JPH0874729A - Method for converting gravity acting on flow of fluid into kinetic energy and device thereof - Google Patents

Abstract

PURPOSE: To convert gravity acting on the flow of fluid into kinetic energy by letting the inside of a pipe in which fluid flows, be so constituted that the energy of fluid flow can be retroactive. CONSTITUTION: An inflow section 9 provided with a water passage the cross sectional area of flow of which is contracted inwardly from an inflow port 2. A front section flow rate maintaining pressure water feeding means 4 supplies both the inflow/outflow loss compensation pressure and the dynamic pressure of a water source V2 for water flow in the vicinity of a draining port 3, to flowing water within the inside of a penstock 1, wherein the inflow/ outflow loss compensation pressure compensates both the whole of an inflow loss in pressure taking place in the specified flow rate of flowing water in a turbine driving energy system between the inflow port 2 and the outlet of an axial flow turbine 6, and the whole of an outflow loss in pressure taking place in the specified flow rate of flowing water in a flow rate maintaining energy system between the outlet of the axial flow turbine 6 and the draining port 3, to zero. A rear section flow rate maintaining pressure water feeding means 8 which is interposed between the axial flow turbine 6 and the draining port 3, supplies rear section flow rate maintaining supplemental kinetic energy to water flow within the inside of the penstock 1. An outflow section 10 is also provided, which is connected to the rear section flow rate maintaining pressure water feeding means 8, and gradually increases the cross sectional area of flow.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a method and apparatus for converting gravity acting on a fluid flow into kinetic energy,
In particular, the present invention relates to a third type permanent motion engine that converts gravity acting on a fluid flow into kinetic energy.

[0002]

2. Description of the Related Art In conventional fluid dynamics, a method and apparatus for converting gravity acting on a fluid flow into kinetic energy has not yet been realized. In particular, gravity acting on a fluid flow is converted into kinetic energy. It is said that a third-class permanent motion engine that does this is not feasible.

[0003]

In conventional fluid dynamics,
Bernoulli's equation is the only equation that expresses the energy of fluid flow due to the action of gravity. However, Bernoulli's equation is made as a law of conservation of energy so that it is convenient for explaining that energy is conserved. Contains. So Bernoulli's formula is
There is a problem that the essence of the energy of the fluid flow due to the action of gravity is not correctly represented.

Further, in connection with the above-mentioned problem of uncertain essence of energy, in conventional fluid dynamics, there is a problem that the energy of the fluid flow cannot be traced back inside the pipe in which the fluid is flowing. Yes, along with this, installing a water pressure pipe with a water wheel inside, in the water flow, or installing a wind pressure pipe with a wind turbine inside, in the water pressure pipe or the wind pressure pipe, By supplying artificial energy for compensating the resistance loss to the flow rate to 0, the energy of the flowing water or the energy of the circulating air is traced back to secure the flow rate, and the gravity acts on the flow of the fluid to drive the water turbine or the wind turbine. There is a problem in that it is not possible to theoretically explain whether or not a method and an apparatus for converting kinetic energy into kinetic energy, that is, the realization of the realization of a type 3 permanent motion engine that converts gravity acting on a fluid flow into kinetic energy.

The present invention solves the above-mentioned problems of conventional fluid dynamics, clarifies the essence of the energy of the fluid flow due to the action of gravity, and based on this essence, the A method and apparatus for converting gravity acting on a fluid flow into kinetic energy by making the flow energy trace back, and in particular, a third method for converting gravity acting on a fluid flow into kinetic energy. The task is to realize a seed-permanent movement engine.

[0006]

In order to solve the above-mentioned problems, a method of converting gravity acting on a fluid flow into kinetic energy according to the first invention of the present application, the action of gravity on the atmosphere and the water flow, and the water depth. Water velocity V _H (m / sec) at _H (m)
A pressure bias due to the action of gravity in the flow direction on the atmosphere and the water flow, which acts on each part of the water flow and balances the resistance to each part of the water flow and maintains the water velocity V _H at the water depth H; The total intrinsic pressure P _FH of the water flow at the water depth H based on the action of gravity on the relative static pressure P _SH = specific static pressure P _SH + specific dynamic pressure P _KH = [ρ × g × (H + 10.33 m _Aq ) − {ρ
× (V _H ) ² ÷ 2}] + {ρ × (V _H ) ² ÷ 2} = ρ ×
g × (H + 10.33m _Aq (t / m ² ), and the specific energy E _FH of the water flow at the water depth H per unit time unit flow rate 1 (m ³ / sec) based on the action of gravity on the atmosphere and the water flow = (the unique static _P specific pressure energy _E PH corresponding to the _SH) + (the inherent dynamic pressure _P inherent kinetic energy corresponding to ^{_{KH E KH) = 1 (m}} 3 / sec) ×
[Ρ × g × (H + 10.33m _Aq ) − {ρ × (V _H ).
² ÷ 2}] (t / m ² ) +1 (m ³ / sec) × {ρ ×
(V _H ) ² ÷ 2} (t / m ² ) = 1 × ρ × g × (H + 1
0.33 m _Aq ) (t · m / sec), in a water stream that circulates on a global scale such as an ocean current or a tidal current, in a water stream that flows by a gradient such as a river or an open channel, or
In a moving body on or under water, the force for maintaining the relative motion with water and the relative velocity with water can be treated as the pressure bias due to the action of gravity in the flow direction of the atmosphere and the water flow and the water velocity V _H. , An inlet of the water cross-section S ₁ (m ² ) is arranged at an arbitrary water depth H ₁ (m) at a water velocity V ₁ (m / sec), and an axial flow turbine provided near the central portion is used for the water depth. The water discharge cross-sectional area S ₂ (m ² ) is placed at the water velocity V ₂ (m
/ Sec) said water depth H or deeper water depth H
₂ (m), and the difference in water pressure between the axial flow turbine and the inlet and the difference in water pressure between the axial flow turbine and the drain are respectively in the hydraulic pipe between the axial flow turbine and the inlet. Of gravity acting on the flowing water of the shaft and gravity acting on the flowing water in the penstock between the axial flow turbine and the drainage port, and the effective water depth of the inlet and the drainage port with respect to the axial flow turbine is the shaft. A penstock having the same water depth H as that of the water turbine is installed in the water flow or in the moving body, and the water passage cross-sections S ₁ and S ₂ are calculated by (S ₁ × predetermined) based on the equation of the water turbine output capacity described later. Inflow velocity V
₁₀ ) = (S ₂ × predetermined outflow velocity V ₂₀ of water velocity V ₂ or less)
(M ³ / sec) = (predetermined flow rate at which required output is obtained), and the cross sectional area of the water flowing from the inlet to the axial flow turbine is increased by the flow of water and the flow velocity V of the turbine is introduced. _G1O (m / sec) is reduced to the turbine inflow cross-sectional area S _G1O (m ² ) so as to flow into the axial flow turbine,
The flow rate of the flowing water flowing out from the axial flow _turbine V _G2I (m) while deflecting the cross sectional area of the water flow from the drain port to the axial flow _{turbine in} the circumferential direction toward the axial flow _{turbine.
Cross} section S _G2I (m
² ) = By gradually reducing to the water turbine inflow cross-sectional area S _G1O and connecting to the axial outlet of the axial flow turbine having a larger water cross-sectional area in a state of being circumferentially deflected,
A state in which the axial flow turbine is unloaded and the inflow / outflow loss compensation pressure artificially supplied as described below and the dynamic pressure of the water velocity V ₂ are balanced with the resistance to running water to maintain a predetermined flow rate described below. Alternatively, the axial flow turbine is loaded, and the inflow / outflow loss compensation pressure artificially supplied as described later and the water velocity V ₂ are balanced with the resistance to the running water to maintain a predetermined flow rate described later, and In the state where the supplemental kinetic energy E _C2K for maintaining the rear flow rate artificially supplied as described later supplements the consumption of the hydraulic turbine drive energy E _T described later, the running water speeds up as the water flow cross-sectional area decreases. Then into the axial water turbine, the running water that has passed through the axial water turbine flows out from the drain port while decelerating with an increase in the water flow cross-sectional area,
With these acceleration and deceleration, the specific static pressure P of each part of the hydraulic pipe based on the action of gravity on the atmosphere and the water flow.
_{The SH} symmetrically reduces the pressure from both the inlet and the drain toward the axial flow turbine, so that the action of gravity on the atmosphere and the water flow outside the inlet causes the flowing water in the penstock to move as described above. The specific energy E _FH at the water depth H per unit time unit flow rate 1 = 1 × ρ × g × (H +
10.33 m _Aq ), the intrinsic total pressure P _FH = ρ
Xg × (H + 10.33m _Aq ), which acts from the inlet to the outlet of the axial flow turbine, and the action of gravity on the atmosphere and the water flow outside the drainage port is the unit time unit of the flowing water in the penstock. The specific energy E _FH = 1 × ρ × g × (H + 10.3) at the water depth H per passing flow rate 1.
3 m _Aq ) of the drainage port static pressure P _S2 constituting (the above-mentioned specific static pressure P _SH ) / (the above-mentioned specific total pressure P _FH ) = the above-mentioned specific total pressure P _{FH at the} drain-the above-mentioned specific dynamic pressure at the drain port P _KH = the specific total pressure _{P FH} at water outlet - water speed _{V 2} dynamic pressure = [{ρ ×
g × (H + 10.33m _Aq )}-{ρ × (V ₂ ) ² ÷
As 2}], leave as dating back from the water outlet to the outlet of the shaft running water vehicle, flows occurring in flowing water of the predetermined flow rate of the water turbine drive energy E _T system between the inlet and the axis running water car outlet Total loss pressure (t / m ² ) and outflow loss pressure (t / m ² ) generated in flowing water of the predetermined flow rate in the flow maintenance energy E _F system between the outlet of the axial flow turbine and the drainage port.
Inflow / outflow loss compensation pressure (t /
m ²⁾ inflow and outflow loss compensation pressure energy to generate a (t · m / sec) = (S 1 × V 10) × ( inflow and outflow loss compensation pressure), and, (wherein the predetermined flow rate) × (the water speed The dynamic pressure of V ₂ ) due to the bias of pressure in the natural water flow due to the action of gravity on the atmosphere and the water flow in the flow direction, and the inherent total pressure P _FH and the static pressure P _{S2 of the} water outlet.
As corresponding to the difference between the artificially supplied to running water of the water turbine drive energy E _T system water pressure tube, said predetermined flow rate the flow rate maintained energy causes balance the resistance of the pressure tube for flowing water E _F The outflow loss pressure generated in the flowing water of the system is compensated from the upstream side, and the difference between the intrinsic total pressure P _FH and the distribution port static pressure P _S2 is compensated from the upstream side to maintain the flow rate as described later. flow rate maintained energy E _F for generating in the form of change places with consumption of water turbine driving energy E _T below the running water of the energy E _F system, the flow rate maintained energy E _F system running water in the later of the water turbine driving energy E of
_The specific flow rate V (m / sec) based on gravity acting on the atmosphere and the water flow is maintained at the predetermined flow rate by tracing back to the axial flow turbine in a form of replacing the consumption of _T
(Predetermined flow rate S ₁ × V ₁₀ ) / (water cross-sectional area of each part)
Fixed at the water depth H, the flowing water per unit time unit passing flow rate 1 of each part in the penstock located at the water depth H is the same as the natural water flow at the water depth H based on the action of gravity on the atmosphere and the water flow. The specific energy E _FH (t · m / s
ec) = (the unique static _P specific pressure energy corresponding to the _{SH E} PH) + (specific kinetic energy _E KH corresponding to the unique dynamic pressure _{P KH) = 1 × [ρ} × g × (H + 10.33
m _Aq ) − {ρ × (V _H ) ² ÷ 2}] + 1 × {ρ × (V
_H ) ² ÷ 2} = 1 × ρ × g × (H + 10.33m _Aq )
And that to have the shaft regardless of whether the load of the flowing water wheel, the flowing water of the flow rate maintained energy E _F system,
Outflow energy E ₂ (t · m / sec) = (S ₂ ×
V ₂₀ ) × [the specific energy E _FH of the water flow per unit time unit passing flow rate at the water depth H {1 × ρ × g ×
(H + 10.33m _Aq )}] is present, the effect of gravity on the atmosphere and water flow at the drain,
Pressure deviation due to the action of gravity in the flow direction on the atmosphere and water flow outside the drainage port, and the specific energy E _FH of the water flow per unit time unit passing flow rate at the water depth H =
1 × ρ × g × (H + 10.33 m _Aq ) and the drain port static pressure P _S2 are the drain port static pressure P from the drain port with the flow rate maintenance energy E _F system running water as the upper limit of the predetermined flow rate. When the axial flow turbine has no load, it has an inflow energy E ₁ (t) because it has a flow rate maintaining action of sucking it into the water flow of _S2 and leaving it without leaving any change in the water flow.
M / sec) = (the predetermined flow rate S ₁ × V ₁₀ ) × [the specific energy E _FH of the water flow per unit time unit flow rate 1 at the water depth H {1 × ρ × g × (H + 10.33
m _Aq )}] = The outflow energy E ₂ is passed through the penstock with the flowing water of the predetermined flow rate flowing in from the inflow port and flowing out from the drain port, and the loaded axial flow turbine is a water turbine. driving energy _E T = {running water kinetic energy of the water wheel drive energy _{E T} system at a predetermined flow rate of the water turbine inlet flow velocity _{V G1O}} - {waterwheel outlet flow velocity _V tO in the axial direction of the outlet of the shaft running water wheel (m / sec ) when consuming a predetermined flow water turbine driving energy E _T system running water kinetic energy of} the is in any position between the axis running water wheel outlet and the water outlet, wherein in the water depth H mentioned above Inherent energy E _FH
= 1 × ρ × g × (H + 10.33m _Aq ) and the intrinsic total pressure P _FH = ρ × g × (H + 10.33m _Aq ), the drain port static pressure P _S2 traced back as described above and the above. As described above, the water passage cross-sectional area on which the dynamic pressure of the water speed V ₂ supplied from the upstream side acts is the water turbine outflow water passage cross-sectional area S.
_Since it is n times as large as _G2I, the specific energy E _FH of the flowing water at the water depth H per required unit time unit passing flow rate 1 is the rear flow rate maintaining flow rate V of 1 / n of the flow rate maintaining flow rate V _{G2I. In the} rear reduced water flow cross-sectional area S _C2O obtained by _C2O , the supplemental kinetic energy for rear flow rate maintenance E _C2O ≧ [rear flow rate maintenance flow velocity V _C2O = {(S ₂ × V
₂₀ ) / S _C2O } kinetic energy of flowing water at a predetermined flow rate]
× [1-[{(the inflow energy E _{1 −the} water turbine drive energy E _T ) gives the flow velocity V _C2O0 } ² / {the inflow energy E ₁ to the running water passing through the rear reduced water passage sectional area S _C2O] The rear flow rate maintaining flow velocity V _C2O } ² ] given to the flowing water passing through the rear reduced water flow cross-sectional area S _C2O ]]
_Is the kinetic energy of the turbine outflow velocity V _TO and the outflow loss compensation pressure (predetermined flow rate) × (dynamic pressure of the water velocity V ₂ ).
Are supplied from the upstream side and are artificially supplied to the flowing water of the flow rate maintaining energy E _F system of the predetermined flow rate that receives the static pressure P _S2 of the water outlet and the flow rate maintaining action by the water flow outside the drain port, by maintaining the flow velocity in the rear reduced water passage cross-sectional area S _C2O to said rear flow maintaining the flow velocity V _C2O, the flow rate maintained energy E _{F =} the water turbine driving energy E _T in a form change places with consumption of the water turbine drive energy E _T The specific energy E _FH at the water depth H per unit time unit flow rate 1 is added to the flowing water of the flow rate maintaining energy E _F system in the penstock at the water depth H, which is generated and traces back to the axial flow _turbine. = 1 × ρ × g × (H + 10.33m
_The outflow energy E ₂ = (S ₂ ×) based on _Aq )
V ₂₀ ) × [the specific energy E at the water depth H
_FH {1 × ρ × g × (H + 10.33 m _Aq )}] is maintained, and the inside of the axial water turbine is rotated while the runner is rotated in the circumferential direction to the predetermined amount of flowing water over the entire length of the penstock. Including the existing water turbine drive energy E _T , the inflow energy E ₁ = outflow energy E ₂ and the intrinsic total pressure P _FH = ρ × at the water depth H based on the action of gravity on the atmosphere and the water flow. g x (H + 10.33
m _Aq ), and the distribution of artificial total pressure P = {(the inflow / outflow loss compensation pressure) − (loss pressure)} due to the artificial energy that balances the resistance and maintains the flow velocity is set to the intrinsic total pressure P _FH . The total pressure P _F of the added flowing water = (specific total pressure P _FH + total artificial pressure P) decreases to the drain port static pressure P _S2 while maintaining the predetermined flow rate from the inlet to the flowing water outlet, The flow rate maintaining action of the water flow outside the drainage port,
The predetermined flow rate flowing water of the flow maintaining energy E _F system, the from the drain outlet predetermined outflow velocity V ₂₀ at the water outlet static pressure P _S2 having the outflow energy E ₂ in the pressure pipe
By sucking into the water flow of No. 1 and causing it to flow away without leaving any change in the water flow and stabilizing the flow rate of the flowing water in the penstock at the predetermined flow rate, the three small artificial energy supplied as described above are received. the third kind of the gravity acting on the fluid flow and converts the large the water wheel drive energy E _T to said flow rate maintained energy E _F drives the shaft running water vehicle maintain said predetermined flow rate of water flow of the water pressure pipe Realizing a permanent motion engine, turbine output capacity (kW) = {predetermined flow rate (S ₁ × V ₁₀ )}
X {g x (H + 10.33 m _Aq )} x turbine efficiency-
{(Inflow / outflow loss compensation pressure energy) + {Predetermined flow rate (S ₁ × V ₁₀ )} × ( _Dynamic pressure of water velocity V ₂ ) + (Replacement kinetic energy for rear flow rate maintenance E _C2K )} ÷ (of artificial energy Power efficiency).

