-liquid phase change, so the heat transfer amount per unit transfer amount can be increased, the transfer amount can be set small, and the gas evaporated by heat rises and liquefies by heat dissipation. In order to return to the original state, no special equipment such as a circulation pump is required.

  Therefore, it becomes a simple structure and can ensure the simplification and durability reliability of components.

In the sixth invention, in particular, the steam turbine according to any one of the first to fifth inventions is mounted on a solar thermal Rankine system so that a cogeneration system of power generation and hot water supply / heating can be realized.

  Embodiments of the present invention will be described below with reference to the drawings. In addition, this invention is not limited by this embodiment.

(Embodiment 1)
In FIG. 1 and FIG. 2, reference numeral 1 denotes a nozzle that ejects steam that has entered from the steam inlet 2, and a blade 3 that rotates by receiving the kinetic energy of the steam ejected from the nozzle 1 is disposed around a rotation shaft (output shaft) 4. A plurality are stacked. The steam may be a high-temperature fluorocarbon or water vapor, or a gas body such as high-temperature CO2 or air.

  The blade 3 is configured by superposing a plurality of blades 5 that are plate-like disks to guide the steam ejected from the nozzle 1, and the blade 5 has a passage 6 through which the steam ejected from the nozzle 1 passes. In the embodiment, four are formed by notches. Then, a plurality of overlapping surfaces are formed as impulse surfaces for converting steam velocity energy into torque, and a part of a plate-like disk is molded, or another part is bonded and welded.

  The nozzle 1 is configured in the steam inlet 2 and is provided so that steam collides with the outer peripheral portion of the blade 3 from the tangential direction.

  The nozzle 1 may be a single-hole nozzle, a tapered nozzle, a divergent nozzle, or the like used in ordinary steam turbines, and the nozzle 1 prepared in advance may be attached to the casing 20 described later by caulking or the like. In addition, it may be molded integrally.

  The nozzle 1 is configured by communicating a throttle portion 7, a throat portion 8, and a diffuser portion 9. The throttle portion 7 sequentially reduces the cross-sectional area of the passage of steam, and the throat portion 8 is a passage. The cross-sectional area is minimized, and the diffuser unit 9 conversely enlarges the passage cross-sectional area sequentially.

  Therefore, the flowing steam flows from the throttle portion 7 of the nozzle 1 and the steam velocity increases as the cross-sectional area decreases, and reaches the maximum at the throat portion 8. In the diffuser section 9, the passage cross-sectional area is increased to such an extent that no flow separation occurs in the surrounding area, thereby incorporating the static pressure component into the dynamic pressure and further accelerating the vapor flow velocity.

  And the heat receiving heat exchanger 10 which heat-exchanges with atmospheric air outside a steam turbine, the pump which conveys this heat, the heat conveyance part 11 which consists of a conveyance path, and the heating means which consists of the heating surface 12 used as a radiation heat exchanger 13 is constituted.

  The heat receiving heat exchanger 10 is a forced type using a fan to promote heat exchange with surrounding air, but may be a natural convection type such as a panel. The heating surface 12 is provided in the diffuser part 9 located between the nozzle 1 and the blades 3 so as to come into contact with the steam.

  In the present embodiment, the passage of the transport unit 11 is embedded in the diffuser unit 9, and the surface of the diffuser unit 9 that is in contact with the steam is used as the heating surface 12.

  As another configuration, as shown in FIG. 3, a heat radiation heat exchanger 12 </ b> B connected to the transport unit 11 is configured in the space between the diffuser unit 9 and the blade 3, and this is used as the heating surface 12.

  Both ends of the blade 5 are held by end plates 14 and 15, and spacers 16 and 17 are provided on the rotary shaft 4 to prevent contact when the blade 5 rotates.

  The blade 5, the rotating shaft 4, and the spacers 16 and 17 are made of a heat-resistant and corrosion-resistant material, for example, a metal material such as stainless steel, titanium, or alumina, ceramic, or resin.

