JPWO2006070497A1 - Convection temperature difference prime mover - Google Patents

Abstract

The convection temperature difference prime mover S1 is rotatably supported by the outer shell 1, and has an inner cylinder 10 in which a gas supply port 11 is formed at one end in the axial direction and a gas discharge port 12 is formed at the other end. The outer cylinder 20 provided to be rotatable with respect to the inner cylinder 10, the moving blade 40 that applies a rotational force to the inner cylinder 10 by the gas flowing in from the supply port 11, and the cooling liquid is sprayed inside the inner cylinder 10. And a cooling liquid circulation line 80 for circulating the cooling liquid, and a heating liquid circulation line 90 for spraying the heating liquid between the inner cylinder 10 and the outer cylinder 20 and circulating the heating liquid. The gas passes from the supply port 11 through the inside of the inner cylinder 10 to the discharge port 12 and through the other channel Rb from the discharge port 12 to the supply port 11 through the outside of the inner tube 10. A temperature difference is imparted to the gas to cause gas convection.

Description

  The present invention can obtain power from various kinds of heat energy such as seawater, snow, groundwater, geothermal heat, industrial waste heat energy, or heat energy obtained by burning waste. The present invention relates to a convection temperature difference prime mover, and more particularly to a convection temperature difference prime mover that generates gas convection inside and generates power by this convection.

  Conventionally, as this type of convection temperature difference prime mover, there is one related to the research of the present applicant. For example, a convection temperature difference prime mover described in Patent Document 1 (Japanese Patent Laid-Open No. 2002-256882) is known.

As shown in FIG. 37, the convection temperature difference prime mover Sa includes a sealed cylindrical outer shell 200, a support shaft 201 provided along the central axis of the outer shell, and a shaft support rotatably on the support shaft 201. An inner cylinder 204 in which a gas supply port 202a is formed at one end in the axial direction and a gas discharge port 203 is formed in the center of the other end; Is provided with an outer cylinder 205 positioned between the outer shell 200 and the inner cylinder 204. In the convection temperature difference driving device Sa, the gas flows from the supply port 202a of the inner cylinder 204 to the discharge port 203 through the inside of the inner cylinder 204 and the outside of the inner cylinder 204 from the discharge port 203 of the inner cylinder 204. A temperature difference is imparted to the gas to cause convection of the gas so as to pass through the other channel that passes through the supply port 202a. The convection temperature difference prime mover Sa rotates the inner cylinder 204 and the outer cylinder 205 by the convection of the gas, and obtains power by the power acquisition mechanism 206a to generate electric power.
One end and the other end of the inner cylinder 204 and the outer cylinder 205 are pivotally supported with respect to the support shaft 201.
The inner cylinder 204 and the outer cylinder 205 are divided into one-end-side rotators 204a and 205a and other-end-side rotators 204b and 205b. The split end portions of the one-end-side rotators 204a and 205a and the other-end-side rotators 204b and 205b are coupled so that the split end portions can be relatively shifted in the direction perpendicular to the axial direction and can be relatively rotated.
A turbine 206 is provided at the other end of the inner cylinder 204. The turbine 206 injects the gas from the discharge port 203 to the outside of the inner cylinder 204 in the direction opposite to the rotation direction of the inner cylinder 204, thereby applying a rotational force to the inner cylinder 204.

  The convection temperature difference prime mover Sa is provided with a liquid circulation line 207. The liquid circulation conduit 207 has an injection port 208 connected to the supply port 202 b of the support shaft 201, and further has a recovery port 209 in the outer shell 200. The liquid passes through the support shaft 201 from the inlet 208 and is jetted into the inner cylinder 204 from the outlet 210, whereby the gas in the inner cylinder 204 is cooled. Thereafter, the liquid circulation line 207 recovers the liquid that reaches the partition wall 211 through the turbine 206 from the recovery port 209 and guides it to the injection port 208 again. A cooling unit 212 that cools the liquid is provided in the middle of the liquid circulation conduit 207.

  Furthermore, a gas circulation conduit 215 through which gas can be circulated is provided. The gas circulation conduit 215 has a blower outlet 213 at one end of the outer shell 200 and further has a return port 214 at the other end. A heating unit 216 for heating the circulating gas is provided in the middle of the gas circulation conduit 215. In addition, on the inner wall of the one end side rotating body 205a of the outer cylinder 205, a large number of air passages 217 through which the gas from the blower outlet 213 flows from the one end side inlet 217a to the other end side outlet 217b are arranged. Thereby, the high-temperature gas flowing out from the other end side outlet 217b of the ventilation path 217 passes through the space between the inner cylinder 204 and the outer cylinder 205, passes through one flow path of the inner cylinder 204, and is liquid in the one flow path. Is cooled to reach the turbine 206.

When the convection temperature difference prime mover Sa generates power, the cooling liquid is supplied into the support shaft 201 from the supply port 202b of the support shaft 201, and the gas is blown out from the air outlet 213. At this time, the cooling liquid passes through the support shaft 201, flows out from the outlet 210 into the inner cylinder 204, is guided to the recovery port 209 through the turbine 206, and passes through the liquid circulation line 207 from the recovery port 209. Then, it is guided to the inlet 208 again. Moreover, gas flows in from the one end side inlet 217a of the ventilation path 217 of the one end side rotary body 205a, and flows out from the other end side outlet 217b. The high temperature gas that has flowed out passes through the other flow path between the inner cylinder 204 and the outer cylinder 205, then passes through one flow path of the inner cylinder 204, and is cooled by the liquid in the one flow path to the turbine 206. It reaches. Then, the gas is led from the return port 214 through the gas circulation line 215 to the blowout port 213 again. In the middle of the gas circulation conduit 215, the cooled gas is heated by the heating unit 216.
As a result, the one flow path from the supply port 202a of the inner cylinder 204 through the inside of the inner cylinder 204 to the discharge port 203 and the other of the discharge path 203 from the inner cylinder 204 through the outside of the inner cylinder 204 to the supply port 202. Gas convection occurs through the flow path. Then, due to this convection, the inner cylinder 204 and the outer cylinder 205 rotate in the same direction via the turbine 206.
By this turbine 206, the gas is injected in the direction opposite to the rotational circumferential direction of the inner cylinder 204, and the inner cylinder 204 and the outer cylinder 205 rotate. The power acquisition mechanism 206a generates power by obtaining power from both the inner cylinder 204 and the outer cylinder 205.

JP 2002-256882 A

  By the way, such a convection temperature difference prime mover Sa heats the gas for rotating the inner cylinder 204 and the outer cylinder 205 once by the heating unit 216 of the gas circulation pipe 215 outside the outer cylinder 205. Then, the air is blown out from the lower side of the outer cylinder 205 through the ventilation path 217. For this reason, the path of the gas flowing through the other flow path becomes complicated, a loss occurs in the energy of the gas convection, and there is a problem that the energy cannot be efficiently applied to the inner cylinder 204 and the outer cylinder 205.

  The present invention has been made in view of the above-described problems. The gas passing through the other channel can be heated in the space between the inner cylinder and the outer cylinder, the gas path is simplified, and convection from the gas is performed. It is an object of the present invention to provide a convection temperature difference prime mover that can efficiently apply the energy of 1 to the inner cylinder and the outer cylinder.

  In order to achieve such an object, the convective temperature difference prime mover of the present invention is supported by an outer shell and a rotatable shaft on the outer shell, a gas supply port is formed at one end in the axial direction, and a gas discharge port is formed at the other end. An inner cylinder in which an outlet is formed, an outer cylinder that is provided rotatably with respect to the outer shell and the inner cylinder, and a wall portion is located between the outer shell and the inner cylinder, and gas is supplied to the inner cylinder. The temperature difference between the gas so that it passes through one flow path from the opening to the discharge port through the inside of the inner cylinder and the other flow path from the discharge port of the inner cylinder to the supply port through the outside of the inner cylinder. In the convection temperature difference prime mover for obtaining power by rotating the inner cylinder and the outer cylinder by the gas convection, the gas flowing from the supply port is supplied to the inner cylinder. A rotor blade that receives and applies a rotational force to the inner cylinder, sprays a cooling liquid into the inner cylinder, and A cooling liquid circulation pipe for cooling the gas passing therethrough and circulating the cooling liquid is provided, and a cooling unit for cooling the cooling liquid is provided in the middle of the cooling liquid circulation pipe, and the inner cylinder and the outer cylinder A warming liquid is sprayed between the two channels to warm the gas passing through the other flow path, and a warming liquid circulation conduit for circulating the warming liquid is provided. Further, a heating unit for heating the heating liquid is provided.

According to this convection temperature difference prime mover, the cooling liquid is sprayed into the inner cylinder by the cooling liquid circulation conduit. The cooling liquid cools the gas flowing through the one flow path and is heated by this gas. And it cools again by the cooling part in the middle of the cooling liquid circulation conduit. Therefore, the cooling liquid sprayed in the inner cylinder is again in a low temperature state, and the cooling state of the gas in the flow path is improved.
Further, the warming liquid is sprayed between the inner cylinder and the outer cylinder by the warming liquid circulation conduit. The warming liquid warms the gas in the other channel and is cooled by this gas. Then, in the middle of the heated liquid circulation tube, the heated liquid is heated again by the heating unit. Therefore, the warming liquid sprayed between the inner cylinder and the outer cylinder is again in a high temperature state, and the gas warming state of the other channel is improved.

As a result, gas convection flows through the one flow path from the supply port of the inner cylinder through the inside of the inner cylinder to the discharge port and the other flow path from the discharge port of the inner cylinder to the supply port through the outside of the inner cylinder. Arise. And by this convection, gas acts on the moving blade of an inner cylinder, and an inner cylinder and an outer cylinder rotate.
At this time, the gas flowing through the other flow path is directly heated in the space between the outer cylinder and the inner cylinder by the heating liquid. For this reason, the gas in the other channel is heated without going out of the outer cylinder, so that the gas path is simplified. Thereby, since the energy loss in the convection of gas is reduced, the energy of this convection is efficiently given to the inner cylinder and the outer cylinder as a rotational force.