The method of converting gravity acting on a fluid flow into kinetic energy according to the second aspect of the present invention converts the gravity acting on the fluid flow into kinetic energy according to the first aspect of the present invention in order to solve the above problems. In the method, a circulation channel having a gradient channel and a circulation / condensation channel for circulating / condensing a water flow at a low water level end of the gradient channel to a high water level end of the gradient channel by pumping of a pumping means is provided. A penstock is installed in the waterway, and a change in the water speed of the gradient waterway due to the installation of the penstock is canceled by adjusting the gradient distribution of the gradient waterway, and the circulation / condensation amount by pumping of the water pumping means is adjusted. So that the water velocity becomes substantially constant over the entire length of the gradient channel, the gravity channel action on the gradient channel and the water velocity V _H (m / sec) at the water depth H (m).
A pressure bias due to the action of gravity in the flow direction on the atmosphere and the water flow, which acts on each part of the water flow and balances the resistance to each part of the water flow and maintains the water velocity V _H at the water depth H; The total intrinsic pressure P _FH of the water flow at the water depth H based on the action of gravity on the relative static pressure P _SH = specific static pressure P _SH + specific dynamic pressure P _KH = [ρ × g × (H + 10.33 m _Aq ) − {ρ
× (V _H ) ² ÷ 2}] + {ρ × (V _H ) ² ÷ 2} = ρ ×
g × (H + 10.33m _Aq ) (t / m ² ) and the specific energy E of the water flow at the water depth H per unit time unit passing flow rate 1 (m ³ / sec) based on the action of gravity on the atmosphere and the water flow _FH = (the unique static _P specific pressure energy _E PH corresponding to the _SH) + (the inherent dynamic pressure _P inherent kinetic energy corresponding to ^{_{KH E KH) = 1 (m}} 3 / sec) ×
[Ρ × g × (H + 10.33m _Aq ) − {ρ × (V _H ).
² ÷ 2}] (t / m ² ) +1 (m ³ / sec) × {ρ ×
(V _H ) ² ÷ 2} (t / m ² ) = 1 × ρ × g × (H + 1
0.33 m _Aq ) (t · m / sec).

In order to solve the above problems, the method for converting gravity acting on a fluid flow into kinetic energy according to the third aspect of the present invention converts gravity acting on a fluid flow into kinetic energy according to the first aspect of the present invention. In the method described above, the penstock is installed across the water level difference between the upstream side and the downstream side of the muzzle orifice provided in the water stream, or across two water streams having a water level difference between the water surfaces. The water level difference is used as all or part of the turbine driving energy E _T or / and the inflow / outflow loss compensation pressure to adjust the turbine inflow cross section S _G1O and the turbine outflow cross section S _G2I. (The hydrostatic water inlet static pressure P of the flowing water passing through the water turbine inflow cross-sectional area S _G1O
STI - characterized by the (the running water waterwheel flow outlet static pressure _{P STO} passing waterwheel outlet water flow cross-sectional area _{S G2i)} = the inflow and outflow loss compensation pressure + water speed _{V 2} dynamic pressure.