  The blade 5 constituting the blade 3 has a thin thickness (for example, 1 mm or less) in order to reduce weight.

  A plurality of steam discharge ports 18 are provided around the rotary shaft 4 of the blade 5. The blade 5, the rotating shaft 4, the steam inlet 2, and the steam outlet 19 are contained in a casing 20.

  End plates 14 and 15 that are thicker than the blades 5 provided at both ends of the spacers 16 and 17 tighten the blades 5 when the blades 5 and the rotary shaft 4 are fixed, thereby increasing the rigidity and preventing the deflection. I am doing so. A plurality of discharge ports 18 provided in each blade 5 are provided so as to communicate coaxially.

  The steam passes through the nozzle 1 from the steam inlet 2, moves while swirling along the passage 6 from the outer periphery of the blade 5 of the blade 3, converges in the vicinity of the rotating shaft 4, and exits from the outlet 18 to the steam outlet 19. I have to.

  A casing 20 that includes the nozzle 1, the blade 5, and the rotating shaft 4, and that forms the steam inlet 2 and the steam outlet 19, has bearings 21 and 22 for supporting the rotation of the rotating shaft 4. It is desirable that the bearings 21 and 22 use seal bearings or non-contact fluid bearings.

  As the material of the casing 20, a heat-resistant and corrosion-resistant material, for example, a metal material such as stainless steel, titanium, or alumina, or a ceramic is selected. The casing 20 is provided with an annular discharge groove 24 on the side where the blade 5 converges on the rotary shaft 4, and a steam outlet 19 is led out from a part of the discharge groove 24.

  A generator 25 that receives the rotation of the rotating shaft 4 and generates electric power is connected to the outside of one bearing 21 of the steam turbine 23.

  This generator 25 uses, for example, an outer rotor type three-phase AC generator, and the AC output is subjected to full-wave rectification, and then an inverter (not shown) is used for current control so as to obtain a stable current. ing.

  In FIG. 4, reference numeral 26 denotes a heat collector that receives and collects solar heat. In order to store the heat of the heat collector 26 in the heat storage tank 27, a circuit 29 (closed circuit) provided with a circulation pump 28 is provided. ing.

  The heat collector 26 includes a tubular heat collector, a vacuum glass tube heat collector, a heat pipe heat collector, or the like. The heat medium 30 circulating in the circuit 29 may be a liquid such as chlorofluorocarbon or water, or CO2 or liquid air in a supercritical state.

  The heat medium 30 is heated by the heat collector 26 to be converted into vapor and sent to the heat storage tank 27 where heat is exchanged to condense and become liquid, and then circulate again to the heat collector 26 by the circulation pump 28. To do. By repeating this operation, heat is stored in the heat storage tank 27.

  The heat storage tank 27 uses a latent heat type using a phase change of a molten salt having a high melting point, a sensible heat type using a molten salt, oil, or the like, or a steam accumulator that stores steam in the form of pressure water or the like. Can store high temperature heat.

  Reference numeral 31 denotes a supply pump connected in the middle of a circuit (closed circuit) 33 for supplying a heat medium 32, which is steam heated in the heat storage tank 27, to the nozzle 1 of the steam turbine 23 and then returning it to the heat storage tank 27 again. .

  The heat medium 32 circulating in the circuit 33 is composed of a liquid such as chlorofluorocarbon or water and its vapor. (Of course, CO2 or liquid air in a supercritical state may be used).

  Further, a hot water storage tank 34 is provided in the middle of the steam turbine 23 and the supply pump 31 of the circuit 33, and hot water is stored in the hot water storage tank 34 by using the heat of high-temperature steam after giving kinetic energy to the steam turbine 23. I am also doing so.

  The heat medium 32 condenses and becomes liquid when transferring heat to the hot water storage tank 34, and is sent to the heat storage tank 27 to be heated again to become steam. By repeating this operation, hot water is stored in the hot water storage tank 34 while power is generated by the generator 25 provided in the steam turbine 23. The hot water stored in the hot water storage tank 34 is supplied by the water supply pump 35 for hot water supply or heating.