Further, in the convection temperature difference prime mover according to the present invention, the cooling liquid circulation conduit has a cooling liquid inlet provided in the outer shell on one end side, and the cooling pipe is connected to the inner cylinder on the other end side. A plurality of outlets for spraying a liquid, and the other end of the inner cylinder and the outer cylinder being rotatable, one support shaft, an inlet connected to the inlet of the one support shaft, and the one flow path A cooling port for recovering the cooling fluid flowing out from the discharge port of the inner cylinder after cooling the gas, and a cooling liquid circulation tube for circulating the cooling liquid from the recovery port to the inlet again. A liquid circulation pipe is provided at one end side of the outer shell and has an inflow port for the heated liquid, has an outflow port at the other end side, and further supports one end of the inner cylinder and the outer cylinder. A flow that covers the outside of the other support shaft and the inner cylinder, and allows the heated liquid to flow from the outlet of the other support shaft to and from the inner cylinder And a cylinder formed with a plurality of injection ports for injecting the heated liquid toward the outer cylinder, an injection port connected to the inlet of the other spindle, and an injection port of the cylinder A recovery port for recovering the jetted warming liquid and a warming liquid circulation tube for circulating the warming liquid from the recovery port to the inlet again are provided.
In this case, since one support shaft is also used as a part of the cooling liquid circulation conduit and the other support shaft is also used as a part of the warming liquid circulation conduit, a dedicated conduit for ejecting these liquids is used. Compared with the case where the is separately provided, the structure becomes simple. Therefore, there is no adverse effect on gas convection in the one channel and the other channel, energy loss in gas convection is reduced, and this convection energy is efficiently applied to the inner and outer cylinders as rotational force. The

In the convection temperature difference driving device of the present invention, the inner cylinder is provided with a tubular inner cylinder rotation shaft that is rotatably inserted into the one support shaft or the other support shaft, and the outer cylinder is provided with the inner cylinder rotation shaft. A tubular outer cylinder rotating shaft coaxial with the shaft is provided, and a power acquisition mechanism for obtaining power from both the inner cylinder rotating shaft and the outer cylinder rotating shaft is provided.
If it does in this way, the rotational force of both an inner cylinder and an outer cylinder can be obtained as motive power by a motive power acquisition mechanism, and the conversion efficiency of energy will become very good.

  In the convection temperature difference prime mover according to the present invention, the power acquisition mechanism meshes with a first prime gear provided on the inner cylinder rotary shaft, a second prime gear provided on the outer cylinder rotary shaft, and a first prime gear. A first driven gear, a second driven gear meshing with the second driving gear, a shaft to which the first driven gear and the second driven gear are attached, and a generator driven in conjunction with the shaft is there. Thereby, motive power can be obtained as electric power by a reliable mechanism called a gear mechanism.

Further, the convection temperature difference prime mover of the present invention is provided with a guide vane for guiding gas to the moving blade provided at the supply port on the inner circumference of one end side of the outer cylinder, and the moving blade is one end of the inner cylinder. A plurality of blades arranged in an equiangular relationship around the rotation axis of the inner cylinder and having a surface for receiving the gas guided by the guide blades, the guide blades including the moving blades It is set as the structure provided with the several baffle plate arranged in an equiangular relationship corresponding to this blade.
If it does in this way, a guide blade will receive the gas of the other channel by a baffle plate, and will change the flow direction. Then, the gas flows into the blade, stops at the blade of the moving blade, escapes to the inner peripheral portion of the moving blade, and flows into the inner cylinder. Therefore, since the gas compressed by the guide blades and applied with the centrifugal force strikes the blade of the moving blade almost at right angles, the blade of the moving blade can sufficiently receive the gas force. Therefore, the conversion efficiency for converting gas energy into the rotational force of the inner cylinder is greatly improved, and the power generation efficiency is improved. Further, at this time, the gas is further compressed between the blades, and the flow velocity becomes extremely fast. Therefore, the energy for striking the blade is increased, and the convection energy is efficiently applied to the inner cylinder as a rotational force.

Further, the convection temperature difference driving device according to the present invention is formed by bending the air guide plate in one circumferential direction, and a centrifugal force is applied to the gas flowing into the supply port by the concave surface of the air guide plate. Is provided.
If it does in this way, the gas of the other channel will stop on the concave curved surface of each baffle plate, and the flow direction of gas will be changed in the state where centrifugal force was given. For this reason, the energy for making contact with the blade of the rotor blade is increased, and the convection energy is more efficiently applied to the inner cylinder as a rotational force.

Further, the convection temperature difference prime mover of the present invention receives the gas discharged from the discharge port on the outside of the other end of the inner tube, applies a rotational force to the inner tube, and is exhausted from the discharge port. The guide vanes for guiding the gas in the gas flow direction of the other channel are provided.
If it does in this way, it will become possible to give rotational force to an inner cylinder also from the gas which descended one flow path, and was discharged from the discharge port, and convection energy will be given to an inner cylinder more efficiently as rotational force. . Further, since the guide vanes guide the gas from the discharge port toward the gas flow direction of the other flow path, the gas is less likely to stay on the other end side of the outer cylinder.

Moreover, the convection temperature difference prime mover according to the present invention has a configuration in which a porous member through which the gas passing through the one passage and the cooling liquid can pass is provided inside the inner cylinder.
If it does in this way, since a cooling liquid will stay temporarily on one flow path by a porous member, the heat exchange efficiency with the gas which distribute | circulates one flow path will improve.
The porous member may be a wound sheet-like metal net. If it does in this way, centrifugal force will be given by rotation of an inner cylinder, a cooling liquid will pass through a mesh, will move to an outside sequentially, will reach an inner cylinder, and will flow down the inner wall of an inner cylinder. This simplifies the structure of the porous member.
Further, a fin that pushes the retained gas into the discharge port side is provided on the supply port side of the one flow path on the inner periphery of the inner tube, or the one support shaft is linked to the inner tube. It is preferable that a fin that pushes the gas staying on the supply port side of the one flow path into the discharge port side may be provided on the one support shaft. In this way, the gas that flows in from the supply port and tries to stay in the one end side of the inner cylinder is pushed into the discharge port side by the fin, so that the gas flow in the one flow path becomes smooth, The convection state is improved.

  As described above, the convection temperature difference prime mover of the present invention scatters the warming liquid between the inner cylinder and the outer cylinder, warms the gas passing through the other channel, and circulates the warming liquid. A heating liquid circulation line is provided, and a heating unit for heating the heating liquid is provided in the middle of the heating liquid circulation line. Thereby, the gas flowing through the other flow path is directly heated in the space between the outer cylinder and the inner cylinder by the heated liquid flowing out from the outlet. Therefore, the gas in the other channel is heated without going out of the outer cylinder, the gas path is simplified, energy loss in the gas convection is reduced, and the energy of this convection is converted into the inner cylinder as a rotational force. And efficiently applied to the outer cylinder.

It is a figure which shows the convection temperature difference prime mover which concerns on 1st embodiment of this invention. It is a figure which shows the principal part of the convection temperature difference prime mover which concerns on 1st embodiment of this invention. It is an enlarged view which shows the principal part of the lower part of the convection temperature difference prime mover which concerns on 1st embodiment of this invention. The convection temperature difference prime mover which concerns on 1st embodiment of this invention is shown, and it is AA sectional drawing of FIG. The convection temperature difference prime mover concerning a first embodiment of the present invention is shown, and is a BB sectional view of FIG. The convection temperature difference prime mover which concerns on 1st embodiment of this invention is shown, and it is CC sectional drawing of FIG. The convection temperature difference prime mover which concerns on 1st embodiment of this invention is shown, and it is DD sectional drawing of FIG. The convection temperature difference prime mover which concerns on 1st embodiment of this invention is shown, and it is EE sectional drawing of FIG. The convection temperature difference prime mover which concerns on 1st embodiment of this invention is shown, and it is FF sectional drawing of FIG. The convection temperature difference prime mover which concerns on 1st embodiment of this invention is shown, and it is GG sectional drawing of FIG. The convection temperature difference prime mover which concerns on 1st embodiment of this invention is shown, and it is HH sectional drawing of FIG. The convection temperature difference prime mover which concerns on 1st embodiment of this invention is shown, and it is II sectional drawing of FIG. The convection temperature difference prime mover which concerns on 1st embodiment of this invention is shown, and it is JJ sectional drawing of FIG. The convection temperature difference prime mover which concerns on 1st embodiment of this invention is shown, and it is KK sectional drawing of FIG. The convection temperature difference prime mover which concerns on 1st embodiment of this invention is shown, and it is LL sectional drawing of FIG. The convection temperature difference prime mover which concerns on 1st embodiment of this invention is shown, and it is MM sectional drawing of FIG. It is a figure which shows the system by which the convection temperature difference prime mover which concerns on 1st embodiment of this invention is used. It is a figure which shows the convection temperature difference prime mover which concerns on 2nd embodiment of this invention. It is an enlarged view which shows the principal part of the lower part of the convection temperature difference prime mover which concerns on 2nd embodiment of this invention. FIG. 19 shows a convection temperature difference prime mover according to a second embodiment of the present invention, and is an NN sectional view of FIG. 18. FIG. 19 is a cross-sectional view taken along line OO in FIG. 18, showing a convection temperature difference prime mover according to a second embodiment of the present invention. It is a principal part enlarged view of the convection temperature difference prime mover which concerns on 3rd embodiment of this invention. It is a figure which shows the convection temperature difference prime mover which concerns on 4th embodiment of this invention. 24 shows a convection temperature difference prime mover according to a fourth embodiment of the present invention, and is a cross-sectional view taken along the line PP in FIG. 23. FIG. It is a QQ sectional view of Drawing 23 showing a convection temperature difference prime mover concerning a fourth embodiment of the present invention. It is a figure which shows the convection temperature difference prime mover which concerns on 5th embodiment of this invention. It is a perspective view showing a convection temperature difference prime mover according to a fifth embodiment of the present invention with a part cut away. It is an enlarged view which shows the principal part of the lower part of the convection temperature difference prime mover which concerns on 5th embodiment of this invention. FIG. 29 shows a convection temperature difference prime mover according to a fifth embodiment of the present invention, and is an RR sectional view of FIG. 28. It is SS sectional drawing of FIG. 28 which shows the inner cylinder of the convection temperature difference prime mover which concerns on 5th embodiment of this invention. FIG. 31 is a cross-sectional view taken along the line U-U in FIG. 30, showing the inner cylinder of the convection temperature difference prime mover according to the fifth embodiment of the present invention. FIG. 29 shows a convection temperature difference prime mover according to a fifth embodiment of the present invention, and is a TT sectional view of FIG. 28. It is a figure which shows the fin of the convection temperature difference prime mover which concerns on 5th embodiment of this invention. It is principal part sectional drawing which shows the convection temperature difference prime mover which concerns on 6th embodiment of this invention. It is a figure showing an example of application of a system using a convection temperature difference prime mover concerning a first embodiment of the present invention. It is a figure which shows the application example of the shape of the inner cylinder and outer cylinder of the convection temperature difference prime mover which concern on each embodiment of this invention. It is a figure which shows an example of the conventional convection temperature difference prime mover.