In order to solve the above-mentioned problems, the method of converting gravity acting on a fluid flow into kinetic energy according to the fourth aspect of the present invention has the effect of gravity on the atmosphere and the wind speed V _H (m / m).
sec) and the resistance to the movement of each part of the atmosphere and the resistance to the movement of each part of the atmosphere are balanced, and the bias of the pressure in the direction of the wind accompanied by the effect of gravity on the atmosphere maintaining the wind velocity V _H and the effect of gravity on the atmosphere Inherent total pressure P _FH of wind at the wind speed V _H = Inherent static pressure P _SH + Inherent dynamic pressure P _KH = [ρ × g ×
_{10.33m Aq - {ρ A × (} V H) 2 ÷ 2}] + {ρ
_A × (V _H ) ² ÷ 2} = ρ × g × 10.33 m _Aq (t
/ M ² ) and the wind speed V _H per unit time unit flow rate 1 (m ³ / sec) based on the action of gravity on the atmosphere
Specific energy of the wind E _FH = (specific pressure energy E _PH corresponding to the specific static pressure P _SH ) + (the specific dynamic pressure P _SH
Specific kinetic energy corresponding to ^{_{KH E KH) = 1 (m}} 3 /
sec) × [ρ × g × 10.33m Aq - {ρ A × (V
_H ) ² ÷ 2}] (t / m ² ) +1 (m ³ / sec) ×
{Ρ _A × (V _H ) ² ÷ 2} (t / m ² ) = 1 × ρ × g ×
In the wind having 10.33 m _Aq (t · m / sec), or the force for maintaining the relative motion with the atmosphere and the relative velocity with the atmosphere in the direction of the wind accompanied by the action of gravity on the atmosphere. in the mobile in the atmosphere can handle a bias pressure as the wind speed V _H of has an inlet ventilation cross-sectional area S _{1 (m} ²⁾ in the position of the wind speed V _{1 (m} / sec), the central axial flow wind turbine And an exhaust port having a ventilation cross-sectional area S ₂ (m ² ) near the wind speed V
_The ventilation cross section S ₁ , S _{2 in} which a wind pressure pipe having a position of ₂ (m / sec) is installed and the change of ρ _A due to the flow velocity is corrected.
The windmill The predetermined outflow velocity V ₂₀ ) (m ³ / sec) = (predetermined flow rate at which required output is obtained) is set, and the ventilation cross-sectional area from the inflow port to the axial wind turbine is increased by the circulating air. Then, the wind turbine inflow ventilation cross-sectional area S is set so as to flow into the axial wind turbine at the wind turbine inflow velocity V _G1O (m / sec).
_Circulating air flowing out from the axial wind turbine while being reduced to _G1O (m ₂ ) and deflecting a ventilation cross-sectional area from the exhaust port to the axial wind turbine in the circumferential direction toward the axial wind turbine. Is a flow rate maintenance flow velocity V _G2I (m / sec), the wind turbine outflow ventilation cross-sectional area S _G2I (m ² ) = the wind turbine inflow ventilation cross-sectional area S _G1O is gradually reduced to a larger axial cross-sectional area. By connecting to the outlet in the axial direction of the wind turbine in a state of being deflected in the circumferential direction, the axial flow wind turbine has no load and the inflow / outflow loss compensation pressure and the wind speed V ₂ which are artificially supplied as described below. Dynamic pressure is balanced with the resistance to the circulating air to maintain a predetermined flow rate described below, or the axial flow turbine is loaded and the inflow / outflow loss compensation pressure and the wind speed artificially supplied as described below. V _2
Of the wind turbine drive energy E _T , which is a supplemental kinetic energy E _C2K for maintaining the rear flow rate, which is artificially supplied as described later, in order to maintain the predetermined flow rate described later in balance with the resistance to the circulating air. In the state of replenishing, the circulating air speeds up with a decrease in the ventilation cross-sectional area and flows into the axial wind turbine, and the circulating air passing through the axial wind turbine decelerates with an increase in the ventilation cross-sectional area. While flowing out from the exhaust port, the specific static pressure P _{SH of} each part of the wind pressure pipe based on the action of gravity on the atmosphere is increased from both the inflow port and the exhaust port with the acceleration and deceleration. By symmetrically reducing the pressure toward the axial-flow wind turbine, the action of gravity on the atmosphere outside the inflow port causes the specific energy E _FH = 1 per unit time unit passing flow rate of the circulating air in the wind pressure tube. × ρ × As the unique total pressure _{P FH = ρ × g × 10.33m} Aq constituting a × 10.33m _Aq, acting from the inlet to the outlet of the axial flow wind turbine, the effect of gravity on the atmosphere of the drainage extraoral is (The specific static pressure P _SH ) / (the specific total pressure P _FH ) of the specific energy E _FH = 1 × ρ × g × 10.33 m _Aq per unit time unit passing flow rate of the circulating air in the wind pressure pipe. ) Constituting the exhaust port static pressure P _S2 = the intrinsic total pressure P _FH − at the exhaust port
The intrinsic dynamic pressure P _{KH at the} exhaust port = the intrinsic total pressure P _FH at the exhaust port−the dynamic pressure of the wind speed V ₂ = [{ρ × g × 10.33 m
_Aq }-{ρ _A × (V ₂ ) ² ÷ 2}], so that the wind turbine drive energy between the inlet and the outlet of the axial wind turbine is set so as to be traced from the exhaust port to the outlet of the axial wind turbine. E
And all of the inflow loss pressure (t / m ²⁾ generated in _T system the predetermined flow rate distribution of air of the predetermined flow rate distribution of air flow rate maintained energy E _F system between the outlet and the exhaust port of the axial flow wind turbine outflow loss pressure (t / m ²⁾ of all the inflow and outflow loss compensation pressure compensation 0 (t / m ²⁾ inflow and outflow loss compensation pressure energy that generates occur (t · m / se
c) = (S ₁ × V ₁₀ ) × (inflow / outflow loss compensation pressure), and (predetermined flow rate) × (dynamic pressure of the windmill V ₂ ), and the action of gravity on the atmosphere in the wind of nature. the associated pressure deviation in the direction of the wind, and the specific total pressure P _FH and as corresponding to the difference between the exhaust port static pressure P _S2, distribution air in the wind turbine drive energy E _T system of the wind pressure pipe artificially supplied to the predetermined flow rate the flow rate maintained to compensate the outflow losses pressure generated in the distribution air energy E _F system from the upstream side and the specific total pressure with balancing the resistance of the wind pressure pipe for circulation of air By compensating for the difference between P _FH and the exhaust port static pressure P _S2 from the upstream side,
Flow rate maintained energy E _F to be generated by the consumed change places the form of the flow rate maintained energy E _F based wind turbine drive energy E _T below the distribution of air as described later, the flow rate maintained energy E _F system flow within the air Wind turbine drive energy E described later
_The predetermined flow rate is maintained by going back to the axial-flow wind turbine in a manner that replaces the consumption of _T , and the flow velocity of each part of the wind pressure tube is set to a specific water speed V (m / sec) = (the predetermined flow rate S ₁ × V ₁₀ ) / (aeration cross-sectional area of each part corrected for changes in _ρA due to flow velocity), and the circulating air per unit time unit passing flow rate 1 of each part in the wind pressure tube is the same as the natural wind. Specific energy E _FH (tm · sec) = (specific pressure energy E _PH corresponding to the specific static pressure P _SH ) +
(The intrinsic volatility energy E corresponding to the intrinsic dynamic pressure P _KH
KH ) = 1 × [ρ × g × 10.33 m _Aq − {ρ _A ×
(V _H ) ² ÷ 2}] + 1 × {ρ _A × (V _H ) ² ÷ 2} =
1 × ρ × g × 10.33 m _Aq , and regardless of whether or not there is a load on the axial-flow wind turbine, the outflow energy E is added to the circulating air of the flow-rate maintaining energy E _F system.
₂ (t · m / sec) = (S ₂ × V ₂₀ ) × [the specific energy E _FH of the wind per unit time unit flow rate at atmospheric pressure E _FH {1 × ρ × g × 10.33 m _Aq }] If there exists, the action of gravity on the atmosphere at the exhaust port, the bias of the pressure in the direction of the wind accompanied by the action of gravity on the atmosphere outside the exhaust port, and per unit time unit flow rate at atmospheric pressure The specific energy of the wind E _FH = 1 × ρ ×
g × 10.33 m _Aq and the exhaust port static pressure P _S2 are
The flow rate maintaining energy E _F has a flow rate maintaining action of sucking the circulating air of the E _F system into the wind of the exhaust port static pressure P _S2 from the exhaust port with the predetermined flow rate as an upper limit, and causing the air to flow away without leaving a change in the wind. Therefore, when the axial flow wind turbine has no load, the inflow energy E ₁ (t · m / sec)
= (The predetermined flow rate S ₁ × V ₁₀ ) × [the specific energy E _FH of the wind per unit time unit flow rate at atmospheric pressure
{1 × ρ × g10.33 m _Aq }] = The outflow energy E ₂ was passed through the wind pressure pipe together with the predetermined flow rate of the circulating air flowing in from the inflow port and flowing out from the exhaust port, and was loaded. The axial flow wind turbine has a wind turbine drive energy E _T = {the wind turbine inflow velocity V _{G1O has} a predetermined flow rate, and the kinetic energy of the circulating air in the E _T system}-{the wind turbine at the axial outlet of the axial wind turbine. Outflow velocity V _TO (m
/ Sec) of the wind turbine drive energy E _T system kinetic energy of the circulating air} at a predetermined flow rate, the fuel cell is located at an arbitrary position between the outlet of the axial wind turbine and the exhaust port, and at the above-mentioned atmospheric pressure. The specific energy of the wind E _FH = 1 × ρ × g × 1
0.33 m _Aq and the intrinsic total pressure P _FH = ρ × g × 10.
33 m _Aq and the exhaust port static pressure P _S2 that traces back as described above and the ventilation cross-sectional area on which the dynamic pressure of the wind speed V ₂ supplied from the upstream side acts as described above is the wind turbine outflow ventilation cutoff. _By being n times the area S _G2I , the required specific energy E _FH of the circulating air per unit time unit passing flow rate 1 described above is 1 of the flow rate maintaining flow rate V _G2I .
/ N in the rear reduced ventilation cross-sectional area S _C2O obtained with the rear flow rate maintenance flow rate V _C2O , the rear flow rate maintenance supplemental kinetic energy E _C2K ≧ [rear flow rate maintenance flow rate V _C2O = {(S
₂ × V ₂₀ ) / _SC2O } kinetic energy of the circulating air at a predetermined flow rate] × [1-[{(the inflow energy E _{1 −the} wind turbine drive energy E _T ] is the rear reduced ventilation cross-sectional area S
_Velocity V _C2O0 } ² given to the circulating air passing through _C2O
/ {The inflow energy E ₁ is the rear reduced ventilation cross-sectional area S
_The rear flow rate maintaining flow velocity V _C2O } ² ]] given to the circulating air passing through _C2O is _defined as the kinetic energy of the wind turbine outflow velocity V _TO and the outflow loss compensation pressure (predetermined flow rate) × (dynamic pressure at the wind velocity V ₂ ). ) are artificially supplied to the flow rate maintained energy E _F system circulation air of the predetermined flow rate for receiving said flow maintenance action by the wind supplied and the exhaust extraoral from the upstream side, said rear reduced ventilation cross-sectional area S _C2O by maintaining the flow velocity in the said rear flow maintaining the flow velocity V _C2O, the consumption to change places form the wind turbine drive energy E _T to generate a flow rate maintained energy E _{F =} the wind turbine drive energy E _T go back to the axial flow wind turbine allowed to flow air in the flow maintaining energy E _F system of the wind pressure tube in the atmospheric pressure, the specific energy E per unit time unit passing flow per distribution air above _H = 1 × the outflow energy based on _{ρ × g × 10.33m Aq E 2} = (S 2 × V 20) to maintain the × [the specific energy _{E FH {1 × ρ × g} × 10.33m Aq}] And includes the wind turbine drive energy E _T that is present in the circulating air of the predetermined flow rate over the entire length of the wind pressure tube while rotating the runner in the circumferential direction while rotating in the axial flow wind turbine. The inflow energy E ₁ = outflow energy E ₂ and the intrinsic total pressure P _FH of the wind at atmospheric pressure P _FH = ρ × g × 10.33 m _Aq , which maintain the flow velocity in balance with the resistance. Total artificial pressure due to artificial energy P = {(the inflow / outflow loss compensation pressure)-
Wherein toward the distribution of (loss pressure)} to the specific total pressure P total pressure distribution air added to _FH P _{F =} (specific total pressure P _{FH +} human total pressure P) is the exhaust port from said inlet a predetermined The flow rate maintenance energy E _{F of the} predetermined flow rate having the outflow energy E ₂ inside the wind pressure pipe is reduced by the flow rate maintaining action of the wind outside the exhaust port that is reduced to the exhaust port static pressure P _S2 while maintaining the flow rate. The system circulating air is sucked into the wind of the exhaust port static pressure P _{S2 from} the exhaust port at the predetermined outflow velocity V ₂₀ and is allowed to flow away without leaving a change in the wind, so that the circulating air in the wind pressure pipe is by stabilizing the flow rate to the predetermined flow rate, supplied with three small artificial energy as described above, in a large wind turbines driving energy E _T of gravity acting on the flow of fluid and the flow rate maintained energy E _F Convert Drives Kijiku flow wind turbine achieves the three permanent motion engine to maintain a predetermined flow rate of the flow air in the wind tube, the wind turbine output capacitance (kW) = {a predetermined flow rate (S ₁ × V _10)}
X {g x 10.33 m _Aq } x wind turbine efficiency-{(inflow / outflow loss compensation pressure energy) + {predetermined flow rate (S ₁ x
V ₁₀ )} × (dynamic pressure of wind velocity V ₂ ) + (replenishment kinetic energy for rear flow rate maintenance E _C2K )} ÷ (power efficiency of artificial energy).

In order to solve the above problems, the method of converting gravity acting on the fluid flow into kinetic energy according to the first, second, third or fourth invention of the present application, is an inflow of a water (windmill) turbine. The water (wind) cross-sectional area S _G1O is made larger than the water (wind) _turbine outflow water (air) cross-sectional area S _G2I , and the water (wind) in the water (wind) vehicle inflow water (air) cross-sectional area S _G1O ) Vehicle inflow velocity V
_G1O is the water (wind) _turbine outflow water (air) cross-sectional area S _G2I
Of the flow velocity maintaining flow velocity V _{G2I of the} water (wind) _turbine and the flow maintaining flow velocity V _G1O.
It is preferable to partially share the inflow / outflow loss compensation pressure of the artificial energy and the dynamic pressure of the water (wind) velocity V ₂ by the difference with the dynamic pressure of _G2I .

In order to solve the above-mentioned problems, the method for converting gravity acting on the fluid flow into kinetic energy according to the first, second, third or fourth aspect of the present invention is to solve the above problems. If the water fluctuates, or if the water (wind) speed fluctuates, a predetermined flow rate and man-made energy are adjusted according to the expected maximum value of the fluctuating water (wind) turbine load or the fluctuating water (wind) speed. Inflow / outflow loss compensation pressure energy and {predetermined flow rate (S ₁ × V
₁₀ )} × {dynamic pressure of water (wind) speed V ₂ } and supplemental kinetic energy E _C2K for maintaining rear flow rate, water (wind) _turbine inflow water (air) cross-sectional area S _G1O and water (wind) _turbine outflow The water (wind) cross-sectional area S _G2I is adjusted to adjust the water (wind) _turbine inflow water (air) cross-sectional area S _G1O to the water (wind) _turbine inflow velocity V _G1O.
And the flow rate maintenance flow velocity V _G2I in the water (wind) _turbine outflow water (gas) cross-sectional area S _G2I are maintained at predetermined values, and the output of the water (wind) _turbine is _adjusted to the load and the water (wind) speed, and It is preferable to maintain the rotation speed of the water (wind) wheel at a predetermined value.

In order to solve the above problems, the method for converting gravity acting on the fluid flow into kinetic energy according to the first, second, third or fourth invention of the present application is intended to solve the above problems. When a speed governor is added to the output side of the water flow rate and the water (wind) speed decreases, a predetermined flow rate, pressure energy for compensating inflow / outflow loss of artificial energy and {predetermined flow rate (S ₁ × V ₁₀ )} × { The dynamic pressure of water (wind) speed V ₂ } and the supplemental kinetic energy E _c2k for maintaining the rear flow rate are adjusted according to the fluctuation of the water (wind) speed to compensate for the energy loss caused by the artificial energy in the _penstock. The water (wind) _turbine inflow water (air) cross-sectional area S _G1O , the water (wind) _turbine outflow water (air) cross-sectional area S _G2I, and the adjusted predetermined flow rate. Decided and decreased water (wind) _turbine inflow velocity V _G1O and flow rate maintenance velocity V _G2I
The axial flow water (wind) wheel is driven by and the reduced rotational speed of the axial flow water (wind) wheel is adjusted to a predetermined rotational speed by the speed governor and output. It is preferable to match the (wind) speed.

Further, in order to solve the above-mentioned problems, the method of converting gravity acting on the fluid flow into kinetic energy according to the first, second, third or fourth invention of the present application, is to reduce the rear reduced water flow (gas ) draining the cross-sectional area S _C2O (air) supply of rear outflow loss compensation pressure energy rear outflow energy loss occurring between the mouth to compensate the 0, water (wind) car drive energy E _T system running water (flow air) From the supply to the above, the rear reduced water flow (Qi)
_Preference is given to transferring with a cross-sectional area S _C2O .