  In the configuration as described above, first, in order to form steam to be supplied to the nozzle 1 of the steam turbine 23, the circulation pump 28 is operated, the heat medium 30 is circulated in the circuit 29, and the solar heat is received. It heats with the heat collector 26, forms high temperature vapor | steam (or the two-phase state etc. with which liquid and vapor | steam and liquid were mixed), and sends to the thermal storage tank 27.

  The vapor of the heat medium 30 is condensed into a liquid in the heat storage tank 27 and is sent again to the heat collector 26 by the circulation pump 28 and heated. By repeating this operation, the necessary amount of heat can be held in the heat storage tank 27.

  When a predetermined amount of heat is accumulated in the heat storage tank 27, the supply pump 31 is driven to circulate the heat medium 32 to the circuit 33, and steam of the heat medium 32 of about 200 ° C. is produced in the heat storage tank 27. It ejects from the nozzle 1.

  The steam ejected from the nozzle 1 has high-speed kinetic energy, and rotates around the passage 6 of each blade 5 along the impulse surface while colliding with the impulse surface constituting the blade 5 of the steam turbine 23. It is discharged from a discharge port 18 provided around.

  At this time, the blade 5 rotates due to the viscous force or adhesion force of the steam and is transmitted to the rotating shaft 4 as torque. The generator 25 is rotated using the torque of the rotating shaft 4 to generate power.

  The steam of the heat medium 32 discharged from the steam turbine 23 is sent to the hot water storage tank 34 to exchange heat with water, and the heat is stored in the hot water storage tank 34 as hot water.

  The steam is condensed in the hot water storage tank 34, becomes a liquid, is refluxed to the heat storage tank 27 through the supply pump 31, and is heated again to form steam.

  By repeating this operation, hot water is stored in the hot water storage tank 34 while generating electricity with the steam turbine 23, and when the hot water supply or heating is necessary, the water supply pump 35 is operated to use the hot water so as to constitute a cogeneration system. I have to.

As described above, in the present embodiment, the nozzle 1 for ejecting steam and the blade 3 configured by superimposing the plurality of blades 5 for guiding the steam ejected from the nozzle 1 are used. The heating means 13 that heats the steam ejected from the nozzle 1 is formed between the nozzle 1 and the blade 3 by enclosing the blade 3 and the rotating shaft 4 to form the steam inlet 2 and the steam outlet 19. The steam thus heated can be heated to a high temperature by the heating means 13, and the steam flow rate is further increased because the volume of the steam increases.

  Therefore, the torque applied to the blades 3 of the turbine is increased, the output of the steam turbine 23 is increased, and the performance of the turbine that converts steam into driving force is improved.

  The steam turbine 23 converts the pressure into speed and rotates the blades 3. In order to obtain momentum from the high pressure to the low pressure with the nozzle 1, even if steam that is as hot as possible is spouted from the nozzle 1 even if heat is added, the steam that is generated from the nozzle 1 expands in an adiabatic state, so it is very low in temperature. (For example, −76 ° C. when the pressure is changed from 0.4 mpa to atmospheric pressure using air).

  Therefore, the volume contracts as shown by the boiled charles and enters the blades at a speed corresponding to the volume reduction. For this reason, the momentum obtained by mass × speed = is small, and the turbine output generated by the steam is also small.

  Therefore, as shown in the present embodiment, the temperature is lowered by adiabatic expansion, and the steam ejected from the nozzle 1 at a high speed is heated by the heating means 13 to make the temperature higher. Heating increases the volume of the steam, and the steam flow rate divided by the passage area is faster. For this reason, the momentum represented by the flow rate × speed increases, the torque applied to the turbine increases, the output of the steam turbine 23 increases, and the turbine performance for converting steam into driving force is improved.

  As a result, it is possible to make the steam turbine more compact and simple by utilizing the improved performance.