Explanation of symbols

S1, S2, S3, S4, S5 Convection temperature difference prime mover Ra One channel Rb Other channel 1 Outer 1a Base 2 Base 3 Side wall 4 Top plate 8 Gear pump 10 Inner cylinder 10a Tube 11 Supply port 12 Discharge port 13 Inner tube Rotating shaft 20 Outer cylinder 23 Outer cylinder rotating shaft 24 Suspension member 25 Protrusion 30 Power acquisition mechanism 31 First driving gear 32 Second driving gear 33 Generator 34 First driven gear 35 Second driven gear 36 Shaft 37 Ball bearing 40 Moving blade 41 Blade 42 Closure plate 50 Guide blade 51 Guide plate body 52 Blade member 53 Inner surface member 54 Outer surface member 55 Recovery blade 56 Basin member 60 Porous member 61 Net 62 Plate body 65 Fin 70 Guide blade 71 Air guide plate 72 Guide Plate 73 Bolt 74 Nut 80 Cooling liquid circulation pipe line 80a Cooling liquid circulation pipe body 81 Cooling portion 82 One support shaft 83 Inlet 84 Outlet 85 Inlet 86 Collecting port 88 hole 89 sliding member 89a groove 89b groove 90 warming liquid circulation pipe 90a warming liquid circulation pipe body 91 warming part 92 other support shaft 93 inlet 94 outlet 95 inlet 96 recovery port 97 feeding pipe 98 Hole 99 Spout 100 Hole 101 Sliding contact portion 102 One passage 103 The other passage 104 Partition

[First embodiment]
Hereinafter, based on an accompanying drawing, the convection temperature difference prime mover concerning a first embodiment of the present invention is explained in detail.

The convection temperature difference prime mover S1 is shown in FIGS.
The convection temperature difference prime mover S <b> 1 includes a cylindrical outer shell 1, an inner tube 10, and an outer tube 20. The inner cylinder 10 is rotatably supported by the outer shell 1, and further, a gas supply port 11 is formed at one end in the axial direction, and a gas discharge port 12 is formed at the other end. The outer cylinder 20 is provided so as to be rotatable with respect to the outer shell 1 and the inner cylinder 10, and its wall portion is located between the outer shell 1 and the inner cylinder 10.
The convection temperature difference prime mover S <b> 1 is configured such that the gas passes from the supply port 11 of the inner cylinder 10 to the discharge port 12 through the inside of the inner tube 10 and from the discharge port 12 of the inner tube 10 to the inner tube 10. A temperature difference is given to the gas so as to pass through the other flow path Rb that reaches the supply port 11 through the outside of the gas, thereby causing convection of the gas. The convection temperature difference prime mover S <b> 1 rotates the inner cylinder 10 and the outer cylinder 20 by gas convection and obtains power from the power acquisition mechanism 30.
Here, for example, carbon dioxide is used as the gas. Moreover, in order to give a temperature difference to gas, the heating liquid which heats gas and the cooling liquid which cools gas are used. The heating liquid and the cooling liquid are, for example, oil having a lubricating ability.

Specifically, as shown in FIGS. 1 to 3, FIGS. 5 to 7, and FIGS. A tubular inner cylinder rotating shaft 13 that is inserted through is provided. The outer cylinder 20 is provided with a tubular outer cylinder rotating shaft 23 that is rotatably inserted into the inner cylinder rotating shaft 13.
In the present embodiment, the inner cylinder 10 is provided with an inner cylinder rotating shaft 13 at both one end and the other end. That is, a tubular inner cylinder rotating shaft 13 (13a) that is rotatably inserted into the other support shaft 92 is provided at one end of the inner cylinder 10, and the other end of the inner cylinder 10 is rotatable about the one support shaft 82. A tubular inner cylinder rotating shaft 13 (13b) to be inserted is provided. The inner cylinder rotation shaft 13 (13a) on one end side of the inner cylinder 10 is rotatably inserted into the other support shaft 92. Moreover, as shown in FIG. 3, the inner cylinder rotating shaft 13 (13b) on the other end side of the inner cylinder 10 has a tubular body 14 provided at the center of the bottom of the inner cylinder 10 and one end in the axial direction of the inner cylinder 10 is tubular. A shaft tube body 15 connected to the inside of the body 14 by a spline gear is provided.
The shaft tube body 15 is provided in a state of penetrating the top plate 4 of the gantry 2 provided inside the outer shell 1. The gantry 2 includes a cylindrical side wall 3 erected on the base 1a and a top plate 4 provided at the upper end edge of the side wall 3 so that a cooling liquid can be stored therein.
The inner cylinder 10 is supported by the outer cylinder 20 while being placed on the bottom of the outer cylinder 20. In the present embodiment, for example, the inner cylinder 10 rotates at a peripheral speed of the outer peripheral edge of about 100 m / s.

Further, the outer cylinder 20 has an outer cylinder rotating shaft 23 (23a) that is rotatably inserted into the other support shaft 92 at one end, and an inner cylinder rotating shaft 13 (13b) on the other end side of the inner cylinder 10 at the other end. ) And an outer cylinder rotating shaft 23 (23b) that is rotatably inserted. The outer cylinder rotation shaft 23 (23 a) on one end side of the outer cylinder 20 is configured to include a triangular pyramid-shaped support member 24 that is supported by the support base 5 provided at the upper part of the outer shell 1. The support member 24 is rotatably inserted into and supported by a funnel-shaped receiving portion 6 provided on the support base 5, and the entire outer cylinder 20 is supported by being suspended from the receiving portion 6. A space surrounded by the support 5 and the outer shell 1 inside the receiving portion 6 is filled with a heating liquid.
The outer cylinder rotating shaft 23 (23b) on the other end side of the outer cylinder 20 is provided at the center of the bottom of the outer cylinder 10, and is rotatably inserted into the shaft tube body 15 on the other axial end side of the inner cylinder 10. ing. In the present embodiment, the outer cylinder 20 rotates, for example, at a peripheral speed of the outer peripheral edge of about 50 m / s.

The power acquisition mechanism 30 is connected to the first driving gear 31 provided on the inner cylinder rotation shaft 13 (13b) on the other end side of the inner cylinder 10 and the outer cylinder rotation shaft 23 (23b) on the other end side of the outer cylinder 20. A configuration comprising a second driving gear 32 provided via the bottom wall of the cylinder 20 and a generator 33 driven in linkage with at least one of the first driving gear 31 and the second driving gear 32. It is said.
Specifically, the power acquisition mechanism 30 includes a first driven gear 34 that meshes with the first driving gear 31, a second driven gear 35 that meshes with the second driving gear 32, and a shaft 36 connected to the generator 33. The generator 33 is operated by the rotation of the shaft 36. The first driving gear 31 and the first driven gear 34 are located inside the gantry 2 provided inside the outer shell 1.
The second driving gear 32 and the second driven gear 35 are provided on the outside of the gantry 2. Further, the shaft 36 is rotatably supported on the outer shell 1 via a ball bearing 37.

  As shown in FIGS. 1, 2, and 5, at one end of the inner cylinder 10, a moving blade 40 that receives gas flowing from the supply port 11 and applies a rotational force to the inner cylinder 10 is provided. The rotor blades 40 are arranged on the one end side of the inner cylinder 10 along the axial direction in an equiangular relationship around the rotation axis of the inner cylinder 10 and receive gas guided by a guide blade 70 described later. A plurality of blades 41 having a surface and a closing plate 42 for closing the upper side in the axial direction of the inner cylinder 10 of the blade 41 group are provided. The gas flows from the side of these blades 41 and flows below the inner cylinder 10.

Further, as shown in FIGS. 13 and 14, a guide blade 50 is provided on the other end of the inner cylinder 10 and on the outer side thereof. The guide vane 50 receives the gas discharged from the discharge port 12 and applies a rotational force to the inner cylinder 10 and guides the gas discharged from the discharge port 12 in the gas flow direction of the other flow path Rb.
The guide blade 50 has a bowl-shaped guide plate body 51 that changes the direction of the gas from the discharge port 12 in the flow direction of the gas in the other flow path Rb, and a plurality of blade members 52 provided inside the guide plate body 51. It has. The guide plate 51 is formed such that the diameter of the opening is larger than that of the inner cylinder 10 so that the discharge port 12 of the inner cylinder 10 is located on the inner side, and a gas is formed between the opening end and the outer wall of the inner cylinder 10. It forms the outlet. Moreover, the center bottom part of the guide plate body 51 is inserted into the inner cylinder rotating shaft 13 (13b) on the other end side of the inner cylinder 10, and is fixed to the inner cylinder rotating shaft 13 (13b). The blade member 52 is blown to the bottom of the guide plate body 51 and includes a surface for receiving gas that flows to the outer side in the circumferential direction of the guide plate body 51. The blade member 52 rotates in the same direction as the rotational force applied to the inner cylinder 10 by the moving blade 40. A force is applied to the inner cylinder 10.

Furthermore, a porous member 60 through which gas and cooling liquid passing through the one passage Ra can pass is provided in the inner cylinder 10. The porous member 60 is a wound sheet-like metal net 61. Since the porous member 60 has a configuration in which the net 61 is wound, the structure is simplified. In addition, a plate body 62 having a large number of through holes is provided above and below the net 61.
Further, a fin 65 is provided inside the inner cylinder 10 and on the supply port 11 side of the one channel Ra to push the accumulated gas into the discharge port 12 side. The fin 65 is provided so as to be suspended from a lower edge of a later-described feed pipe 97, and is bent in one circumferential direction. The fin 65 forms a vortex in the gas in the inner cylinder 10 by the rotation of the inner cylinder 10, and makes it easy for the gas staying in the upper part of the inner cylinder 10 to descend.

  A plurality of guide vanes 70 that guide gas to the supply port 11 are provided on the inner periphery of one end side of the outer cylinder 20. The guide blade 70 includes an air guide plate 71. The air guide plate 71 is arranged in an equiangular relationship at a portion surrounding the outer peripheral portion of the rotor blade 40, and has a surface along the axial direction. The air guide plate 71 is recessed in one circumferential direction, and imparts centrifugal force to the gas flowing into the supply port 11 by the recessed surface. Further, the guide blade 70 includes a hook-shaped guide plate 72. The guide plate 72 is suspended from the upper wall of the outer cylinder 20 by a bolt 73 inserted into the upper wall of the outer cylinder 20 and a nut 74 provided on the guide plate 72.