In order to solve the above problems, the device for converting gravity acting on the fluid flow into kinetic energy according to the fifth aspect of the present invention has the effect of gravity on the atmosphere and the water flow and the water depth H.
Flow velocity V _H (m / sec) at (m) and gravity flow to the atmosphere and water flow that acts on each part of the water flow and maintains resistance to each part of the water flow and maintains the water speed V _H at the water depth H _{Unidirectional} total pressure P _FH = specific static pressure P _SH + specific dynamic pressure P _KH = [ρ × g × due to the pressure bias due to the action in the direction and the action of gravity on the atmosphere and the water flow at the water depth H
_{(H + 10.33m Aq) - {} ρ × (V H) 2 ÷ 2}]
+ {Ρ × (V _H ) ² ÷ 2} = ρ × g × (H + 10.33
m _Aq ) (t / m ² ) and a unit time unit flow rate 1 (m ³ / sec) based on the action of gravity on the atmosphere and water flow
Specific energy E _FH of water flow at said water depth H per
(The specific pressure energy E corresponding to the specific static pressure P _SH
PH ) + (specific kinetic energy E _KH corresponding to the specific dynamic pressure P _KH ) = 1 (m ³ / sec) × [ρ × g × (H +
10.33 m _Aq )-{ρ × (V _H ) ² ÷ 2}] (t /
^{m 2) +1 (m 3 /} sec) × {ρ × (V H) 2 ÷ 2}
(T / m ² ) = 1 × ρ × g × (H + 10.33m _Aq )
(T · m / sec), in a water stream that circulates on a global scale such as a sea current or a tidal current, in a water stream that flows by a gradient such as a river or an open channel, or relative movement with water. The cross-sectional area S ₁ (in the moving body above or under water, which can treat the force for maintaining and the relative velocity with water as the pressure bias due to the action of gravity in the flow direction on the atmosphere and the water flow and the water velocity V _H , m ² ) at the inlet of the flow velocity V ₁ (m / se
c) Arbitrary water depth H ₁ (m), the axial flow turbine provided near the center is placed at water depth H (m), and the drainage port of water cross section S ₂ (m ² ) is It is arranged at the water depth H at a speed of V ₂ (m / sec) or at a water depth H ₂ (m) deeper than the water depth H, and the water passage cross-sections S ₁ and S ₂ are calculated based on the equation for the water turbine output capacity described later ( S ₁ × predetermined inflow velocity V ₁₀ ) = (S ₂ × predetermined outflow velocity V ₂₀ below water velocity V ₂ ) (m ³ / sec) =
(A predetermined flow rate that provides a required output), and the water flow cross-sectional area from the inflow _port toward the axial water turbine is increased by the water flow and the water wheel inflow velocity V _G1O (m / se
In c), it is reduced to a turbine inflow water cross-sectional area S _G1O (m ² ) so as to flow into the axial water turbine, and the water cross-sectional area from the drain port to the axial water turbine is set to the axial water turbine. towards waterwheel outlet water passage cross-sectional area S _{G2I (m 2)} which is flowing water flowing out from the axis running water wheel while deflected circumferentially passes at a rate maintaining the flow velocity V _{G2I (m /} sec) and ⁼ the water turbine inlet passage A hydraulic pipe connected in a circumferentially deflected state to an axial outlet of the axial flow _turbine having a larger water cross-sectional area by gradually reducing to a water sectional area S _G1O , the inlet and the axial flow water. All of the inflow loss pressure (t / m ² ) generated in the flowing water of the predetermined flow rate of the turbine driving energy E _T system between the vehicle outlets,
Outflow loss Pressure (t / m ²⁾ inflow and outflow loss compensation pressure and all compensating to zero the generated running water of the predetermined flow rates maintain the energy E _F system between the outlet and the water outlet of the shaft running water wheel Inflow / outflow loss compensation pressure energy (t · m / sec) that generates (t / m ² ) = (S ₁ × V ₁₀ ) ×
(Inflow / outflow loss compensation pressure) and {predetermined flow rate (S ₁ × V
_10)} × (a front flow maintains pressure pumping water means for supplying running water of the water turbine drive energy E _T based water speed V ₂ dynamic) and the water pressure pipe, the drainage and the axis running water car outlet In the rear reduced water flow cross-section S _C2O at any position between the mouths, the supplemental kinetic energy for rear flow rate maintenance E _C2K ≧ [rear flow rate maintenance flow velocity V _C2O = {(S ₂ × V ₂₀ ) /
S _C2O } kinetic energy of flowing water at a predetermined flow rate] × [1-
[{(The inflow energy E ₁ −the water turbine drive energy E
Flow velocity V _C2O0 } ² / {inflow energy E ₁ given by _T ) to the flowing water passing through the rear reduced water flow cross-sectional area S _C2O
Said rear flow maintaining the flow velocity V _C2O} ^2]], the rear flow maintains pressure pumping for supplying the running water of the flow rate maintained energy E _F system of the predetermined flow rate but that gives the water flow passing through said rear reduced water passage cross-sectional area S _C2O Water means, and water turbine output capacity (kW) = {predetermined flow rate (S ₁ × V ₁₀ )}
X {g x (H + 10.33 m _Aq )} x turbine efficiency-
{(Inflow / outflow loss compensation pressure energy) + {Predetermined flow rate (S ₁ × V ₁₀ )} × ( _Dynamic pressure of water velocity V ₂ ) + (Replacement kinetic energy for rear flow rate maintenance E _C2K )} ÷ (of artificial energy Power efficiency).

In order to solve the above-mentioned problems, the device for converting gravity acting on the flow of fluid into kinetic energy according to the sixth aspect of the present invention and the action of gravity on the atmosphere and the wind speed V _H (m / m).
sec) and the resistance to the movement of each part of the atmosphere and the resistance to the movement of each part of the atmosphere are balanced, and the bias of the pressure in the direction of the wind accompanied by the effect of gravity on the atmosphere maintaining the wind velocity V _H and the effect of gravity on the atmosphere Inherent total pressure P _FH of wind at the wind speed V _H = Inherent static pressure P _SH + Inherent dynamic pressure P _KH = [ρ × g ×
_{10.33m Aq - {ρ A × (} V H) 2 ÷ 2}] + {ρ
_A × (V _H ) ² ÷ 2} = ρ × g × 10.33 m _Aq (t
/ M ² ) and the wind speed V _H per unit time unit flow rate 1 (m ³ / sec) based on the action of gravity on the atmosphere
Specific energy of the wind E _FH = (specific pressure energy E _PH corresponding to the specific static pressure P _SH ) + (the specific dynamic pressure P _SH
Specific kinetic energy corresponding to ^{_{KH E KH) = 1 (m}} 3 /
sec) × [ρ × g × 10.33m Aq - {ρ A × (V
_H ) ² ÷ 2}] (t / m ² ) +1 (m ³ / sec) ×
{Ρ _A × (V _H ) ² ÷ 2} (t / m ² ) = 1 × ρ × g ×
In the wind having 10.33 m _Aq (t · m / sec), or the force for maintaining the relative motion with the atmosphere and the relative velocity with the atmosphere in the direction of the wind accompanied by the action of gravity on the atmosphere. in the mobile in the atmosphere can handle a bias pressure as the wind speed V _H of has an inlet ventilation cross-sectional area S _{1 (m} ²⁾ in the position of the wind speed V _{1 (m} / sec), the central axial flow wind turbine And an exhaust port having a ventilation cross-sectional area S ₂ (m ² ) near the wind speed V
Has at the position of ₂ (m / sec), the corrected changes in [rho _A by the flow rate ventilation cross-sectional area _S 1, _{S 2,} based on the formula of the windmill output capacity of below, _{(S 1} × predetermined inlet flow rate V ₁₀ )
= (S ₂ × predetermined outflow velocity V ₂₀ below V ₂ ) (m ³
/ Sec) = (predetermined flow rate at which a required output is obtained), and the ventilation cross-sectional area from the inlet to the axial wind turbine is increased by the circulating air to increase the wind turbine inflow velocity V.
_G1O (m / sec) is reduced to a wind turbine inlet ventilation cross-sectional area S _G1O (m ² ) so as to flow into the axial wind turbine, and the ventilation cross-sectional area from the exhaust port to the axial wind turbine is changed to the axial flow. The circulating air flowing out from the axial-flow wind turbine while being deflected in the circumferential direction toward the wind turbine is a flow-rate maintaining flow velocity V.
_Wind turbine outflow ventilation cross-section area S passing at _G2I (m / sec)
_G2I (m ² ) = a wind turbine connected to the axial outlet of the axial wind turbine in a state of being circumferentially deflected while being gradually reduced to the wind turbine inflow ventilation cross-sectional area S _G1O and having a larger ventilation cross-sectional area. the a whole inflow loss pressure generated in the distribution air in the predetermined flow rate of the wind turbine drive energy E _T system between the outlet of said inlet and said axial flow wind turbine (t / m ^2), and outlet of the axial flow wind turbine exhaust Inlet / outlet loss compensating pressure (t / m ² ) for compensating to 0 all of the outflow loss pressure (t / m ² ) generated in the circulating air of the above-mentioned predetermined flow rate of the flow rate maintenance energy E _F system between the ports
Inflow / outflow loss compensating pressure energy (t ・ m
/ Sec) = (S ₁ × V ₁₀ ) × (inflow / outflow loss compensation pressure) and {predetermined flow rate (S ₁ × V ₁₀ )} × (dynamic pressure at wind speed V ₂ ) as the wind turbine drive energy in the wind pressure pipe a front flow maintains pressure pumping air means for supplying the flow of air E _T system, at the rear reduced airflow cross-sectional area S _C2O at an arbitrary position between the outlet and the exhaust port of the axial flow wind turbine, supplemental rear flow maintained Kinetic energy E _C2K ≧ [rear flow rate maintenance flow velocity V _C2O =
{(S ₂ × V ₂₀ ) / S _C2O } kinetic energy of circulating air at a predetermined flow rate] × [1-[{(the inflow energy E ₁
The flow velocity V _C2O0 } ² / {where the inflow energy E ₁ passes through the rear reduced ventilation cross-sectional area S _C2O that the wind turbine drive energy E _T ) gives to the circulating air passing through the rear reduced ventilation cross-sectional area S _C2O The rear flow rate maintaining flow velocity V _C2O } ² ]] to the circulating air of the flow rate maintaining energy E _F system at the predetermined flow rate, and a wind turbine output capacity (kW) = {Predetermined flow rate (S ₁ × V ₁₀ )}
X {g x 10.33 m _Aq } x wind turbine efficiency-{(inflow / outflow loss compensation pressure energy) + {predetermined flow rate (S ₁ x
V ₁₀ )} × (dynamic pressure of wind velocity V ₂ ) + (replenishment kinetic energy for rear flow rate maintenance E _C2K )} ÷ (power efficiency of artificial energy).

In order to solve the above problems, the apparatus for converting gravity acting on the flow of fluid into kinetic energy according to the fifth and sixth inventions of the present invention, the hydraulic pipe or the wind pipe is provided with water flowing from the inflow port. An inflow portion having a water (air) passage with a reduced (air) cross-sectional area, a front cylindrical similar space connected to the inflow portion, and a deflection in the circumferential direction in the front cylindrical similar space. It consists of a plurality of front guide vanes that gradually increase the angle and gradually reduce the water (air) cross-sectional area of the front cylindrical similar space, and the water (wind) turbine inflow water (air) at the outlet. Cross-sectional area S
_G1O (m ² ) and a water (wind) wheel inflow velocity V _G1O (m / sec) of running water (circulating air), and a front guide vane portion having the water (wind) wheel inflow velocity V _G1O. By receiving the flowing water (circulating air) that is deflected in the circumferential direction from the guide vanes and flowing out, the direction of the water (wind) _turbine inflow velocity V _G1O that is deflected in the circumferential direction is changed to the axial direction. Wind) Vehicle inflow velocity V _G1O circumferential component velocity V _TK
It is rotationally driven in the circumferential direction with kinetic energy of (m / sec), and the water (wind) _turbine outflow velocity V _TO is determined by the axial component flow velocity of the water (wind) _turbine inflow velocity V _G1O or the load factor.
At (m / sec), flowing water (circulating air) is let out from the water (wind) wheel outlet of the water (air) cross-sectional area S _TO (m ² ) and {(water (wind) wheel inflow velocity V _G1O kinetic energy ) - a shaft running water (wind) car with a (water (wind) runners driven by a drive outflow velocity V _tO of consisting kinetic energy)} water (wind) car drive energy E _T, said axis running water (wind) car Output device for transmitting the output of the, the rear cylindrical similar space connected to the outlet of the axial water (wind) turbine, the deflection angle in the circumferential direction at the upstream inlet in the rear cylindrical similar space The inlet is composed of a plurality of rear guide vanes that are the largest and gradually reduce the deflection angle in the circumferential direction toward the downstream to gradually increase the water (air) cross-sectional area of the rear cylindrical similar space. Water (wind) turbine outflow cross-sectional area S at
_Flow rate maintenance flow velocity V of _G2I (m ² ) and running water (circulating air)
_{It is preferable} to have a rear guide vane part having _G2I (m / sec), and an outflow part connected to the outlet of the rear guide vane part and gradually increasing the water (air) cross-sectional area thereof.

[0017]

Although there are 11 claims of the present invention, since the basic functions are common, they will be described collectively. First, the present invention shows that the total energy in each flow tube of a fluid flow under the action of gravity is represented by the concept of the conventional Bernoulli equation of fluid dynamics =
The error that the kinetic energy + pressure energy + potential energy is moving from the upstream side to the downstream side of the flow is corrected and treated as follows. That is, of the total energy in each flow tube of the fluid flow, the pressure energy is, for each part in each flow tube, independently constituted by the static pressure of that part and is essentially No transfer or potential energy can exist because each part of the fluid flow is surrounded by fluid of the same mass, and kinetic energy is the moving fluid because the entire fluid is a carrier of energy. However, it is the gravity acting on the fluid flowing above each part of each flow tube of the fluid flow, and the static pressure of the fluid generated by the action of gravity causes the kinetic energy to move. The presence of a directional gradient causes the flow to be biased in the direction of flow, which acts individually on each part of the flow of fluid in each flow tube, causing a flow velocity that is commensurate with the resistance to be individually generated in each flow tube. There is. The Bernoulli equation can be used for penstocks that are in the air and subject to potential energy, but not for fluid flow and flowtubes that are in fluid flow. The details will be described below.