  In addition, the nozzle 1 is composed of a throttle section 7, a throat section 8, and a diffuser section 9, and the heating surface 12 of the heating means 13 is configured in the diffuser section 9, thereby obstructing the flow of steam flowing at high speed. It is possible to heat without any problem, and the steam flow rate can be maximized and led to the blade 5 of the blade 3 to increase the output of the turbine.

  That is, the high-pressure steam flows from the steam inlet 2 to the throttle portion 6 and the throat portion 8 to significantly reduce the cross-sectional area of the flow path and increase the flow velocity. At this time, the steam enters an adiabatic compression state and the temperature of the steam rises. Thereafter, the flow area is increased by gradually increasing the cross-sectional area of the flow path at the diffuser unit 8 and lowering the static pressure, thereby increasing the flow rate. Become.

  Therefore, by supplying heat to the steam from the heating surface 12 and heating it, it becomes possible to increase the speed while maintaining the temperature without lowering the temperature of the steam once.

  Further, since the distance between the heating surface 12 and the steam is short, heat transfer can be improved, and the heat is easily transmitted to the center of the steam. Therefore, since the temperature difference between the heating surface 12 and the steam is reduced, and the temperature of the steam can be uniformly increased, the temperature of the entire steam is high, the volume of the steam is the largest, and the momentum represented by the flow rate × velocity is The torque applied to the turbine increases, the output of the steam turbine 23 increases, and the turbine performance for converting steam into driving force is improved.

  Further, the steam in the diffuser 9 is fast and easily exchanges heat between the heating surface 12 and the steam, so that the heating device can be made small.

  The heating means 13 includes a heat exchanger 10 that exchanges heat with atmospheric air outside the steam turbine 23, a heat transfer unit 11 that transfers this heat, and a heating surface 12. It is configured to heat.

  Thereby, the heat exchanger 10 can receive heat easily. That is, the heating means 13 for heating the steam receives the amount of heat for heating the steam ejected from the nozzle 1 from the ambient air outside the turbine by the heat exchanger 10, and the heating surface 12 is transferred by the heat transfer unit 10 for transferring this heat. The heat is dissipated from the heating surface 12 to the steam.

  Therefore, it is the heating surface 12 for providing the heat receiving heat exchanger of the heat exchanger 10 for exchanging heat in the atmospheric air outside the steam turbine 23 and receiving heat between the nozzle 1 and the blades 3 and dissipating it to the steam. A heat dissipating heat exchanger is provided to constitute the heat transfer unit 10 that heat-transfers the heat receiving heat exchanger and the heat dissipating heat exchanger.

  The temperature of the atmosphere air of the turbine is warmed by the heat from the turbine in addition to the normal temperature. For this reason, since it becomes possible to heat the steam which became low temperature by the adiabatic expansion from the nozzle 1 even if there is no special heating source, turbine efficiency improves with a simple structure.

  Moreover, if the heat exchanger 10 is configured to perform heat exchange with the casing 20 to heat, the heat exchanger 10 has a simpler configuration. That is, the casing 20 rises in temperature by receiving conduction heat from the place where the high-temperature steam enters the nozzle 1.

  The heating means 13 exchanges heat with the casing 20 and receives the heat so as to heat the steam emitted from the nozzle 1, so that the steam emitted from the nozzle 1 becomes faster due to being heated, and the blade 3 Since the momentum can be converted into torque, the turbine output can be increased with a simpler configuration. Therefore, it is possible to make the steam turbine more compact and simple using the improved performance.

  In addition, the accuracy of the blade 5 can be maintained by simple processing in which disk-shaped plates are overlapped and fixed on the rotating shaft 4, and the ability can be easily changed by selecting the number of blades 5. In other words, the blade 5 that forms a flat plate into a circular shape and a hole is easily machined with high precision, and has a high balance of dynamic balance and does not generate vibration or vibration even when rotated at a high speed. Can make the whole smaller.