Further, the convection temperature difference prime mover S1 includes a cooling liquid circulation pipe 80 that cools the gas passing through the one flow path Ra and circulates the cooling liquid by spraying the cooling liquid into the inner cylinder 10. ing. A cooling unit 81 that cools the cooling liquid is provided in the middle of the cooling liquid circulation line 80.
The cooling liquid circulation pipe 80 is provided in the outer shell 1 and has a cooling liquid inlet 83 on one end side and a plurality of outlets 84 for spraying the cooling liquid on the inner cylinder 10 on the other end side. . The cooling liquid circulation pipe 80 includes a support shaft 82 that pivotally supports the other ends of the inner cylinder 10 and the outer cylinder 20 and a cooling liquid circulation pipe body 80a. The cooling liquid circulation tube 80 a flows out from the inlet 85 for injecting the cooling liquid supplied to the inlet 83 of the one support shaft 82 and the outlet 12 of the inner cylinder 10 after cooling the gas in the one channel Ra. The recovery port 86 for recovering the cooled liquid is provided, and the cooling liquid is circulated from the recovery port 86 to the injection port 85 again.

On the other hand, the support shaft 82 stands upright with one end in contact with the outer shell 1. A plurality of inflow ports 83 are provided on the tube wall on the other end side of the one support shaft 82.
The one support shaft 82 supplies the cooling liquid in the one support shaft 82 to the inner tube rotation shaft 13 at a position where the inner tube rotation shaft 13 (13b) on the other end side of the inner tube 10 is inserted. A hole 82a is provided.
The inlet 85 of the cooling liquid circulation tube 80 a is connected to the inlet 83 of the one support shaft 82 through the space inside the gantry 2. The recovery port 86 of the cooling liquid circulation tube 80 a is provided in the outer shell 1. The recovery port 86 recovers the cooling liquid through the hole 88 and the groove 89 a of the sliding contact member 89. A plurality of holes 88 are provided at the other end of the outer cylinder 20 along the circumferential direction of the outer cylinder 20. The sliding contact member 89 is in sliding contact with the surface of one end portion of the outer cylinder 20 and surrounds a plurality of holes 88 provided in the outer shell 1.
The cooling unit 81 is provided in the middle of the cooling liquid circulation tube 80a. In the present embodiment, the temperature of the cooling liquid cooled by the cooling unit 81 is about −50 ° C.

Further, the convection temperature difference prime mover S1 heats the gas passing through the other flow path Rb and circulates the heated liquid by spraying the heated liquid between the inner cylinder 10 and the outer cylinder 20. , A heated liquid circulation line 90 is provided. Further, a heating unit 91 for heating the heated liquid is provided in the middle of the heated liquid circulation conduit 90.
The warming liquid circulation conduit 90 includes the other support shaft 92, a cylindrical body 10a, and a warming liquid circulation tube 90a. The other support shaft 92 is provided on the outer shell 1, has an inflow port 93 for a heated liquid at one end side, and has an outflow port 94 at the other end side, and one end of the inner cylinder 10 and the outer cylinder 20. Is supported. The cylindrical body 10 a covers the inner cylinder 10, and a flow passage through which the heated liquid flows from the outlet 94 of the other support shaft 92 is formed between the cylindrical body 10 a and the outer cylinder 20. Thus, a large number of jets 99 through which the liquid flows out are formed. The heated liquid circulation tube 90 a includes an injection port 95 connected to the inlet 93 of the other support shaft 92 and a recovery port 96 that recovers the heated liquid, and warms the recovery port 96 to the injection port 95 again. Circulate the liquid. The warming liquid is injected from the injection port 95, is ejected from the ejection port 99 toward the outer cylinder 20 through the flow passage, and warms the gas in the other flow path Rb.
The cylindrical body 10a is provided to be rotatable with respect to the inner cylinder 10.

The other support shaft 92 is formed with an inlet 93 at one end to which the inlet 95 of the heated liquid circulation tube 90a is connected. The outlet 94 is formed at the other end of the other support shaft 92 and is located inside the inner cylinder rotating shaft 13 (13 a) on one end side of the inner cylinder 10. Further, the lower end of the inner cylinder rotating shaft 13 (13a) on one end side of the inner cylinder 10 is closed, and the inside thereof communicates with the flow path of the cylinder 10a via a plurality of feed pipes 97. . The feed pipes 97 are arranged in an equiangular relationship in the circumferential direction of the inner cylinder 10.
The jet outlet 99 of the cylinder 10a is provided over the whole outer peripheral surface of the cylinder 10a. The other support shaft 92 is provided with a supply hole 92 a, and this supply hole 92 a supplies the heated liquid flowing inside to the space surrounded by the support 5 and the outer shell 1 inside the receiving portion 6. . In the present embodiment, a pressure of about 10 kg / cm ^{2 to} 100 kg / cm ² ( ¹ MPa to 10 MPa) is applied to the heated liquid ejected from the ejection port 99.

A recovery port 96 of the heated liquid circulation tube 90 a is provided in the outer shell 1. The recovery port 96 has a plurality of holes 98 arranged along the circumferential direction of the outer cylinder 20 on the upper side of the hole 88 communicating with the recovery port 86 for recovering the cooling liquid of the outer cylinder 20, and the sliding contact member 89. The heated liquid is recovered through another groove 89b provided on the upper side of the groove 89a.
Between the hole 88 into which the cooling liquid flows and the hole 98 into which the warming liquid flows, a ridge 25 is provided that partitions the cooling liquid and the warming liquid that are pressed against the wall surface of the outer cylinder 20 and flows.
The warming part 91 is provided in the middle of the warming liquid circulation tube 90a. In this embodiment, the warming liquid warmed by the warming unit 91 is about 200 ° C to 250 ° C.
Although not shown, the cooling liquid circulation line 80 and the warming liquid circulation line 90 are provided with pumps for sucking up these liquids from the respective recovery ports 96 to the injection port 95.

  Further, in the convection temperature difference driving device S1, the cooling liquid and the heating liquid as the lubricating oil leaking from the inner cylinder rotating shaft 13 and the outer cylinder rotating shaft 23 and accumulated on the base 1a in the outer shell 1 A gear pump 8 is provided. The gear pump 8 includes a pulley 8a for operation, and operates in conjunction with rotation of the shaft 36 via a belt hung on the pulley 8a and a pulley 36a provided on the shaft 36.

Next, an example of a system for operating the convection temperature difference prime mover S1 will be described.
As shown in FIG. 17, in this system, the cooling liquid circulation pipe 80a discharges the air bubbles in the check liquid 110 provided on the upstream side and the downstream side of the cooling unit 81, respectively, and the cooling liquid circulation pipe 80a. And a gas vent valve 111. The warming liquid circulation tube 90a includes a check valve 112 provided on the upstream side of the warming unit 91, and a gas vent valve 113 that discharges bubbles in the warming liquid circulation tube 90a. The cooling unit 81 is a radiator. The heating unit 91 burns the LP gas from the LP gas storage tank 91a to heat the warming liquid.

Further, this system is provided with a flow rate adjusting mechanism 120 that adjusts the flow rates of the cooling liquid flowing through the cooling liquid circulation pipe body 80a and the warming liquid flowing through the heating liquid circulation pipe body 90a.
This flow rate adjusting mechanism 120 takes in a part of both the liquid from the cooling liquid flowing through the cooling liquid circulation pipe body 80a and the warming liquid flowing through the heating liquid circulation pipe body 90a, and each pipe body 80a, The liquid of approximately the same amount as the liquid taken in from 90a flows into each tube 80a, 90a. In contrast, in the flow rate adjusting mechanism 120, the flow rate of the liquid flowing through one of the cooling liquid circulation tube 80a and the heated liquid circulation tube 90a is smaller than the flow rate of the liquid in the tubes 80a and 90a flowing through the other. In this case, the liquid taken up preferentially is caused to flow into one of the pipe bodies 80a and 90a having a reduced flow rate.
Specifically, the flow rate adjusting mechanism 120 includes an upstream branch pipe 121, an upstream branch pipe 122, a main pipe 123, a downstream branch pipe 124, and a downstream branch pipe 125. The upstream branch pipe 121 branches the cooling liquid between the recovery port 86 of the cooling liquid circulation pipe body 80 a and the check valve 110 closer to the recovery port 86 than the cooling unit 81. The upstream branch pipe 122 branches the heated liquid between the recovery port 96 of the heated liquid circulation tube 90 a and the check valve 112 on the recovery port 96 side of the heating unit 91. The main pipe 123 includes a pump 123a that always operates while the upstream branch pipes 121 and 122 merge. The downstream branch pipe 124 branches from the main pipe 123 and merges with the cooling liquid circulation pipe body 80a and opens and closes based on the flow rate of the warming liquid flowing through the warming liquid circulation pipe body 90a. The downstream branch pipe 125 branches from the main pipe 123 and merges with the heated liquid circulation pipe body 90a and opens and closes based on the flow rate of the cooling liquid flowing through the cooling liquid circulation pipe body 80a.

Each upstream branch pipe 121, 122 is provided with a check valve 119 to prevent backflow from the upstream branch pipe 121 to the cooling liquid circulation pipe body 80a and from the upstream branch pipe 122 to the warming liquid circulation pipe body side 90a. To do.
Further, an electromagnetic valve 127 is provided in the downstream branch pipe 124 connected to the cooling liquid circulation pipe body 80a. The electromagnetic valve 127 is provided between the warming portion 91 of the warming liquid circulation tube 90a and the check valve 112 on the upstream side of the warming portion 91, and the warming liquid flowing through the warming liquid circulation tube 90a. It opens and closes based on the flow rate measured by the heated liquid flow rate measuring device 126 that measures the flow rate. This solenoid valve 127 is normally open, but when the flow rate of the warming liquid measured by the warming liquid flow rate measuring device 126 becomes a certain amount or less, the switch 128 is turned on and connected to the power source 150. Operates and closes the downstream branch pipe 124.
In addition, an electromagnetic valve 130 is provided in the downstream branch pipe 125 connected to the heated liquid circulation pipe body 90a. The electromagnetic valve 130 is provided between the cooling part 91 of the cooling liquid circulation pipe body 80a and the check valve 110 upstream of the cooling part 91, and measures the flow rate of the cooling liquid flowing through the cooling liquid circulation pipe body 80a. It opens and closes based on the flow rate measured by the cooling liquid flow rate measuring device 129. The electromagnetic valve 130 is normally open, but when the flow rate of the cooling liquid measured by the cooling liquid flow rate measuring device 129 is below a certain amount, the switch 131 is turned on and connected to the power source 150 to operate. The downstream branch pipe 125 is closed.