Regarding the flow of fluid: 1. The flow velocity of each part of the fluid flowing by the action of gravity is a bias of the pressure due to the static pressure acting on that part by gravity and the gradient of the static pressure isostatic surface parallel to the gradient surface of the surface of the fluid flow. Decided. In the case of wind, it depends on the bias of the pressure in the direction of the wind accompanied by the action of gravity on the atmosphere, that is, in the direction of the isobar of atmospheric pressure. Explain. Water velocity V _H (m / s at depth H (m) of water flow due to the action of gravity
ec) is the water velocity V _H at the water depth H so that the pressure bias due to the action of gravity in the flow direction on the atmosphere and the water flow is in a state of acting on each part of the water flow and balancing with the resistance to each part of the water flow. Have decided.

2. Therefore, the total pressure of the water flow at the water depth H is determined by the action of gravity on the atmosphere and the water flow, and the intrinsic total pressure P _FH of the water flow at the water depth H = intrinsic static pressure P _SH + intrinsic dynamic pressure P _KH
= [Ρ × g × (H + 10.33m _Aq ) − {ρ ×
(V _H ) ² ÷ 2}] + {ρ × (V _H ) ² ÷ 2} = ρ × g
It becomes x (H + 10.33 m _Aq ) (t / m ² ).

3. Also, the energy per unit time unit flow rate 1 (m ³ / sec) of the water flow at the water depth H is determined by the action of gravity on the atmosphere and the water flow, and the natural energy E _FH of the water flow at the water depth H = specific pressure energy _E PH) corresponding to the static pressure _{P SH} + (the inherent dynamic pressure _P inherent kinetic energy corresponding to ^{_{KH E KH) = 1 (m}} 3 / sec)
× [ρ × g × (H + 10.33m _Aq ) − {ρ ×
(V _H ) ² ÷ 2}] (t / m ² ) +1 (m ³ / sec)
× {ρ × (V _H ) ² ÷ 2} (t / m ² ) = 1 × ρ × g ×
(H + 10.33 m _Aq ) (t · m / sec).

4. As described above, the flow velocity and the flow rate are determined by the gradient of the water surface, and the total pressure of the water flow and the energy per unit time unit flow rate are eigenvalues determined by the action of gravity on the atmosphere and the water flow and the water depth. Therefore, by adding the word “specific”, the specific total pressure P _FH of the water flow at the water depth H = the specific static pressure P
_SH + intrinsic dynamic pressure P _KH = ρ × g × (H + 10.33 m
_Aq ) (t / m ² ), specific energy E of water flow at water depth H
_FH = (the unique static _P specific pressure energy corresponding to the _{SH E} PH) + (the inherent dynamic pressure _{P KH} corresponding to the unique kinetic energy _{E KH) = 1 × ρ ×} g × (H + 10.33m
_Aq ) (t · m / sec) can be distinguished from static pressure and dynamic pressure due to artificial energy. Therefore, the force acting on each part of the water flow in the flow direction changes corresponding to the water depth of that part,
Since there is a force that interacts between adjacent flow pipes in the depth direction of the water flow, even if the flow becomes a steady flow, friction and energy flow in and out between the side faces of the flow pipes adjacent in the depth direction of the water flow. Is always present. Then, according to this idea of the present invention, it is possible to explain a well-known phenomenon that the flow velocity of a portion slightly below the water surface is the fastest in the water flow. Bernoulli's equation treats a steady stream of water as a complete fluid, with no friction or energy flow between the sides of the flow tube.
This is convenient for explaining the law of conservation of energy, but unlike the substance, in reality, there is a loss due to friction between the side surfaces of the flow tube in each part of the flow tube, and the loss is above that part. The effect of gravity on the flow of a certain fluid is supplemented. Also, the potential energy of Bernoulli's equation exists in the penstock in the air, but in the case of a penstock in the water flow, it cannot be offset by the potential energy of the water flow outside the penstock.

5. According to the above theory of the present invention relating to the energy of the fluid flow, whether in the case of water flow or wind in an open channel, or in the case of running water or circulating air in a conduit, each part of these fluids is exposed to the atmosphere or water flow. As long as static pressure is supplied to each part of the fluid by the action of gravity or the supply of artificial energy, when the force is exerted by the action of gravity or artificial energy on each part of the fluid, the force and the fluid The fluid moves at a speed that balances the resistance to the movement of the fluid. Then, at that time, the total pressure of each part of the fluid becomes the total pressure = the dynamic pressure of the moving speed of the fluid + the static pressure corresponding to the moving speed of the fluid. Inherent total pressure P _FH = intrinsic static pressure P _SH + intrinsic dynamic pressure P _KH = [ρ × g × (H + 10.33m _Aq ) − {ρ
× (V _H ) ² ÷ 2}] + {ρ × (V _H ) ² ÷ 2} = ρ ×
It can be separated as g × (H + 10.33m _Aq ) (t / m ² ). For the running water in the penstock, the continuous equation of fluid dynamics is established, and the specific energy per unit time unit passing flow rate is determined by the water depth, so the flow velocity of each part of the penstock is determined by the flow velocity of each part of the penstock. Since it can be fixed by the cross-sectional area, and the whole water is an energy carrier, the specific energy E _FH = (corresponding to the specific static pressure P _SH of the water flow at the water depth H possessed by the water flow in each part of the penstock specific kinetic energy _E KH) ^{= 1} corresponding to the unique pressure energy _E PH) + (the inherent dynamic pressure _{P KH (m 3 / sec)} ×
[Ρ × g × (H + 10.33m _Aq ) − {ρ × (V _H ).
² ÷ 2}] (t / m ² ) +1 (m ³ / sec) × {ρ ×
(V _H ) ² ÷ 2} (t / m ² ) = 1 × ρ × g × (H + 1
0.33 m _Aq ) can be fixed by the water passage cross-sectional area of each part of the penstock. For example, when a hydraulic tube with a turbine in the center is installed in the water flow, by adjusting the water passage cross-sectional area of each section of the hydraulic tube, various energy supplied to the upstream side of the turbine can be used to control the energy of the turbine. The energy that should be consumed up to the outlet can be consumed up to the outlet of the water turbine, and the energy that should be passed to the downstream side of the water turbine as it is can pass through the water turbine. Therefore, if the water passage cross-sectional area of the penstock is set as in the present invention, the intrinsic total pressure of the water flow in the vicinity of the inlet acts from the inlet of the penstock to the water wheel, and the drainage of the penstock from the outlet to the water wheel. The specific static pressure of the water flow near the mouth is traced back, and pressure energy corresponding to the dynamic pressure of the water velocity V ₂ of the water flow near the drainage port is supplied from the inlet of the penstock to reduce the pressure on the downstream side of the water turbine. The static pressure in the hydraulic pipe is the above-mentioned inherent static pressure + pressure energy corresponding to the dynamic pressure of the water velocity V ₂ of the water flow near the drainage port = the specific total pressure, and the running water in the hydraulic pipe on the downstream side of the water turbine If the kinetic energy is applied to the water flow, the above-mentioned specific energy can be generated in the water flow by adjusting the other requirements of the present invention.

6. For penstock, cross-sectional area S
The inflow port of ₁ (m ² ) is arranged at an arbitrary water depth H ₁ (m) of the flow velocity V ₁ (m / sec), and the axial flow turbine provided near the central portion is arranged at the water depth H (m), Water cross section S ₂ (m ² )
Of the drainage port of the water is arranged at the water depth H of water velocity V ₂ (m / sec) or at a deeper water depth H ₂ (m), and the water passage cross-section S
₁ and S ₂ based on the formula for the hydraulic turbine output capacity described later (S
₁ × predetermined inflow velocity V ₁₀ ) = (S ₂ × predetermined outflow velocity V ₂₀ equal to or less than water velocity V ₂ ) (m ³ / sec) = (predetermined flow rate at which required output is obtained) The cross sectional area of water flowing into the turbine S _G1O (S _G1O so that the flowing water is accelerated to flow into the axial flowing turbine at a flow velocity of the turbine flowing into the turbine of V _G1O (m / sec). m
² ) to maintain the flow rate of running water flowing out from the axial flow turbine while reducing the water flow cross-sectional area from the drain port to the axial flow turbine in the circumferential direction toward the axial flow turbine. Turbine outflow cross-sectional area S _G2I (m ² ) = turbine inflow cross-sectional area S passing at a flow velocity V _G2I (m / sec)
_G1O is gradually reduced to a larger flow cross-sectional area and connected to the outlet in the pongee direction of the axial flow _turbine in a state of being deflected in the circumferential direction.

7. As described above, when the water passage cross-sectional area is reduced from both the inlet and the outlet of the penstock toward the axial flow turbine in the central part of the penstock, the characteristic of the water flow at the water depth H is obtained. The total pressure P _FH acts from the inflow port to the axial flow turbine, and the specific static pressure P _SH of the water flow at the water depth H acts from the drain port back to the axial flow turbine. In this case, what goes back from the drainage port is not the energy accompanied by the movement of water but the static pressure that does not move the water. However, from the above description of the intrinsic total pressure P _FH and the intrinsic energy E _FH , in order to maintain the flow rate by aligning the intrinsic energy E _FH per unit time unit flow rate over the entire length in the penstock, to maintain the flow rate, In between, the intrinsic total pressure P
Inherent dynamic pressure P _KH = which is the difference between _FH and inherent static pressure P _SH
It is necessary to artificially supplement {ρ × (V _H ) ² ÷ 2}. This replenishment of the dynamic pressure cannot be performed retroactively from the drainage port, so at the same time when the inflow / outflow loss compensation pressure, which will be described later, is supplied to the running water in the hydraulic pipe on the upstream side of the water turbine,
Supply from the upstream side of the axial flow turbine.

8. The flowing water in the penstock has no gravity effect from the side due to the obstruction of the penstock, and even if the penstock has a gradient, the gravity effect on the running water in the penstock is as described above. It is offset by the effect of gravity on the water flow outside the penstock. Therefore, the above 7. As described in the section, the action of gravity acts only as the intrinsic total pressure P _FH from the inlet and the intrinsic static pressure P _SH from the drain. Therefore, in order to generate a flow rate act on the flowing water of the water pressure tube, as described below, the inflow and outflow loss compensation pressure, artificially running water waterwheel drive energy E _T system lying between the inlet and the waterwheel outlet Need to be supplied to.

9. For the inflow and outflow loss compensation pressure, and all of the inflow loss pressure generated flowing water of a predetermined flow rate of the water turbine drive energy E _T system between the inlet and the shaft running water wheel outlet (t / m ^2), the axis running water car outlet a flow rate maintained energy E _F system of outflow losses pressure generated flowing water of a predetermined flow rate between the drain port (t /
Inflow / outflow loss compensation pressure energy (t · m / sec) for generating inflow / outflow loss compensation pressure (t / m ² ) for compensating all of m ² ) and 0 to (S ₁ × V ₁₀ ) × ( Inflow
Outflow loss compensation pressure) and (the predetermined flow rate) × (the dynamic pressure of the water velocity V ₂ ) are the bias of the pressure due to the action of gravity in the water flow of nature on the aforementioned atmosphere and water flow, and , The specific total pressure P _FH and the specific static pressure P _SH
As corresponding to the difference between the artificially supplied to running water of the water turbine drive energy E _T system of the water pressure pipe.

10. When there is static pressure due to the action of gravity in the penstock and the inflow / outflow loss compensation pressure is supplied, the inflow / outflow loss compensation pressure has a gradient distribution in which the resistance of the penstock is large. It acts on the entire length and generates a bias in the static pressure of each part in the penstock that is necessary to maintain a predetermined flow rate, thereby ensuring a predetermined flow rate. And in this case, the static pressure is reduced by the dynamic pressure of the flow velocity generated in each part,
Excluding the inflow / outflow loss compensation pressure artificially supplied,
The total pressure due to the action of gravity is similar to the case of the water flow under the action of gravity described above, and the intrinsic total pressure P _FH of the water flow at the water depth H =
Intrinsic static pressure P _SH + Intrinsic dynamic pressure P _KH = ρ × g × (H + 1
0.33 m _Aq ), and the energy per unit time unit passing flow rate is also the specific energy E per unit time unit passing flow rate of the water flow at the water depth H, as in the case of the water flow under the action of gravity described above. _FH = (the intrinsic static pressure P
Specific pressure energy _E PH corresponding to the _SH) + (the unique hydrodynamic inherent kinetic energy corresponding to _{P KH E KH)} 1 × _ρ
To become _{× g × (H + 10.33m Aq} ).

11. As described above, in the water flow or the penstock, at the water depth H, the intrinsic total pressure P _FH of the water flow at the water depth H = intrinsic static pressure P _SH + intrinsic dynamic pressure P _KH = ρ × g ×
(H + 10.33 m _Aq ) and specific energy E _FH per unit time unit passing flow rate of water flow at water depth H = (specific pressure energy E _PH corresponding to the specific static pressure P _SH ) +
(Natural kinetic energy E corresponding to the above-mentioned intrinsic dynamic pressure P _KH
KH ) 1 × ρ × g × (H + 10 · 33 m _Aq ) are commonly present.

12. Therefore, when there is no load on the axial flow turbine, if the inflow / outflow loss compensating pressure energy described later and (the predetermined flow rate) × (the dynamic pressure of the water speed V ₂ ) are artificially replenished, the central portion A predetermined amount of flowing water flows in the penstock having a reduced aeration cross-sectional area.