  Further, the processing can be made inexpensively by a die multi-sided press or the like. In addition, since the interval can be adjusted by selecting the thickness of the blade 5 according to the type of refrigerant, it is easy to set the interval to maximize the viscosity, the rotational force can be transmitted by the viscosity, and the efficiency of the turbine can be improved. The efficiency of the turbine can be increased, and a plurality of blades molded in the same shape can be easily stacked, and the assembly accuracy of the unit can be improved by forming a uniform gap. Further, the entire steam turbine 23 can be made compact and simplified.

  When the maximum power generation amount is increased, it is possible to increase the number of blades 5 to be overlapped, and since there is no addition of a complicated shape, an increase in cost can be suppressed. Further, since the steam ejected from the nozzle 1 stays on the impulse surface of the blade 5 for a long time and increases the viscous force and adhesion force to increase the torque applied to the rotating shaft 4, it operates at a low temperature (about 200 ° C.). Since the steam turbine 23 can be realized and a plurality of blades molded in the same shape can be easily overlapped, the assembly accuracy of the unit can be improved.

In addition, an independent heat collecting circuit 29 is configured so that solar heat obtained by the heat collector 26 can be stored and maintained in the heat storage tank 27 at all times regardless of the operation of the steam turbine 23. In addition, the steam turbine 23 can take out necessary electricity from the generator 25 at any time.

  And since the hot water storage tank 34 is provided in the middle of the circuit 33, the heat of the heat storage tank 27 can be stored in the hot water storage tank 34 as hot water regardless of power generation, so that hot water necessary for hot water supply and heating can be taken out at any time. .

  In addition, since steam is generated using solar heat, and is generated from the nozzle 1 by rotating the generator 25 of the steam turbine 23, power generation can be achieved.

(Embodiment 2)
FIG. 5 shows a second embodiment of the present invention, which is different from the first embodiment in the heating means 13. That is, the heating means 13 of the second embodiment includes the heat exchanger 10 provided at the steam outlet 19 that is the steam outlet, the heating surface 12 provided between the nozzle 1 and the blade 3, and the heat of the heat exchanger 10. It is comprised with the heat pipe 36 as a heat conveyance part which conveys. The heat pipe 36 is connected to the heating surface 12 and the heat exchanger 10.

  The configuration other than the heating means 13 is the same as that of the first embodiment, and the specific description is the same as that of the first embodiment.

  Since the heat of the steam discharged from the steam turbine 23 is recovered and supplied to the flowing steam through the nozzle 1 to increase its temperature and the momentum is increased, the turbine performance can be improved.

  That is, the steam emitted from the nozzle 1 is discharged from the steam outlet 19 by rotating the blade 3 while flowing through the blade 3, but when the steam generates torque by pushing the blade 3, it is converted to 100% torque. Can not.

  The turbine efficiency to convert this torque is generally 20 to 80%, and this loss becomes heat and raises the steam temperature.

  Therefore, the temperature of steam when it exits from the blade 3 becomes higher than when it exits the nozzle 1 and enters the blade 3.

  In the present embodiment, the heat of the steam discharged from the steam outlet 19 is recovered by the heat exchanger 10, transported to the heating surface 12 via the heat pipe 36, and the recovered heat is converted into steam flowing through the nozzle 1. I tried to supply.

  Therefore, the steam emitted from the nozzle 1 is heated and becomes high speed, and can be converted into torque by the blades 3, so that the turbine output can be increased. And since the vapor | steam exiting from the vapor | steam outlet 19 is used as a heat source, a special heat source is unnecessary, a structure becomes simple, and simplification of components and durability reliability can be ensured.

  By using the heat pipe 36 as the heat transfer section of the heating means 13, the apparatus can be made compact and simple. That is, the heat pipe 36 is a hermetically sealed pipe that connects the high temperature side and the low temperature side, and after having been evacuated into the pipe, the carrier medium and the wick are injected. When heat is received on the high temperature side, the carrier medium evaporates and becomes gas and moves to the low temperature side. On the low temperature side, the high temperature carrier medium releases heat and liquefies, and the liquefied carrier medium impregnates the wick and flows to the high temperature side.