The flow rate adjusting mechanism 120 includes a receiving member 135, a tank 136, and a supply pipe 137.
The receiving member 135 receives the cooling liquid and the heating liquid that have leaked from the sliding contact portion between the outer cylinder 20 and the sliding contact member 89. The receiving member 135 has a substantially U-shaped cross section so as to cover the lower portion of the outer cylinder 20 and the sliding member 89, and the cooling liquid and the warming liquid are stored in the interior 135a.
The tank 136 is provided with a liquid replenishing port 136a for accumulating liquid from the receiving member 135 and replenishing liquid that has decreased due to volatilization or the like. The tank 136 communicates with the interior 135 a of the receiving member 135 through the recovery pipe 138.
The supply pipe 137 supplies the liquid in the tank 136 to the main pipe 123 when the amount of liquid stored in the tank 136 exceeds a predetermined amount. The supply pipe 137 joins between the junction of the upstream branch pipes 121 and 122 and the pump 123a. The supply pipe 137 includes an electromagnetic valve 141 for opening and closing the supply pipe 137 and a check valve 142 for preventing liquid from flowing backward from the main pipe 137. The electromagnetic valve 141 is provided between the confluence of the main pipe 123 and the replenishment pipe 137 and the confluence of the upstream branch pipes 121 and 122 by the liquid amount measuring device 139 that measures the amount of liquid in the tank 136. It opens and closes together with the solenoid valve 140.

The operations of the electromagnetic valve 140 and the electromagnetic valve 141 are as follows.
When the liquid amount measuring device 139 detects that the amount of liquid in the tank 136 is less than a predetermined amount, the power supply 150 is connected to the electromagnetic valve 141 by the switch 143, the electromagnetic valve 141 is closed, and the electromagnetic valve 140 is connected to the power supply 150. Disconnect and open. In this case, the liquid from the upstream branch pipes 121 and 122 is sucked by the pump 123a. Further, when the liquid amount measuring device 139 detects that the amount of liquid in the tank 136 is larger than a predetermined amount, the switch 143 connects the power source 150 to the electromagnetic valve 140 and the electromagnetic valve 140 is closed. It is disconnected from the power supply 150 and opened. In this case, the liquid in the tank 136 is sucked by the pump 123a.

Further, a compressor 145 is provided for supplying a gas for rotating the inner cylinder 10 and the outer cylinder 20 into the outer cylinder 20 by using the cooling liquid circulation pipe body 80a before flowing the cooling liquid and the heating liquid. Yes. The gas from the compressor 145 does not flow into the cooling unit 81 due to the check valve 110 provided on the downstream side of the cooling unit 81.
In FIG. 17, reference numeral 146 denotes a pressure gauge that measures the pressure of the cooling liquid flowing inside the cooling liquid circulation tube 80a.

Therefore, according to this system, the convection temperature difference prime mover S1 according to the first embodiment operates as follows.
First, gas is introduced into the outer cylinder 20 by the compressor 145. In this state, the cooling liquid is circulated by the cooling liquid circulation line 80, and the warming liquid is circulated by the heating liquid circulation line 90.
At this time, the cooling liquid is supplied to the gantry 2 from the inlet 85 through the cooling liquid circulation pipe body 80a of the cooling liquid circulation pipe 80, and subsequently, the inside of the one spindle 82 from the inlet 83 of the one spindle 82. It passes through and flows out from the outlet 84 into the inner cylinder 10. Thereafter, the cooling liquid cools the gas in one flow path Ra in the inner cylinder 10, passes through the discharge port 12 and the guide vane 50, passes through the cooling liquid circulation pipe body 80 a from the recovery port 86, and is led to the injection port 85 again. It is burned. The cooling liquid is heated by the cooling of the gas, but is cooled again by the cooling unit 81 in the middle of the cooling liquid circulation pipe body 80a. Therefore, the cooling liquid sprayed in the inner cylinder 10 is cooled to a low temperature state, and the cooling state of the gas in the flow path Ra is improved.

On the other hand, the warming liquid is fed from the inlet 93 of the other support shaft 92 into the other support shaft 92 and into the inner cylinder rotating shaft 13 (13a) on one end side of the inner cylinder 10 through the heating liquid circulation line 90. It passes through the tube 97 and the flow passage, and is ejected from the ejection port 99 to the outside of the inner cylinder 10. Subsequently, the warming liquid warms the gas in the other flow path Rb, and then is led from the recovery port 86 through the warming liquid circulation tube 90a to the injection port 95 again. The warming liquid is cooled by warming the gas in the other flow path Rb, but is warmed again by the warming portion 91 in the middle of the warming liquid circulation tube 90a. Therefore, the warming liquid sprayed between the inner cylinder 10 and the outer cylinder 20 is in a high temperature state again, and the warming state of the gas in the other flow path Rb is improved.
In this case, the gas flowing through the other flow path Rb is directly heated in the space between the outer cylinder 20 and the inner cylinder 10 by the heated liquid ejected from the ejection port 99. Therefore, the gas in the other flow path Rb is heated without going out of the outer cylinder 20, so that the structure of the other flow path Rb is simplified.
In addition, since the one support shaft 82 is also used as a part of the cooling liquid circulation conduit 80 and the other support shaft 92 is also used as a part of the warming liquid circulation conduit 90, a dedicated flow through which these liquids flow out. Compared with the case where a separate pipe line is provided, the structure is simplified. Therefore, there is no adverse effect on the convection of the gas generated in the one flow path Ra and the other flow path Rb, the energy loss in the convection of the gas is reduced, and the inner cylinder 10 and the outer cylinder 20 are used as the rotational force. Is efficiently applied.

At this time, when the flow rate of the cooling liquid flowing through the cooling liquid circulation pipe body 80a decreases, this is detected by the cooling liquid flow rate measuring device 129, the switch 131 is turned on, and the electromagnetic valve 130 is closed. Therefore, the liquid in the main pipe 123 flows only into the downstream branch pipe 124 and flows into the cooling liquid circulation pipe body 80a. On the other hand, when the flow rate of the warming liquid flowing through the warming liquid circulation pipe body 90a decreases, this is detected by the warming liquid flow rate measuring device 126, the switch 128 is turned on, and the electromagnetic valve 127 is closed. Therefore, the liquid in the main pipe 123 flows only into the downstream branch pipe 125 and flows into the heated liquid circulation pipe body 90a.
That is, the flow rates of the cooling liquid flowing through the cooling liquid circulation pipe body 80a and the warming liquid flowing through the heating liquid circulation pipe body 90a are ensured to be a certain amount or more.

  When the amount of liquid accumulated in the tank 136 increases, the liquid amount measuring device 139 detects this. At this time, the switch 143 connects the power supply 150 to the electromagnetic valve 141 side, opens the electromagnetic valve 141, and closes the electromagnetic valve 140. Thereby, the liquid in the tank 136 is sucked by the pump 123a and flows into the cooling liquid circulation pipe body 80a and the warming liquid circulation pipe body 90a. Therefore, even if the liquid leaks and the cooling liquid flowing through the cooling liquid circulation conduit 80 and the warming liquid flowing through the warming liquid circulation conduit 90 decrease, they can be replenished in a timely manner.

As a result, the flow path Ra from the supply port 11 of the inner cylinder 10 through the inside of the inner cylinder 10 to the discharge port 12 and the discharge port 12 of the inner cylinder 10 to the supply port 11 through the outside of the inner cylinder 10 are reached. On the other hand, convection of gas passing through the flow path Rb occurs. Due to this convection, the inner cylinder 10 rotates via the moving blade 40 and the guide blade 50.
When the inner cylinder 10 rotates, the rotational force is generated by the inner cylinder rotating shaft 13 (13b), the first driving gear 31, the first driven gear 34, the shaft 36, the second driven gear 35, and the second driving gear on the other end side. 32 and the outer cylinder 20 is transmitted to the outer cylinder 20 via the outer cylinder rotating shaft 23 (23b) on the other end side of the outer cylinder 20, and the outer cylinder 20 also rotates in the same direction as the rotation direction of the inner cylinder 10.

At this time, since the structure of the other flow path Rb is simplified and energy loss in gas convection is reduced, this convection energy is efficiently applied to the inner cylinder 10 and the outer cylinder 20 as a rotational force.
At this time, the gas in one flow path Ra that has cooled and lowered in the inner cylinder 10 and reached the discharge port 12 is sequentially discharged from the discharge port 12 provided at the other end of the inner tube 10, and the guide vanes 50. To. In this guide vane 50, the gas stops at the guide plate body 51, is guided so as to be along the gas flow direction of the other flow path Rb outside the guide plate body 51 in the circumferential direction, and the guide plate body The inner cylinder 10 is rotated by stopping against the surface of the blade member 52 provided in the interior 51.

Further, the gas in contact with the blade member 52 of the guide vane 50 is sent out in the opposite direction to the rotation direction of the inner cylinder 10 in the gas flow direction of the other flow path Rb, and between the outer cylinder 20 and the inner cylinder 10. To the space.
At this time, the gas from the discharge port 12 is blown out in the flow direction of the other flow path Rb and is less likely to stay in the lower part in the outer cylinder 20. Thereby, convection of gas is performed smoothly.
Thus, the gas discharged from the discharge port 12 rises as a vortex.

The gas in the other flow path Rb reaches the guide blades 70 at the upper part of the outer cylinder 20 in a compressed state by the centrifugal force applied by the expansion and vortex flow caused by the heating of the heated liquid, and stops at the guide plate 72. Then, the flow direction is directed inward in the circumferential direction of the outer cylinder 20.
At this time, the gas impinges on the concave curved surface of the air guide plate 71 in the guide blade 70. Then, the flow direction is changed substantially in the radial direction by the air guide plate 71. Since each air guide plate 71 of the guide blade 70 is bent in one circumferential direction, the gas is further subjected to centrifugal force to change the flow direction. Then, the gas flows in from the supply port 11 on the outer peripheral portion of the blade 41, strikes the blade 41 of the moving blade 40, escapes to the inner peripheral portion of the moving blade 40, and flows into the inner cylinder 10. Therefore, since the gas compressed by the guide blade 70 and applied with centrifugal force strikes the blade 41 of the moving blade 40 almost at right angles, the blade 41 of the moving blade 40 receives sufficient gas force. Therefore, the conversion efficiency for converting the gas energy into the rotational force of the inner cylinder 10 is greatly improved, and the power generation efficiency is improved. Further, at this time, the gas is further compressed between the blades 41 and the flow velocity becomes extremely fast, so that the energy for striking the blade 41 is increased, and the convection energy is efficiently transferred as the rotational force of the inner cylinder 10. It is given to the tube 10.

The gas that has passed through the blade 41 group of the moving blade 40 from the supply port 11 and entered the inner cylinder 10 has its convection energy converted into the rotational force of the inner cylinder 10 via the moving blade 40, and has a certain temperature. It is high. Therefore, the gas tends to stay in the upper part of the inner cylinder 10. However, this gas is pushed into the discharge port 12 by the fin 65 that rotates with the rotation of the inner cylinder 10. That is, the gas that has entered from the supply port 11 moves toward the discharge port 12 with almost no stagnation, so that the convection state of the gas becomes good.
Then, this gas reaches the discharge port 12 again, circulates through the other flow path Rb and the one flow path Ra in the same manner as described above, and rotates the inner cylinder 10 and the outer cylinder 20.