13. For flow maintains action, regardless of whether the load of the shaft running water wheel, the flowing water of the flow rate maintained energy E _F system, the outflow energy E _{2 (t} · m / se
c) = (S ₂ × V ₂₀ ) × [the specific energy E of the water flow per unit time unit flow rate at the water depth H]
_{If FH} {1 × ρ × g × (H + 10.33m _Aq )}] exists, the action of gravity on the atmosphere and the water flow at the outlet and the flow direction of gravity on the atmosphere and the water outside the outlet are described. Of the pressure due to the action of and the specific energy E _FH = 1 × ρ × g × (H + 10.33 m _Aq ) of the water flow per unit time unit flow rate at the water depth H
When, with the water outlet static pressure P _S2 is, the suction flowing water flow maintaining the energy E _F system from drain outlet said predetermined flow rate as an upper limit in water of the water outlet static pressure P _S2, leaving a change in water flow It has the function of maintaining the flow rate without causing it to flow away. The flow rate maintained action, even the shaft running water vehicle consumes water turbine driving energy E _T, inflow and outflow losses and compensating pressure energy is small three human energy (the predetermined flow rate) ×
( _Dynamic pressure at the water velocity V ₂ ) and supplemental kinetic energy E _C2O for maintaining the rear flow rate, which will be described later, are simply supplied to the running water in the _penstock to generate large energy: [{unit time at the water depth H. The specific energy E _FH of the water flow per unit passing flow rate 1 × 1 × ρ × g × (H + 10.33 m _Aq )} ×
(The predetermined flow rate)] can be maintained. And
Although the existence of this flow maintaining function enables the realization of the third type permanent motion engine, the concept of Bernoulli's equation does not allow this flow maintaining operation to exist. This is the third one ever
It is presumed that this is one of the reasons why he did not notice the possibility of realizing a permanent movement engine.

14. Regarding the supplemental kinetic energy E _C2K for maintaining the rear flow rate when driving the axial flow turbine, the loaded axial flow turbine has a turbine drive energy E _T =
{Running water kinetic energy of the water wheel drive energy E _T system at a predetermined flow rate of water turbine inlet flow velocity V _G1o} - {predetermined flow rate of the water wheel drive of a wind turbine outflow velocity V _TO in the axial direction of the outlet of the axial flow wind turbine _(m / sec) when consuming the flowing water of kinetic energy} energy E _T system, drain outlet static pressure P dating back as described above
_S2 and the water velocity V ₂ supplied from the upstream side as described above
Of the water flow at the water depth H and the intrinsic total energy P _FH = ρ × g × (H + 10.33m _Aq ) and the intrinsic energy E _FH = 1 × ρ × g × (H + 10.33m _Aq ). ) And the cross-sectional area of water flow that constitutes n ₎ are n times the cross-sectional water flow area of the turbine outflow S _G2I at the outlet of the axial flow turbine, and the rear reduced ventilation cutoff at any position between the outlet of the axial flow turbine and the drain port. In the area S _C2O , the supplemental kinetic energy for maintaining the rear flow rate E _C2K ≧
[Rear flow rate maintenance flow velocity V _C2O = {(S ₂ × V ₂₀ ) / S
_2O } kinetic energy of flowing water at a predetermined flow rate] x [1-
² / {inflow energy _{E 1} is a rear reduced water passage cross-sectional area _{S C2O} - {(waterwheel orbital energy _{E T} inflow energy _{E 1)} flow velocity _{V C2O0} give flowing water passing through the rear reduced water flow cross-sectional area _{S C2O}} where [ The rear flow rate maintenance flow velocity V _C2O } ² ]] given to the flowing water is _{calculated as} the kinetic energy of the wind turbine outflow velocity V _TO and the outflow loss compensation pressure (predetermined flow rate) × (the water velocity V ₂
Dynamic pressure) and is artificially supplied to running water flow maintaining the energy E _F system at a predetermined flow rate to undergo flow maintenance action by water flow supplied and drained extraoral from the upstream side, in the rear reduced water passage cross-sectional area S _{C2O Is} maintained at the rear flow rate maintaining flow rate V _C2O .

15. Thus, the consumption in the change places the form of water turbine driving energy E _T to generate a flow rate maintained energy E _{F =} the water turbine driving energy E _T was go back to the axis running water wheel, the flow rate maintained energy E of pressure tube in water depth H _F
In the flowing water of the system, the specific energy E _FH per unit time unit passing flow rate of the above-mentioned flowing water is E _FH = 1 × ρ × g × (H + 1
The outflow energy E ₂ = (S based on 0.33 m _Aq ).
₂ × V ₂₀ ) × [said characteristic energy E _FH {1 × ρ × g
X (H + 10.33m _Aq )}] can be maintained.

16. Summarizing the above, the turbine drive energy E that exists in the running water of the axial flowing water turbine while rotating the runner in the circumferential direction to the running water of the predetermined flow rate over the entire length of the penstock
Including the _T , the inflow energy E ₁ = outflow energy E ₂ based on the action of gravity on the atmosphere and the water flow, and as shown in FIG. 2, the intrinsic total pressure P _FH at the water depth H = ρ × g × (H + 1
0.33 m _Aq ), and the artificial total pressure P = {(inflow ·
Outflow loss compensation pressure) - (Loss pressure) total pressure P _F distribution of the flowing water was added to the specific total pressure P _FH of} ₌ (specific total pressure P _{FH +} human total pressure P) is toward the drain outlet from the inlet The static pressure P _{S2 is} reduced while maintaining a predetermined flow rate, and the flow rate maintaining action of the water flow outside the drain port has an outflow energy E in the water pressure pipe.
Flow rate maintenance energy E _F system running water having a predetermined flow rate having ₂ is discharged from the drain port at a predetermined outflow velocity V ₂₀ and the drain port static pressure P _S2.
By sucking into the water flow of No.3 and letting it flow away without leaving any change in the water flow, and stabilizing the flow rate of the flowing water in the penstock, it receives the supply of three small artificial energy and acts on the fluid flow. gravity is converted into a large water wheel drive energy E _T and the flow rate maintained energy E _F realizes the three permanent motion engine to maintain a predetermined flow rate of flowing water driven by water pressure tube axis running water wheel, the water wheel output capacity (kW ) = {Predetermined flow rate (S ₁ × V ₁₀ )}
× {g × (H + 10.33m _Aq } × water turbine efficiency − {(inflow / outflow loss compensation pressure energy) + {predetermined flow rate (S ₁ ×
V ₁₀ )} × (dynamic pressure of water velocity V ₂ ) + (replacement kinetic energy for rear flow rate maintenance E _C2K )} ÷ (power efficiency of artificial energy)

The first invention of the present application is intended for a water turbine, and since atmospheric pressure can be utilized, it can be economically implemented even with a shallow water flow. When it is used for a moving body, the output is generated only by a phenomenon inside the penstock and does not affect the outside, so that the increase in resistance is small and the increase in the propulsive force of the moving body is small.

In the second invention of the present application, when the gradient waterway of the open waterway is placed on the upper side and the circulation / condensation waterway of the closed waterway is placed on the lower side, the pumping head of the water pumping means necessary for obtaining a predetermined water flow is provided. The specific total pressure that can be used is ρ × g.
× 10.33m _Aq or more, so even if efficiency is considered,
You can get enough output.

In the third invention of the present application, the water level difference can be effectively utilized to eliminate or at least reduce the energy supplied from the outside at the start.

The fourth invention of the present application is intended for a wind turbine, and since atmospheric pressure can be used, an extremely large output can be obtained as compared with a conventional wind turbine. And when using it for mobiles,
The output is generated only by the phenomenon inside the wind pressure tube and does not affect the outside, so that the increase in resistance is small and the increase in the propulsive force of the moving body can be small.

[0038]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The first invention of the present application is a case where the fluid flow is a water flow, and the fourth invention of the present application is a case where the fluid flow is a wind. However, since these principles are the same, the case where the fluid flow is a water flow will be described as the first embodiment.

In the first embodiment, the depth H of the strait with a tidal current is H =
At the seabed of 30m, a penstock is installed at a water velocity V ₁ = 2m / sec (about 4 knots per hour), and 20000kW
It drives a generator having a capacity of 1 to 2 and will be described with reference to FIGS. 1 and 2. Since maintenance is difficult when installed on the seabed as in the present embodiment, the penstock may be placed near the water surface so that the inside of the penstock can be maintained from inside the barge.

In FIG. 1, reference numeral 1 is a hydraulic tube, and 12 is a jacket tube provided on the outer circumference of the hydraulic tube 1 so as not to disturb the flow of water flow.

In the penstock 1, an inflow port 2 having a cross-sectional area S ₁ (m ² ) is arranged at a water depth H = 30 m at a water velocity V ₁ = 2 m / sec, and an axial flow turbine 6 is arranged near the central portion. and, cross-sectional flow area _S ^{2 (m} 2) water speed the discharge port 3 at a depth H = 30 m of _V 2 =
It is arranged at a position of 2 m / sec, and the water flow cross-sectional areas S ₁ and S are
₂ , the turbine output capacity (kW) = {predetermined flow rate (S ₁ × V ₁₀ )}
X {g x (H + 10.33 m _Aq )} x turbine efficiency-
{(Inflow / outflow loss compensation pressure energy) + {Predetermined flow rate (S ₁ × V ₁₀ )} × ( _Dynamic pressure of water velocity V ₂ ) + (Rear flow maintenance supplemental kinetic energy E _C2K )} ÷ (of artificial energy (S ₁ × predetermined inflow velocity V ₁₀ ) = (S ₂ ×
Predetermined outflow velocity V ₂₀ below water velocity V ₂ ) (m ³ / sec)
= (Predetermined flow rate at which required output is obtained) is set by the following.

In this case, since the required capacity is 20000 kW, the turbine efficiency, the generator efficiency, and (inflow / outflow loss compensation pressure energy) + {predetermined flow rate (S ₁ × V ₁₀ )} ×
In consideration of (dynamic pressure of water velocity V ₂ ) + (replenishment kinetic energy E _C2K for maintaining rear flow rate) and power efficiency of artificial energy, the predetermined flow rate at which the required output is obtained is determined.

By _{adjusting the} flow velocity V _{G1O of the} turbine inflow = predetermined flow rate / the cross sectional area S _{G1O of the} turbine inflow water flow and the inflow / outflow loss compensation pressure, the inflow / outflow loss compensation pressure is completely consumed for the loss compensation in the hydraulic pipe. Therefore, the specific total energy E _FH = 1 × ρ × g × (H + 10.
33 m _Aq (t · m / sec) = 395 kW / m ³ / s
All ec can be converted into kinetic energy. The turbine inflow velocity V _{G1O in} that case is the turbine inflow velocity V _G1O = {2 × g × (30 + 10.33)
m _Aq )} ^1/2 = 28.1 m / sec, which is the maximum flow velocity at a water depth of 30 m obtained from gravity acting on the atmosphere and the water flow.

In the present embodiment, in order to obtain the required capacity of 20000 kW, turbine efficiency: 90%, generator efficiency: 95%, inflow / outflow loss compensation pressure energy: estimated from generally known resistance loss of the penstock 29% of specific total energy of flowing water having a predetermined flow rate passing through the penstock {predetermined flow rate (S ₁ × V ₁₀ )} × (dynamic pressure at water speed V ₂ ):
Specific energy E _FH of flowing water at a predetermined flow rate passing through the _penstock
2 ^{2 /} 28.1 ² × 100 = 0.5% The necessity of this energy: {predetermined flow rate (S ₁ × V ₁₀ )} × (dynamic pressure of water speed V ₂ ) is as follows. In order for the flowing water to flow in the penstock due to gravity acting on the atmosphere and the water flow, the intrinsic total pressure P _FH needs to exist over the entire length of the _penstock . The intrinsic total pressure P _FH acts from the inlet on the upstream side of the axial flow turbine, whereas the intrinsic static pressure PS _SH acts from the drain on the downstream side of the axial flow turbine, and the intrinsic dynamic pressure P _KH = ( The water pressure V ₂ ) is insufficient. Since the dynamic pressure does not flow back from the drainage port, {predetermined flow rate (S ₁ × V ₁₀ )}
× (dynamic pressure of water velocity V ₂ ) is replenished from the upstream side of the axial flow turbine together with inflow / outflow loss compensation pressure energy. Replenished,
Inflow / outflow loss compensation pressure energy and {predetermined flow rate (S ₁ ×
V ₁₀ )} × (dynamic velocity of water velocity V ₂ ) is consumed both at the time of a predetermined flow rate inside the penstock, so it does not affect the water flow outside the penstock, and the upstream side from the outlet of the axial flow turbine Then, it acts separately from the intrinsic total pressure. Replenishment kinetic energy E _C2K for rear flow rate maintenance: The rear reduced water cross-sectional area S _C2O is 1/2 of the water cross-sectional area S ₂ of the drain port 2.
Then, in the case of the largest estimation, the specific energy _EFH of the flowing water at a predetermined flow rate passing through the _penstock is (2 ×
2) ^{2 /} 28.1 ² × 100 = 2% Assuming that the power efficiency of artificial energy is 85%, the specific energy E _FH = 2000 required for flowing water at a predetermined flow rate.
0kW ÷ {0.9 × 0.95- (0.29 + 0.005
+0.02) ÷ 0.85} = 41322kW, and the required flow rate = 41322kW ÷ 395kW / m ³ / sec.
= 104.6 m ³ / sec.