Therefore, since heat transfer is performed by gas-liquid phase change, the transfer amount with a large transfer heat amount per unit transfer amount can be set small, and the gas evaporated by heat rises, liquefies by heat dissipation and liquefies again. Because it returns, no special equipment such as a circulation pump is required. Therefore, it becomes a simple structure and can ensure the simplification and durability reliability of components.

(Embodiment 3)
FIG. 6 shows a solar thermal Rankine system according to Embodiment 3 of the present invention, and the steam of the heat medium 30 heated by the heat collector 26 is sent directly from the circuit 29 (closed circuit) to the steam turbine 23 via the circulation pump 28. This is the difference from FIG. 4 of the first embodiment.

  The hot water storage tank 34 is provided in the middle of the steam turbine 23 and the circulation pump 28 in the circuit 29, and hot water is stored in the hot water storage tank 34 by using the heat of the high temperature steam after the kinetic energy is given to the steam turbine 23. It is.

  The heat medium 30 condenses into a liquid when transferring heat to the hot water in the hot water storage tank 34 and is sent again to the heat collector 26 to be heated and form steam. By repeating this operation, hot water is stored in the hot water storage tank 34 while generating electricity by the generator 25 provided in the steam turbine 23. The hot water stored in the hot water storage tank 34 is supplied by the water supply pump 35 for hot water supply or heating.

  As shown in FIG. 7, the steam of the heat medium 29 heated by the heat collector 26 is directly sent to the steam turbine 23 by the circuit 29 (closed circuit) by the circulation pump 28, and the steam turbine 23 is rotated to generate the generator 25. It is also possible to generate only electricity.

  As described above, in the present embodiment, the steam turbine 23 can be mounted on the solar thermal Rankine system to realize a cogeneration system that combines power generation, hot water supply, and heating. Effective means of energy saving promotion and CO2 reduction can be obtained.

  As described above, the present invention can operate a steam turbine using solar heat having a low energy density, and therefore can be applied to exhaust heat recovery of automobiles and fuel cells.

Front sectional view of a steam turbine according to Embodiment 1 of the present invention. XX side sectional view of FIG. Expanded sectional view of the main part Configuration diagram of solar thermal Rankine system Side sectional view of a steam turbine according to Embodiment 2 of the present invention. Configuration diagram of solar thermal Rankine system in Embodiment 3 of the present invention The block diagram which shows the modification of the solar thermal Rankine system in Embodiment 3

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Nozzle 2 Steam inlet 3 Blade | blade 4 Rotating shaft 5 Blade 7 Restriction part 8 Throat part 9 Diffuser part 10 Heat exchanger 11 Heat transfer part 12 Heating surface 13 Heating means 19 Steam outlet 20 Casing 25 Generator

Claims (6)

A nozzle for jetting steam, a blade formed by superimposing a plurality of blades for guiding the steam jetted from the nozzle, the nozzle, the blade, and a rotating shaft of the blade are included, and an inlet and an outlet for the steam are provided. The steam turbine which comprised the casing comprised and arrange | positioned the heating means which heats the steam ejected from the said nozzle between the said nozzle and the said blade | wing. 2. The steam turbine according to claim 1, wherein the nozzle includes a throttle portion, a throat portion, and a diffuser portion, and a heating surface of a heating unit is set in the diffuser portion. The steam turbine according to claim 1 or 2, wherein the heating means includes a heat exchanger that exchanges heat with external atmospheric air, a heat transfer unit that transfers the heat, and a heating surface. The steam turbine according to claim 1 or 2, wherein the heating means includes a heat exchanger that exchanges heat with steam at an outlet of the steam, a heat transfer unit that transfers the heat, and a heating surface. The steam turbine according to claim 3 or 4, wherein the heat transfer section of the heating means is configured using a heat pipe. A solar thermal Rankine system equipped with the steam turbine according to any one of claims 1 to 5 to perform a power generation, hot water supply / heating cogeneration system.

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