  When the inner cylinder 10 is rotating, the cooling liquid strikes the mesh 61 of the porous member 60 within the inner cylinder 10 and moves outward from the mesh of the mesh 61 by the centrifugal force of the rotated inner cylinder 10. It reaches the inner surface of the inner cylinder 10, flows down the inner surface of the inner cylinder 10, and is discharged from the discharge port 12 to the outside of the inner cylinder 10. In this case, since the cooling liquid stays temporarily in the net 61 of the porous member 60, the time for contacting the cooling liquid in the one flow path Ra is longer than that in the case where the porous member 60 is not provided. The efficiency of heat exchange with the gas flowing through the path Ra is improved, while the gas flowing through the flow path Ra is further cooled. For this reason, the gas flowing through the one-side channel Ra is likely to descend, and the flow rate of the gas becomes extremely fast.

  Further, in the outer cylinder 20, the cooling liquid and the warming liquid are pressed against the inner wall of the outer cylinder 20 by centrifugal force and accumulated, and from the holes 88 and 98 through the grooves 89 a and 89 b, the recovery ports 86 and 96. At this time, since the hole 88 and the hole 98 are separated by the protrusion 25, the cooling liquid and the heating liquid are hardly mixed, and the cooling liquid and the heating liquid can be collected separately. Therefore, the temperature of the recovered cooling liquid does not rise so much, and the temperature of the recovered warming liquid does not drop so much, so that the cooling liquid 81 is cooled efficiently and the heating liquid 91 is heated efficiently. Can be done well.

Furthermore, when the inner cylinder 10 and the outer cylinder 20 are rotated by convection, the power acquisition mechanism 30 can obtain power from both because the inner cylinder 10 and the outer cylinder 20 rotate in the same direction. That is, the rotational force of the inner cylinder 10 is transmitted through the inner cylinder rotating shaft 13 (13b), the first driving gear 31, the first driven gear 34, the shaft 36, and the second driven gear 35 on the other end side of the inner cylinder 10. Since the outer cylinder 20 itself rotates the second driving gear 32, the rotation of the first driving gear 31 is transmitted to the generator 33, which is transmitted by the generator 33. Power is generated.
In addition, the inner cylinder 10 and the outer cylinder 20 are supplied with cooling liquid or warming liquid as lubricating oil to the bearing portion of the inner cylinder rotation shaft 13 of the inner cylinder 10 and the bearing portion of the outer cylinder rotation shaft 23 of the outer cylinder 20. Therefore, it rotates smoothly.

[Second Embodiment]
18 to 21 show a convection temperature difference prime mover S2 according to the second embodiment of the present invention.
Unlike the convection temperature difference prime mover S1, the convection temperature difference prime mover S2 is provided with a mechanism for recovering the cooling liquid and the heated liquid by the relative rotation of the inner cylinder 10 and the outer cylinder 20.

Specifically, the guide blade 50 is provided around the inner cylinder rotation shaft 13 (13b), and the guide plate body 51 has a concave curved surface that extends from the inner cylinder rotation shaft 13 (13b) toward the outer side of the inner cylinder 10. A blade member 52 provided inside the guide plate 51 is provided.
In addition, the guide plate body 51 of the guide blade 50 has a cooling liquid from the discharge port between the inner surface member 53 that forms the inner surface of the guide plate body 51 and the inner surface member 53 provided outside the inner surface member 53. And an outer surface member 54 in which a space communicating with the recovery port 86 of the cooling liquid circulation pipe body 80a is formed. A plurality of holes 100 through which cooling liquid that collects on the inner side of the inner surface member 53 in the axial direction by the centrifugal force generated by the rotation of the inner cylinder 10 flows is arranged in the opening edge portion of the inner surface member 53.

Further, around the guide blade 50, a recovery blade 55 that scrapes off the warmed liquid collected in a recess provided on the outer side in the axial direction of the outer cylinder 20 near the lower portion inside the outer cylinder 20, and a lower side of the recovery blade 55 A basin-shaped basin member 56 in which a heated liquid from the recovery blade 55 circulates between the outer surface member 54 and a space communicating with the recovery port 96 of the heated liquid circulation tube 90a is formed. Is provided.
Further, the shaft tube body 15 of the inner cylinder rotation shaft 13 (13b) inserted through the one support shaft 82 is slidably contacted with the one support shaft 82 by a sliding contact portion 101 provided at the top and bottom. Further, the shaft tube body 15 is formed with one passage 102 through which the cooling liquid flows and the other passage 103 through which the heating liquid flows, between the one support shaft 82. The inner cylinder rotating shaft 13 (13 b) is internally partitioned by a partition wall 104, and separates the one passage 102 and the other passage 103. On the other hand, the passage 102 is a part of the cooling liquid circulation pipe body 80a, and is formed in the recovery port 86 communicating with the space between the inner surface member 53 and the outer surface member 54 on the upper end side. The other passage 103 is a part of the heated liquid circulation tube body 90a, and is provided with a recovery port 96 communicating with the space between the outer surface member 54 and the tray member 56 on the upper end side.
Further, the upper end of the cylindrical body 10 a is joined to the air guide plate 71 of the guide blade 70 and is rotated together with the guide blade 70. Moreover, the upper part and the lower part of the inner periphery of the cylinder 10a slide with respect to the inner cylinder.
Other configurations are substantially the same as the convection temperature difference prime mover S1 of the first embodiment.

When operating this convection temperature difference prime mover S2, the cooling liquid is circulated through the cooling liquid circulation line 80 and the heating liquid is circulated through the heating liquid circulation line 90 in the same manner as in the first embodiment. The inner cylinder 10 and the outer cylinder 20 rotate.
Then, in a state where the inner cylinder 10 and the outer cylinder 20 are rotated, the cooling liquid flowing out from the outlet 84 of the one support shaft 82 flows down the inner wall of the inner cylinder 10 and falls to the inner surface member 53 of the guide plate body 51. The centrifugal force gathers at the opening edge of the guide plate 51, reaches the recovery port 86 from the hole 100, and is recovered in the cooling liquid circulation tube 80a. Further, the heated liquid flowing out from the outlet 99 of the cylinder 10a is accumulated in the recess by the centrifugal force of the outer cylinder 20, and is scraped off by the recovery blade 55 and recovered from the recovery port 96 to the heated liquid circulation tube 90a. Is done. In this case, since the cooling liquid is recovered without leaking to the outer cylinder 20 side, it becomes difficult to mix with the warming liquid and can be recovered separately. Therefore, the temperature of the recovered cooling liquid does not increase so much and the temperature of the recovered warming liquid does not decrease so much, so that the cooling by the cooling unit 81 and the heating by the heating unit 91 can be performed efficiently.
Furthermore, since the outer cylinder 20 rotates and the cylindrical body 10a also rotates through the air guide plate 71 of the guide blade 70 and the jet port 99 itself rotates, the heated liquid from the jet port 99 also rotates. Become. For this reason, the rotation of the gas in the warming liquid and the other flow path Rb becomes substantially the same, fluid friction is reduced, and gas convection is performed smoothly, so that the energy from the convection efficiently generates the inner cylinder 10 and the outer cylinder 20. Is applied as a rotational force.
Other operations and effects are the same as those in the first embodiment.

[Third embodiment]
Next, a convection temperature difference prime mover S3 according to a third embodiment of the present invention will be described using FIG.
The convection temperature difference prime mover S3 has substantially the same configuration as the convection temperature difference prime mover S2 according to the second embodiment, but unlike this, the cooling liquid and the heating liquid are collected at the same collection port 86. The cooling liquid circulation pipe body 80a and the heated liquid circulation pipe body 90a are partly used.
Specifically, this convection temperature difference prime mover S3 does not have the outer surface member 54, and the cooling liquid flows out from the opening of the guide vane 50 to the outer cylinder 20 side.
In addition, a recovery pipe made of the shaft tube body 15 inserted coaxially with the one support shaft 82 is provided. This recovery pipe is provided with a recovery port 86 communicating with the space between the inner surface member 53 of the guide plate body 51 and the tray-shaped member 56 at the upper part, and the cooling liquid circulation pipe body 80a and the heating liquid circulation pipe at the lower end side. The body 90a communicates with the collection tube 300 that shares the body 90a.
Other configurations are the same as those in the above embodiment.

When operating this convection temperature difference prime mover S3, the cooling liquid is circulated through the cooling liquid circulation line 80, the heating liquid is circulated through the heating liquid circulation line 90, and the inner cylinder as in the above embodiment. 10 and the outer cylinder 20 rotate.
Then, in a state where the inner cylinder 10 and the outer cylinder 20 are rotated, the cooling liquid that has flowed out from the outlet 84 of the one support shaft 82 flows down the inner wall of the inner cylinder 10 and falls onto the guide plate body 51, and is caused by centrifugal force. Go to the outer cylinder 20 side. The cooling liquid accumulates in the recess by the centrifugal force of the outer cylinder 20 together with the heated liquid flowing out from the outlet 84 of the cylinder 10a, and is scraped off by the recovery blade 55 to the recovery tube 300 from the recovery port 86. To be recovered. In this case, the cooling liquid and the heating liquid are not collected separately, so that the structure is simplified accordingly.
Other actions and effects are the same as in the above embodiment.

[Fourth embodiment]
23 to 25 show a convection temperature difference prime mover S4 according to a fourth embodiment of the present invention.
The convection temperature difference prime mover S4 is substantially the same as the convection temperature difference prime mover S2 according to the second embodiment. However, unlike this, the lower end of the support shaft 82 is separated from the base 1a and the lower end is inward. The inner cylinder rotating shaft 13 (13b) on the other end side of the cylinder 10 is welded and fixed coaxially with the inner cylinder rotating shaft 13 (13b). The one support shaft 82 is rotatable in conjunction with the inner cylinder 10. In addition, the lower end of the one support shaft 82 is formed in the cooling liquid inflow port 83.