[0045] Therefore, the water passage cross-sectional area _S 1, _{S 2 is, S 1 = S 2 = 104.6m} 3 / sec ÷ 2m 3 / sec
A / ^{m 2} = 52.3m 2.

An inflow part 9 having a water passage whose water passage cross-sectional area is reduced is provided from the inflow port 2.

The entire inflow loss pressure (t / m ² ) generated in the flowing water of the predetermined flow rate of the turbine driving energy E _T system between the inlet 2 and the outlet of the axial turbine 6 and the outlet of the axial turbine 6. The inflow / outflow loss compensation pressure (t / m ² ) for compensating to 0 all the outflow loss pressure (t / m ² ) generated in the flowing water of the predetermined flow rate of the flow maintenance energy E _F system between the drainage ports 3 Generated inflow / outflow loss compensation pressure energy (t · m / sec)
= (S ₁ × V ₁₀ ) × (inflow / outflow loss compensation pressure) and {predetermined flow rate (S ₁ × V ₁₀ )} × (dynamic pressure of water speed V ₂ ) as the water turbine drive energy in the hydraulic pipe 1. the front flow maintains pressure pumping water means 4 for supplying the running water E _T system, provided between the front guide vane section 5 to be described below and the inlet 9. From the above calculation, the required power of the front flow rate maintaining pressurized water feeding means 4 is 41322 kW × 0.29 ÷ 0.85 + 104.
6 × (2 ² /2)÷0.85=14098+246=1
It becomes 4344kW.

The front cylindrical similar space connected to the front flow maintaining pressurized water feeding means 4 and the front cylindrical similar space in the front cylindrical similar space are gradually increased in deflection angle in the circumferential direction. A front guide vane portion 5 including a plurality of front guide vanes that gradually reduces the water passage cross-sectional area of the shape-like space is provided, and the water passage cross-sectional area from the inlet 2 toward the axial water turbine 6 is increased by the flowing water. _{Speed up and} flow velocity of water turbine V _G1O = 28.1 m / se
Turbine inflow cross-sectional area S so as to flow into the axial flow turbine 6 at c
_G1O = 104.6 m ³ /sec÷28.1 m ³ / se
reduced to the c ^/ m ² = 3.72m 2.

Flow velocity V _{G1O of the} turbine is 28.1 m /
By receiving the flowing water that is deflected in the circumferential direction from the front guide vane portion 5 in sec and flowing out, and changing the direction of the water turbine inflow velocity V _G1O = 28.1 m / sec deflected in the circumferential direction in the axial direction, Water turbine inflow velocity V _G1O = 28.1
It is rotationally driven in the circumferential direction with kinetic energy of the circumferential component flow velocity V _TK (m / sec) of m / sec, and the axial component flow velocity of the water turbine inflow velocity V _G1O = 28.1 m / sec,
Alternatively, the turbine outflow velocity V _TO (m / se
In (c), running water is caused to flow out from the outlet of the water flow cross-sectional area S _TO (m ² ), and {(kinetic energy of water wheel inflow velocity V _G1O ) −
(A kinetic energy of the turbine outflow velocity V _TO )} is provided to provide an axial flow turbine 6 having a runner driven by a turbine driving energy E _T.

A generator 11 for transmitting the output of the axial flow turbine 6 to the outside is provided.

The rear cylindrical similar space connected to the outlet of the axial flow water turbine 6 and the upstream cylindrical inlet in the rear cylindrical similar space have the largest deflection angle in the circumferential direction, and the circumferential direction goes to the downstream. A rear guide vane portion 7 composed of a plurality of rear guide vanes for gradually reducing the deflection angle in the direction and gradually increasing the water cross-sectional area of the rear cylindrical similar space is provided, and the axial flow water is supplied from the drain port 3 to the rear guide vane portion 7. The axial flow turbine 6 is deflected in the circumferential direction toward the axial flow turbine 6 while the water flow cross-sectional area up to the vehicle 6 is deflected in the circumferential direction.
The flowing water flowing out from the flow rate maintenance flow velocity V _G2I = 28.
Turbine outflow cross-sectional area S passing at 1 m / sec
_G2I (m ² ) = water turbine inflow cross-sectional area S _G1O = 3.7
Cross-sectional flow area reduced gradually to the 2m ² to connect more cross-sectional flow area S _TO axial outlet of the large axial running water wheel 6 while deflected circumferentially.

Rear reduced water cross-sectional area S _C2O = 52.3 m ² _/2=26.26 , which is connected to the rear guide vane portion 7.
Replenishment kinetic energy E for maintaining the rear flow rate at 2 m ² .
_C2K ≧ [rear flow rate maintenance flow velocity V _C2O = {(S ₂ × V
₂₀ ) / S _C2O } kinetic energy of flowing water at a predetermined flow rate]
× [1-[{(inflow energy E ₁ −turbine drive energy E
_T ) is the rear reduced water flow cross-sectional area S _C2O = 26.2 m ²
Flow velocity V _C2O0 } ² / {inflow energy E ₁ given to the flowing water passing through the rear reduced water flow cross-sectional area S _C2O = 26.
The rear flow rate maintaining pressurized water supply means 8 is provided to supply the rear flow rate maintaining flow velocity V _C2O } ² ]] to the flowing water passing through 2 m ² to the flow water of the flow rate maintaining energy E _F system having the predetermined flow rate. Replenishment kinetic energy E _C2K for rear flow rate maintenance
When the above equation is used, the inflow energy E ₁ and the turbine driving energy E _T are converted into the flow rate (the rear reduced water flow cross-sectional area S in terms of the specific energy per unit time unit flow rate at the water depth H).
_C2O × flow velocity), the ratio between the flow velocity V _C2O0 and the rear flow rate maintenance flow velocity V _C2O is a ratio between (inflow energy E _{1 −turbine} drive energy E _T ) and (inflow energy E ₁ ) and is easily calculated. it can. However, even if the amount exceeding the calculated value is supplied, the predetermined flow rate is determined by the inflow / outflow loss compensation pressure described above, so there is no problem simply by spinning the excess amount, and it is necessary to respond to load fluctuations each time. Therefore, the supplemental kinetic energy E _C2K for maintaining the rear flow rate when the turbine driving energy E _T is maximum is calculated and used. The power required by the rear flow rate maintaining pressurized water feeding means 8 is, as described above,
Rear reduced water flow cross-sectional area S _C2O = 52.3 m ² ÷ 2 = 2
When 6.2 m ² , the rear flow rate maintenance flow velocity V _C2O = {(S
_{Since 2} × V ₂₀ ) / _SC2O } = 4 m / sec,
104.6 × (4 ² /2)÷0.85=984 kW.

An outflow part 10 is provided which is connected to the rear flow rate maintaining pressurized water supply means 8 and whose water passage cross-sectional area is gradually increased.

In summary, the specific energy at a predetermined flow rate of 104.6 m ³ / sec = 41
322 kW Generated power = 41322 kW × 0.9 × 0.95 = 3
5330kW Electric power required for artificial energy supply = 14098 + 246 +
984 = 15328kW Deduction available output = 35330-15328 = 20
It will be 002 kW.

Next, FIG. 2 will be described. In the present embodiment, as described above, the _penstock 1 is shaped according to the constitutional conditions of the present invention, and the rear flow rate maintaining / pressurizing water feeding means 8 supplies the rear flow rate maintaining supplemental kinetic energy E _C2O to the front section. Outflow loss compensating pressure from the flow rate maintaining pressurized water feeding means 4 and outflow that is necessary between the axial flow turbine 6 and the rear flow rate maintaining pressurized water feeding means 8 but cannot be supplied retroactively from the rear flow rate maintaining pressurized water feeding means 8. The loss compensating pressure and the dynamic pressure of the water velocity V ₂ are supplied by setting the amount consumed up to the drain port in order to maintain a predetermined flow rate of the flowing water in the penstock 1 and to compensate the loss. Therefore, in the penstock 1, it is possible to drive the axial flow turbine by flowing a predetermined flow rate of flowing water at a desired flow velocity, but since the predetermined flow rate is matched with the flow rate of the water flow, the above-mentioned artificial energy supply and the axial flow turbine The drive of a has no effect on the water flow outside the penstock. Therefore, in FIG. 2, the total pressure in the penstock 1 is the intrinsic total pressure P
_FH = ρ × g × (H + 10.33) = H + 10.33
And total artificial pressure P = (compensation pressure for inflow / outflow loss + water velocity V ₂
Dynamic pressure) and the front flow rate maintaining pressure water supply means 4
From the downstream side to the downstream side, the intrinsic total pressure P _FH + man-made total pressure P is always large on the upstream side and becomes the intrinsic total pressure P _FH at the drainage port 3. As a result, the predetermined flow rate is maintained. The dynamic pressure is determined by the flow rate fixed by the predetermined flow rate and the cross-sectional area of water flow, and is only the specific dynamic pressure. The static pressure is the sum of the intrinsic static pressure P _SH and the pressure artificially supplied = (inflow / outflow loss compensation pressure + dynamic pressure of water velocity V ₂ ).

When the flow of the fluid is wind, if the specific energy of the circulating air in the wind pressure tube is converted into 100% kinetic energy, it becomes about 410 m / sec, which is difficult to carry out due to the air compression phenomenon. . Therefore, the wind turbine inflow velocity V
_G1O has a technically _processable flow rate, for example, 10
It is sufficient to set 0 to 200 m / sec, gain experience, and then adopt the fast wind turbine inflow velocity V _G1O .

Further, in the present embodiment, since it is sufficient that the distribution of total pressure has the gradient shown in FIG. 2, as shown in claim 5,
Turbine inflow water flow cross-sectional area S _G1O
And greater than _G2i, the waterwheel inlet flow velocity _{V G1o} Chisashi than the flow rate maintained velocity _{V G2i,} and dynamic pressure of the hydraulic turbine inlet flow velocity _{V G1o,} when utilizing the difference between the dynamic pressure of the flow maintaining the flow velocity _{V G2i,} (inflow and outflow It is possible to cover a part of the loss compensation pressure + the dynamic pressure of the water velocity V ₂ .

Further, in this embodiment, when the turbine load changes or the water speed changes, in order to keep the rotation speed of the turbine constant, the turbine inflow velocity V _G1O and the flow maintenance velocity V _{G2I are} maintained. Since it suffices to maintain and at a predetermined value, the predetermined flow rate, human energy inflow / outflow loss compensation pressure and water velocity V _2
Dynamic pressure and supplemental kinetic energy E _C2O for maintaining the rear flow rate,
Turbine inflow cross section S _G1O and turbine outflow cross section S
_G2I is adjusted to maintain the turbine inflow velocity V _G1O and the flow rate maintenance velocity V _G2I at predetermined values.

Further, in the present embodiment, if a speed governor is added to the output side of the axial flow turbine, mechanical operation of changing the water passage cross-section is not performed when the water speed decreases, and electrical operation is performed. Only by doing so, it is possible to maintain the rotation speed of the water turbine at a constant value. That is, the predetermined flow rate, the inflow / outflow loss compensation pressure of the artificial energy, the dynamic pressure of the water speed V _{2 and} the supplemental kinetic energy E _C2O for maintaining the rear flow rate are adjusted according to the reduced water speed, and the reduced predetermined flow rate is obtained. The reduced rotational speed of the axial flow turbine using the reduced turbine inflow velocity V _G1O and the flow maintenance velocity V _G2I determined by the fixed turbine inflow cross sectional area S _G1O and the fixed turbine outflow sectional area S _G2I. Is increased to a predetermined value by the speed governor.

Further, in this embodiment, since the rear outflow loss energy generated between the rear flow rate maintaining pressure water supply means 8 and the drainage port can be supplied from the rear flow rate maintaining pressure water supply means 8, the front flow rate maintaining pressure supply water is transmitted. The rear outflow loss energy supplied from the water means 4 can be transferred to the supply from the rear flow rate maintaining pressurized water supply means 8.

As a second embodiment, above water, in water, or
A case where the first invention of the present application is applied to a moving object in the atmosphere will be described. FIG. 3 shows, as a representative, a case where the first invention of the present application is carried out on an underwater ship, and the penstock 1 may be provided on the underwater ship 20. In principle, the description is omitted because it is the same as the first embodiment. As moving objects, bicycles, cars, trains, trains,
There are water-based vessels, underwater vessels, and the like. In the case of an underwater vessel, the water depth H can be increased, so that a large output can be obtained.