Further, as shown in FIGS. 23 and 24, the guide blade 70 is integrated with the cylindrical body 10a and is rotatable with respect to the inner cylinder 10. The outer cylinder 20 is capable of transmitting power to the guide blade 70 via the planetary gear mechanism 170.
In this planetary gear mechanism 170, the relationship among the rotation speed V1 of the inner cylinder 10, the rotation speed V2 of the cylinder 10a rotated by the guide blade 70, and the rotation speed V3 of the outer cylinder 20 is V1>V2> V3. The meshing relationship of the gears is determined so as to be. The gear ratio of the planetary gear mechanism 170 is set so that the inner peripheral speed of the outer cylinder 20 and the outer peripheral speed of the cylindrical body 10a are substantially the same.
Further, as shown in FIG. 23, the convection temperature difference prime mover S4 is provided with a detection mechanism for detecting an abnormality due to the secular change of the outer cylinder 20. This detection mechanism has a thin part 175 in which the thickness of the outer cylinder 20 is reduced. When the thin part 175 has a hole due to aging of the outer cylinder 20, it leaks from the upper part of the outer shell as the atmospheric pressure in the outer shell increases. The gas that comes out can be detected.

Furthermore, as shown in FIG. 25, unlike the convection temperature difference prime movers S1, S2, and S3 according to the above-described embodiments, a large number of air guide plates 71 are provided, and the concavely curved surface goes to the tip. Accordingly, the radius of curvature gradually decreases. The blade 41 is formed to have the same curvature as an arc whose diameter is the average diameter of the rotor blade 40, and the inclination angle is determined so that the efficiency of the rotational speed is optimized.
The other structure is substantially the same as the convection temperature difference prime mover S2 of the second embodiment.

When this convection temperature difference prime mover S4 is operated, the cooling liquid is circulated through the cooling liquid circulation pipe 80 and the heating liquid is circulated through the heating liquid circulation pipe 90 in the same manner as in the above embodiment. 10 and the outer cylinder 20 rotate.
In this case, when the inner cylinder 10 and the outer cylinder 20 are rotated, the planetary gear mechanism 170 causes the outer cylinder 20 to rotate at a low speed. Therefore, the frictional resistance against the gas in the outer shell 1 of the outer cylinder 20 is reduced, and the output efficiency of power from the inner cylinder 10 and the outer cylinder 20 is improved.
Further, the planetary gear mechanism 170 causes the inner peripheral speed of the outer cylinder 20 and the peripheral speed of the outer periphery of the cylindrical body 10a to be substantially the same, so that a frictional resistance is generated between the outer cylinder 20 and the cylindrical body 10a. The power output efficiency from the inner cylinder 10 and the outer cylinder 20 is improved. Furthermore, since the peripheral speed of the inner periphery of the outer cylinder 20 and the peripheral speed of the outer periphery of the cylinder 10a become substantially the same, the heat generation of the gas outside the inner cylinder 10 is suppressed.

Furthermore, since the air guide plate 71 of the guide blade 70 has a small radius of the concave surface, the centrifugal force applied to the gas flowing through the other flow path Rb is increased. That is, power transmission to the blade 41 of the rotor blade 40 that receives the gas flowing into the supply port 11 guided by the air guide plate 71 of the guide blade 70 is ensured, and the inner cylinder 10 is reliably rotated.
Further, when the thin portion 175 has a hole due to secular change, the gas in the outer cylinder 20 leaks into the outer shell 1 from the hole, and the atmospheric pressure in the outer shell 1 rises, and the gas leaks from the outer shell 1. By detecting the leaked gas, it is possible to detect an abnormality due to the secular change of the outer cylinder 20.
Other actions and effects are the same as in the above embodiment.

[Fifth embodiment]
26 to 33 show a convection temperature difference prime mover S5 according to a fifth embodiment of the present invention.
In this convection temperature difference prime mover S5, like the convection temperature difference prime mover S4 according to the fourth embodiment, one support shaft 82 is provided to be rotatable with respect to the inner cylinder rotary shaft 13 (13b). Further, unlike the convection temperature difference prime mover S4 according to the fourth embodiment, a rod 306 is provided at the lower end of the one support shaft 82. The rod 306 closes the lower end of the one support shaft 82, moves together with the one support shaft 82, and slidably contacts the inner cylinder rotation shaft 13 (13 b) via the bearing 305.

  In addition to the planetary gear mechanism 170 (hereinafter referred to as “first planetary gear mechanism 170”), the convection temperature difference prime mover S5 transmits power from the inner cylinder rotary shaft 13 (13b) to the one support shaft 82. A second planetary gear mechanism 310 for transmission is provided, and the support shaft 82 can rotate in conjunction with the inner cylinder 10.

As shown in FIGS. 28 and 32, the second planetary gear mechanism 310 has a central gear 311 whose shaft is fixed to a rod 306 provided at the lower end of the one support shaft 82 and that moves together with the one support shaft 82, Three gears 313 are provided around the gear 311 and rotatably supported by a disc body 312 provided at the lower end portion of the inner cylinder rotary shaft 13 (13b). The center of the disk body 312 is screwed into a right screw provided at the lower end of the inner cylinder rotation shaft 13 (13b), and is coupled to the inner cylinder rotation shaft 13 (13b). The three surrounding gears 312 are meshed with a gear 316 provided inside a cylindrical guide member 315 provided upright on the base 1a.
The second planetary gear mechanism 310 is provided in a room formed below the inner space of the outer shell 1 by a partition plate 317 provided in the lower portion of the outer shell 1. The partition plate 317 is provided at its center with a plain bearing 321 that supports the inner cylinder rotary shaft 13 (13b).
Further, the meshing relationship between the gear 311 and the gear 313 is the relationship between the rotation speed V1 of the inner cylinder 10 and the rotation speed V4 of the one support shaft 82 rotated by the inner cylinder rotation shaft 13 (13b) of the inner cylinder 10. It is determined that V4> V1.

  Moreover, as shown to FIGS. 26-29, the cylinder 10a is provided so that conversion is possible up and down. A lower portion of the cylindrical body 10 a is inserted into a cylindrical body 315 attached to a plurality of arms 314 fixed to the outer cylinder 20. The upper part of the cylindrical body 10 a is inserted into a cylindrical body 316 provided on the air guide plate 71 of the guide blade 70. The cylindrical body 10a is guided in sliding contact with any one of the cylindrical bodies 315 and 316, and is connected to either one. The cylindrical body 10a and the cylindrical bodies 315 and 316 are connected to each other by a plurality of slits provided in the cylindrical bodies 315 and 316 so as to protrude in the circumferential direction of the surface on the upper or lower side of the cylindrical body 10a. This is performed by fitting the convex body 318.

In addition, as shown in FIG. 26, a fin 320 is provided on the upper side of the one support shaft 82 for pushing the gas staying on the supply port 11 side of the one flow path Ra downward. As shown in FIG. 33, the fin 320 includes a tube body 321 inserted through the one support shaft 82 and four blades 322 provided around the tube body 321.
Further, the inside of the inner cylinder 10 has a configuration in which the porous member 60 provided around the one support shaft 82 is not provided.
Furthermore, a ring-shaped protrusion 330 that protrudes along the inner peripheral surface is provided on the discharge port 12 side of the inner cylinder 10. The ridge 330 has a rectangular cross section.
The other configuration is substantially the same as the convection temperature difference prime mover S4 of the fourth embodiment.

In the convection temperature difference prime mover S5, when the cylindrical body 10a is moved together with the outer cylinder 20 at the time of installation, the convex body 318 is fitted in the slit of the cylindrical body 315 provided with the arm 314. Thus, the side with the convex body 318 is set to the lower side, the cylindrical body 316 is inserted into the cylindrical body 10a, and the tip of the arm 314 is joined to the inner wall of the outer cylinder 20.
On the other hand, when the cylindrical body 10a is moved together with the guide wing 70, the cylindrical body 10a is inserted into the cylindrical body 10a while the cylindrical body 315 is inserted into the cylindrical body 10a. The slit of this cylindrical body 316 is fitted into the convex body 318 through insertion. Then, the arm 314 of the cylindrical body 315 is joined to the inner wall of the outer cylinder 20.

When the convection temperature difference prime mover S5 is operated, the cooling liquid is circulated through the cooling liquid circulation pipe 80 and the heating liquid is circulated through the heating liquid circulation pipe 90 in the same manner as in the above embodiment. And the outer cylinder 20 rotates.
In this case, in the state in which the inner cylinder 10 is rotated, the rotation of the one support shaft 82 is faster than the rotation of the inner cylinder 10 by the second planetary gear mechanism 310. For this reason, the gas staying on the supply port 11 side of the one-side channel Ra is pushed into the discharge port 12 side at high speed by the fins 320, so that the gas flow inside the inner cylinder 10 becomes high speed and the convection is smoothly performed. , Easy to get power.

Further, the gas in the one flow path Ra pushed into the discharge port 12 side by the fin 320 becomes a vortex by the rotation of the fin 320 and the rotation of the inner cylinder 10, and the inner peripheral surface of the inner cylinder 10 by the centrifugal force due to the vortex Compressed to the side. Then, a compressed gas layer is formed near the inner peripheral surface of the inner cylinder 10 by this gas. The gas in the compressed gas layer collides with the protrusion 330 on the discharge port 11 side, and passes over the protrusion 330 and is discharged from the discharge port 12.
At this time, the gas in the one flow path Ra collides with the protrusion 330 and its flow velocity is limited to some extent.
That is, when there is no protrusion 330, the gas on the discharge port 12 side in the vicinity of the inner peripheral surface of the inner cylinder 10 is sequentially discharged from the discharge port 12, and its density is significantly lower than that on the supply port 11 side. The density of the gas in the compressed gas layer tends to be non-uniform. On the other hand, when the protrusion 330 is provided, the protrusion 330 limits the gas flow in the vicinity of the inner peripheral surface of the inner cylinder 10 and keeps the gas on the discharge port 12 side. It can be made almost uniform throughout. Thereby, the cooling liquid from the outflow port 84 is sprayed on the compressed gas layer in which the gas is uniformly distributed, and the gas is cooled, so that the cooling efficiency is improved and power is easily obtained.

Further, since the cylinder body 10a can be selected to move together with either the guide blade 70 or the outer cylinder 20 at the time of installation, the cylinder body 10a rotates at a high speed when moved along with the guide blade 70 via the tubular body 316. Can be made. On the other hand, if it moves with the outer cylinder 20 via the cylindrical body 315 and the arm 314, the cylindrical body 10a can be rotated at low speed.
Other actions and effects are the same as in the above embodiment.

[Sixth embodiment]
FIG. 34 shows a convection temperature difference prime mover S6 according to the sixth embodiment of the present invention.
This convection temperature difference prime mover S6 is substantially the same as the convection temperature difference prime mover S1 according to the first embodiment, but unlike this, the one support shaft 82 is rotatable integrally with the inner cylinder, An opening at the lower end is formed in the cooling liquid inlet 83.
The power acquisition mechanism 30 is provided on the inner cylinder rotation shaft 13 (13a) on one end side of the inner cylinder 10 and a timing belt transmission mechanism 400 that takes out the rotation of the inner cylinder rotation shaft 13 (13a); It is comprised from the timing belt transmission mechanism 401 which takes out rotation of the outer cylinder rotating shaft 23 (23b) of the other end side.

Further, at one end of the inner cylinder 10, a moving blade 40 that receives gas flowing from the supply port 11 and applies a rotational force to the inner cylinder 10 is provided. The rotor blades 40 are arranged on one end side of the inner cylinder 10 at an equiangular relationship around the rotation axis of the inner cylinder 10 and have a surface for receiving the gas guided by the guide blades 70 provided on the outer cylinder 20. A plurality of blades 41 for guiding the gas from the upper side into the inner cylinder 10 are provided.
On the other hand, the guide blade 70 provided in the outer cylinder 20 includes a wind guide plate 71 arranged in an equiangular relationship corresponding to the blade 41 of the rotor blade 40, and passes through the outer side of the inner cylinder 10 to the supply port 11. The gas from the other flow path Rb is reversed and fed to the blade 41 from the upper side of the blade 41 of the rotor blade 40. For this reason, since the gas is caused to flow in the vertical direction, the gas is surely received by the blade 41 and the rotation efficiency is improved.

  Furthermore, a guide vane 50 is provided outside the other end of the inner cylinder 10. The guide vane 50 receives the gas discharged from the discharge port 12, applies a rotational force to the inner cylinder 10, and guides the gas discharged from the discharge port 12 in the gas flow direction of the other flow path Rb. The guide blade 50 includes a bowl-shaped guide plate body 51 that reverses the gas from the discharge port 12 in the gas flow direction of the other flow path Rb, and a plurality of blade members 52 provided on the guide plate body 51. Yes. The guide plate body 51 is fixed to the outer cylinder 20. Thereby, the guide vane 50 and the outer cylinder 20 rotate in the same direction. Other actions and effects are the same as described above.

<Application example>
FIG. 35 shows an application example of a system for operating the convection temperature difference prime mover according to the first embodiment of the present invention.
In this system, the convection temperature difference prime mover S1 has a cooling liquid circulation pipe upstream of the cooling section and a part of the heating liquid circulation pipe upstream of the heating section. However, it is divided into a cooling liquid circulation pipe and a warming liquid circulation pipe.
Specifically, the convection temperature differential prime mover S1 has a recovery pipe body provided with a recovery port 156 on the upstream side for recovering the cooling liquid and the heated liquid on the cooling liquid circulation line 80 and the heated liquid circulation line 90. 155. On the downstream side of the recovery pipe body 155, it branches off into a cooling liquid circulation pipe body 80a and a warming liquid circulation pipe body 90a. Further, a check valve 157 is provided on the upstream side of the branch point where the cooling liquid circulation pipe body 80a and the heated liquid circulation pipe body 90a branch.

  In addition, in this system, a bypass pipe 160 that bypasses the recovery pipe 155 is provided. A pump 160 a is provided in the middle of the bypass pipe 160, and the pump 160 a sucks the liquid flowing through the recovery pipe 155 and causes the liquid to flow into the recovery pipe 155 downstream of the check valve 157. . Further, a supply pipe 161 for replenishing the recovery pipe body bypass pipe 160 with the liquid stored in the tank 136 is provided. The supply pipe 161 is opened and closed based on the liquid amount measured by the liquid amount measuring device 139 provided in the tank 136.

The supply pipe 161 includes an electromagnetic valve 163 that opens and closes the supply pipe 161 and a check valve 164 for preventing liquid from flowing backward from the bypass pipe 160. The electromagnetic valve 163 opens and closes together with the electromagnetic valve 162 provided on the upstream side of the junction of the supply pipe 161 and the bypass pipe 160 by the liquid amount measuring device 139 that measures the amount of liquid in the tank 136.
The operations of the electromagnetic valve 162 and the electromagnetic valve 163 are as follows. When the liquid amount measuring device 139 detects that the amount of liquid in the tank 136 is less than a predetermined amount, the switch 143 connects the power source 150 to the electromagnetic valve 163 and closes the electromagnetic valve 163. On the other hand, the solenoid valve 162 is disconnected from the power source 150 and opened. In this case, the liquid from the recovery pipe 155 is sucked by the pump 160 a and returned to the recovery pipe 155. When the liquid amount measuring device 139 detects that the amount of liquid in the tank 136 is larger than a predetermined amount, the switch 143 connects the power source 150 to the electromagnetic valve 162 and closes the electromagnetic valve 162. On the other hand, the electromagnetic valve 163 is disconnected from the power supply 150 and opened. In this case, the liquid in the tank 136 is sucked by the pump 160a.

According to this system and the convection temperature difference prime mover S 1, the cooling liquid and the heating liquid are collected together at the collection port 156, and the cooling liquid and the heating leaked from between the outer cylinder 20 and the sliding contact member 89. Since the liquid can be returned to the cooling liquid circulation line 80 and the warming liquid circulation line 90 via the bypass pipe 160 at an appropriate time, the cooling liquid and the warming liquid are exchanged with the cooling liquid circulation line 80 and the warming liquid. A predetermined amount can flow through the circulation line 90.
Further, since the cooling liquid and the heating liquid are not separately collected, the structure is simplified, and the installation cost of the convection temperature difference prime mover S1 is reduced.
Other actions and effects are the same as those described above.

  In addition, in each convection temperature difference prime mover S1, S2, S3, S4, S5 which concerns on each embodiment of this invention, although the shape of the inner cylinder 10 and the outer cylinder 20 was made into cylindrical shape, it is limited to this Instead, as shown in (a), (b), (c), (d), (e), (f), (g), (h) in FIG. The design can be changed as appropriate.

Claims (11)

An outer shell, an inner cylinder rotatably supported by the outer shell, a gas supply port formed at one end in the axial direction, and a gas discharge port formed at the other end, and rotatable relative to the outer shell and the inner tube An outer cylinder whose wall is located between the outer shell and the inner cylinder, and a gas flow from the supply port of the inner cylinder to the discharge port through the inside of the inner cylinder and the flow path A temperature difference is imparted to the gas so as to pass through the other flow path from the discharge port of the inner tube to the supply port through the outside of the inner tube, and convection of the gas is generated. And in the convection temperature difference prime mover for obtaining power by rotating the outer cylinder,
The inner cylinder is provided with a moving blade that receives the gas flowing from the supply port and applies a rotational force to the inner cylinder,
A cooling liquid is sprayed in the inner cylinder, a gas passing through the one flow path is cooled, and a cooling liquid circulation pipe for circulating the cooling liquid is provided. In the middle of the cooling liquid circulation pipe, A cooling unit for cooling the cooling liquid is provided,
A heating liquid is sprayed between the inner cylinder and the outer cylinder, the gas passing through the other channel is heated, and a heating liquid circulation conduit for circulating the heating liquid is provided. A convection temperature difference prime mover characterized in that a warming section for warming the warming liquid is provided in the middle of the warm liquid circulation conduit. The cooling liquid circulation conduit has a cooling liquid inlet provided in the outer shell on one end side, and a plurality of outlets for spraying the cooling liquid on the inner cylinder on the other end side, Further, the one support shaft that enables rotation of the other ends of the inner cylinder and the outer cylinder, an injection port connected to the inlet of the one support shaft, and a discharge port of the inner cylinder after cooling the gas in the one flow path A recovery port for recovering the cooling fluid that has flowed out of the cooling fluid, and a cooling liquid circulation tube that circulates the cooling liquid from the recovery port to the inlet again.
The warming liquid circulation conduit is provided on one end side with an inlet for the warming liquid provided on the outer shell, has an outlet on the other end side, and further has one end of the inner cylinder and the outer cylinder. The other support shaft that supports the shaft, covers the outside of the inner cylinder, forms a flow passage through which the heated liquid from the outlet of the other support shaft can flow, and the outer cylinder. A cylinder having a plurality of injection ports for injecting the heated liquid toward the injection port, an injection port connected to the inlet of the other support shaft, and a recovery for recovering the heated liquid injected from the injection port of the cylinder The convection temperature difference prime mover according to claim 1, further comprising a heated liquid circulation tube that circulates the heated liquid from the opening and the recovery port to the injection port again.   The inner cylinder is provided with a tubular inner cylinder rotating shaft that is rotatably inserted into the one supporting shaft or the other supporting shaft, and the outer cylinder is provided with a tubular outer cylinder rotating shaft that is coaxial with the inner cylinder rotating shaft. The convection temperature difference prime mover according to claim 2, further comprising a power acquisition mechanism for obtaining power from both the inner cylinder rotation shaft and the outer cylinder rotation shaft.   The power acquisition mechanism meshes with a first driving gear provided on the inner cylinder rotating shaft, a second driving gear provided on the outer cylinder rotating shaft, a first driven gear meshing with the first driving gear, and a second driving gear. The convection temperature difference driving device according to claim 3, further comprising: a second driven gear, a shaft to which the first driven gear and the second driven gear are attached, and a generator driven in association with the shaft. apparatus. Provided on the inner periphery of one end side of the outer cylinder is a guide blade that guides gas to the moving blade provided at the supply port,
A plurality of blades each having a surface for receiving the gas guided by the guide blades, wherein the rotor blades are arranged on one end side of the inner tube at an equiangular relationship around the rotation axis of the inner tube. Prepared,
5. The convection temperature difference driving device according to claim 1, wherein the guide blade includes a plurality of air guide plates arranged in an equiangular relationship so as to correspond to the blades of the moving blade. apparatus.   6. The air guide plate is formed by being bent in one circumferential direction, and centrifugal force is applied to the gas flowing into the supply port by the concave surface of the wind guide plate. Convection temperature difference prime mover.   On the outside of the other end of the inner cylinder, the gas discharged from the discharge port is received and a rotational force is applied to the inner tube, and the gas discharged from the discharge port is made to flow in the other channel. The convection temperature difference prime mover according to claim 5 or 6, characterized in that a guide vane is provided to guide the convection.   The convection temperature according to claim 1, 2, 3, 4, 5, 6 or 7, wherein a porous member capable of passing the gas passing through the one passage and the cooling liquid is provided inside the inner cylinder. Differential prime mover.   9. The convection temperature difference prime mover according to claim 8, wherein the porous member is a wound sheet-like metal net.   7. A fin for pushing the accumulated gas to the discharge port side is provided on the supply port side of the one flow path on the inner periphery of the inner cylinder. , 7, 8 or 9 convection temperature difference prime mover.   The one support shaft is rotatable in conjunction with the inner cylinder, and the one support shaft is provided with a fin for pushing the gas retained on the supply port side of the one flow path to the discharge port side. The convection temperature difference prime mover according to claim 1, 2, 3, 4, 5, 6, 7, 8, or 9.

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