As a third embodiment, the second invention of the present application will be described with reference to FIG. In FIG. 4, ADE
The gradient water channel 31 which is an open water channel between B and the water flow at the low water level end B of the gradient water channel 31 is pumped by the water pumping means 32 so that the gradient water channel 3
The high water level end A of 1 is provided with a circulation water channel having a circulation / condensation channel 33, which is a channel between BCAs for circulation / condensation, and the water pressure tube 1 is installed in the gradient water channel 31. The change in the water velocity of the gradient waterway 31 is changed between the AD of the gradient waterway 31 and the DE
The gradient between EB and EB, the amount of circulation / condensation by pumping of the pumping means 32 is adjusted so that the water speed becomes substantially constant over the entire length of the gradient channel 31. The action of gravity on the water flow, the water velocity V _H (m / sec) at the water depth H (m), and the resistance to each part of the water flow acting on each part of the water flow are balanced with the water depth H.
At the water depth V, the inherent total pressure P _FH of the water flow at the water depth H based on the bias of the pressure on the air and the water flow maintaining the water velocity V _H due to the action of gravity in the flow direction and the action of gravity on the atmosphere and the water flow. = Specific static pressure P _SH + Specific dynamic pressure P _KH = [ρ ×
g × (H + 10.33m _Aq ) − {ρ × (V _H ) ² ÷
2}] + {ρ × (V _H ) ² ÷ 2} = ρ × g × (H + 1
0.33 m _Aq ) (t / m ² ) and a unit time unit flow rate 1 (m ³ / based on the action of gravity on the atmosphere and water flow)
specific energy E of the water flow at the water depth H per sec)
_FH = (the unique static _P specific pressure energy corresponding to the _{SH E} PH) + (the inherent dynamic pressure _P inherent kinetic energy corresponding to ^{_{KH E KH) = 1 (m}} 3 / sec) × [ρ × g ×
_{(H + 10.33m Aq) - {} ρ × (V H) 2 ÷ 2}]
(T / m ² ) +1 (m ³ / sec) × {ρ × (V _H ) ²
÷ 2} (t / m ² ) = 1 × ρ × g × (H + 10.33 m
_Aq ) (t · m / sec).
In the case of one, as described above, the circulation water channel is the gradient water channel 31.
Is disposed above and the circulation / condensation channel 33 is disposed below, it is difficult for dead points at which water flow is retained at both ends of the gradient water channel 31 to occur, and at the low water level end B of the gradient water channel 31, inside the gradient water channel 31. Near the water surface of the river and the slope channel 3
The bias in the flow direction of the action of gravity on the water flow near the bottom surface in 1 becomes a force corresponding to each water depth, and the difference in water speed from the water surface to the bottom surface of the sloped water channel 31 becomes small, and the present invention is achieved. It is rational in forming the above flow necessary.

As a fourth embodiment, the third invention of the present application will be described with reference to FIG. 4, the pressure tube 1 was placed straddling the water level difference H _D between the upstream side and the downstream side of the submerged orifice 40 provided in the water flow _(m), the water level difference H _D, water turbine driving energy E _T or / and used as all or part of the inflow / outflow loss compensating pressure to adjust the turbine inflow water cross-section S _G1O and the turbine outflow water cross-section S _G2I to S running water waterwheel inlet static pressure _{P STI} passing _G1o) - (running water waterwheel flow outlet static pressure P passing through the water turbine outlet water passage cross-sectional area _{S G2i
STO} = Inflow / outflow loss compensation pressure.

As a fifth embodiment, the third invention of the present application will be described with reference to FIG. 5, the pressure tube 1 is placed astride between the water level difference _H D (m) 2 two water flow _F 1 there is, _{F 2} between the water surface. In this case, penstock 1
The part having the action of the first invention of the present application is the lower water flow F ₂
It is placed inside at a position of water depth H (m), and its inflow port 2 and the upper water flow F ₁ are connected by an extension pipe 1a having an equal diameter. Then, the water level difference H _D, used as all or part of the water wheel drive energy E _T or / and the inflow and outflow loss compensation pressure, water turbine inlet water passage cross-sectional area S _G1o and waterwheel outlet water passage cross-sectional area S _G2i
Adjust the bets, (waterwheel inlet static pressure P _STI of flowing water passing through the water turbine inlet water passage cross-sectional area S _{G1o) -} (running water waterwheel flow outlet static pressure passing through the water turbine outlet water passage cross-sectional area S _{G2i PSTO} ) = inflow / outflow loss compensation pressure.

[0065]

INDUSTRIAL APPLICABILITY The method and apparatus for converting gravity acting on a fluid flow into kinetic energy according to the present invention can be used for moving in various water streams, in the wind, or in moving bodies in water or water, or in the atmosphere. In the body etc., correct the theory error for the energy of the fluid flow in the conventional fluid mechanics, and based on the corrected theory, adjust the shape of the water pressure pipe and wind pressure pipe to the constituent requirements and supply three small artificial energy As a result, there is an effect that a third-class permanent motion engine that converts gravity acting on the flow of fluid into kinetic energy can be realized. Therefore,
This has an effect of solving an energy problem which will be a problem in the future.

[Brief description of drawings]

FIG. 1 is a side view showing a configuration of a first embodiment using the present invention.

FIG. 2 is a diagram showing total pressure, static pressure, and dynamic pressure of the present invention.

FIG. 3 is a side view showing a configuration of a second embodiment using the present invention.

FIG. 4 is a side view showing a configuration of a third embodiment using the present invention.

FIG. 5 is a side view showing the configuration of a fourth embodiment using the present invention.

FIG. 6 is a side view showing a configuration of a fifth embodiment using the present invention.

[Explanation of symbols]

 1 water pressure pipe 1a extension pipe 2 inflow port 3 drainage port 4 front flow rate maintaining pressurized water supply means 5 all guide vane section 6 axial flow turbine 7 rear guide vane section 8 rear flow maintaining pressurized water supply section 9 inflow section 10 outflow section 11 Generator 12 Outer tube 20 Underwater vessel 31 Gradient water channel 32 Pumping means 33 Circulation / condensation channel 40 Mug orifice

Claims (11)

[Claims] 1. The effect of gravity on the atmosphere and the water flow, the water velocity V H (m / sec) at the water depth H (m), and the resistance to each part of the water flow that acts on each part of the water flow and the water depth H is balanced.
At the water depth V, the inherent total pressure P FH of the water flow at the water depth H based on the bias of the pressure on the air and the water flow maintaining the water velocity V H due to the action of gravity in the flow direction and the action of gravity on the atmosphere and the water flow. = Specific static pressure P SH + Specific dynamic pressure P KH = [ρ ×
g × (H + 10.33m Aq ) − {ρ × (V H ) 2 ÷
2}] + {ρ × (V H ) 2 ÷ 2} = ρ × g × (H + 1
0.33 m Aq ) (t / m 2 ) and a unit time unit flow rate 1 (m 3 / based on the action of gravity on the atmosphere and water flow)
specific energy E of the water flow at the water depth H per sec)
FH = (the unique static P specific pressure energy corresponding to the SH E PH) + (the inherent dynamic pressure P inherent kinetic energy corresponding to KH E KH) = 1 (m 3 / sec) × [ρ × g ×
(H + 10.33m Aq) - { ρ × (V H) 2 ÷ 2}]
(T / m 2 ) +1 (m 3 / sec) × {ρ × (V H ) 2
÷ 2} (t / m 2 ) = 1 × ρ × g × (H + 10.33 m
Aq ) (t · m / sec) in a water stream that circulates on a global scale such as a sea current or a tidal current, in a water stream that flows by a gradient such as a river or an open channel, or relative to water In the moving body above or underwater, the force for maintaining the motion and the relative velocity with water can be treated as the bias of pressure due to the action of gravity in the flow direction of the atmosphere and the water flow and the moving body on or under water as the water velocity V H. The water velocity V 1 (m / se) is set at the inlet of the area S 1 (m 2 ).
c) Arbitrary water depth H 1 (m), the axial flow turbine provided near the central portion is arranged at the water depth H, and the water flow cross-sectional area S
A drainage port of 2 (m 2 ) is arranged at the water depth H of water velocity V 2 (m / sec) or a deeper water depth H 2 (m), and a water pressure difference between the axial flow turbine and the inflow port, Water pressure difference between the axial flow turbine and the drainage port, gravity acting on the running water in the penstock between the axial flow turbine and the inlet, respectively, and running water in the penstock between the axial flow turbine and the drainage port. Installed in the water flow or in the moving body, which is counteracted by gravity acting on, and the effective water depth of the inflow port and the drain port with respect to the axial flow turbine becomes the same water depth H as the axial flow turbine. Based on the equation of the turbine output capacity described later, the water flow cross-sections S 1 and S 2 are calculated as (S 1 × predetermined inflow velocity V 10 ) = (S 2 ×
Predetermined outflow velocity V 20 below water velocity V 2 ) (m 3 / sec)
= (Predetermined flow rate at which the required output is obtained), and the cross sectional area of water flowing from the inflow port toward the axial flow turbine is increased by the flowing water and the turbine inflow velocity V G1O (m / s
ec) is reduced to a turbine inflow water cross sectional area S G1O (m 2 ) so as to flow into the axial water turbine, and the water cross sectional area from the drain port to the axial water turbine is set to the axial water turbine. The flowing water flowing out of the axial flowing water turbine while being deflected in the circumferential direction passes through at a flow rate maintaining flow velocity V G2I (m / sec). The water turbine outflow cross-sectional area S G2I (m 2 ) = the water turbine inflow communication By gradually reducing the water cross-sectional area S G1O and connecting it to the axial outlet of the axial flow turbine having a larger water cross-sectional area in the state of being circumferentially deflected, the axial flow turbine is unloaded. Yes As will be described later, the inflow / outflow loss compensation pressure artificially supplied and the dynamic pressure of the water velocity V 2 balance with the resistance to the running water to maintain a predetermined flow rate described later, or the axial water turbine is present. It is a load and is artificially supplied as described below. The inflow / outflow loss compensating pressure and the dynamic pressure of the water velocity V 2 are balanced with the resistance to running water to maintain a predetermined flow rate described below, and further, supplemental kinetic energy for artificially supplying the rear flow rate as described below. E C2K
Is but in a state that supplemented with consumption of water turbine driving energy E T described later, running water and accelerated with the reduction of the cross-sectional flow area to flow into the shaft running water wheel, flowing water having passed through the shaft running water wheel The specific static pressure P of each part of the hydraulic pipe based on the effect of gravity on the atmosphere and the water flow is discharged from the drain port while decelerating with the increase of the cross-sectional area of water flow, and with the acceleration and deceleration of these. The SH symmetrically reduces the pressure from both the inlet and the drain toward the axial flow turbine, so that the action of gravity on the atmosphere and the water flow outside the inlet causes the flowing water in the penstock to move as described above. The specific energy E FH = 1 × ρ × g × (H + 10.
33m Aq ), the intrinsic total pressure P FH = ρ × g ×
(H + 10.33 m Aq ), which acts from the inlet to the outlet of the axial flow turbine, and the action of gravity on the atmosphere and the water flow outside the drainage outlet causes the flowing water in the penstock to pass through the above-mentioned unit time unit flow rate 1 The specific energy E FH at the water depth H per hit = 1 × ρ × g × (H + 10.33 m
Aq ) (the specific static pressure P SH ) / (the specific total pressure P
FH ) drainage port static pressure P S2 = the specific total pressure P FH at the drainage port-the specific dynamic pressure P KH at the drainage port = the specific total pressure P FH at the drainage port-water velocity V 2 Dynamic pressure = [{ρ × g
× (H + 10.33m Aq )}-{ρ × (V 2 ) 2 ÷
As 2}], leave as dating back from the water outlet to the outlet of the shaft running water vehicle, flows occurring in flowing water of the predetermined flow rate of the water turbine drive energy E T system between the inlet and the axis running water car outlet and all of the loss pressure (t / m 2), all of the outflow losses pressure generated flowing water of the predetermined flow rate maintained energy E F system between said shaft running water vehicle exit the water outlet (t / m 2) Inflow / outflow loss compensation pressure energy (t · m / sec) that generates inflow / outflow loss compensation pressure (t / m 2 ) that compensates and
(S 1 × V 10 ) × (compensation pressure for inflow / outflow loss) and (predetermined flow rate) × (dynamic pressure at the water velocity V 2 ) are defined as the gravity of the atmosphere and the water flow in the natural water flow. the pressure bias due to the action of the flow direction, and the unique total pressure P FH and as corresponding to the difference between the distribution Mizuguchi static pressure P S2, artificially flowing water of the water turbine drive energy E T system of the hydraulic tube Is supplied to balance the resistance of the penstock to the flowing water of the predetermined flow rate, compensates the outflow loss pressure generated in the flowing water of the flow rate maintaining energy E F system from the upstream side, and the intrinsic total pressure P FH and Water outlet static pressure P S2
By compensating for the difference from the upstream side of the flow rate maintained energy E F for generating in the form of change places with consumption of water turbine driving energy E T described later to the flowing water of the flow rate maintained energy E F system as described later, the maintaining the predetermined flow back in the flowing water flow maintaining the energy E F system with change places the form on the consumption of the water turbine drive energy E T below to said axis running water wheel, acting the flow velocity of the penstock each portion with the atmosphere and water Inherent water velocity V (m / sec) based on gravitational force = (the predetermined flow rate S 1 ×
V 10 ) / (water passage cross-sectional area of each part), and the water depth H
Per unit time unit flow rate of each part in the penstock located at
Similar to the natural water flow, the flowing water is the specific energy E FH (t · m / sec) = (at the specific static pressure P SH at the water depth H based on the action of gravity on the atmosphere and the water flow described above. corresponding unique pressure energy E PH) + (specific kinetic energy E KH corresponding to the unique dynamic pressure P KH) =
1 × [ρ × g × ( H + 10.33m Aq - {ρ ×
(V H ) 2 ÷ 2}] + 1 × {ρ × (V H ) 2 ÷ 2} = 1
And that to have a × ρ × g × (H + 10.33m Aq), said shaft regardless of whether the load of the flowing water wheel, the flowing water of the flow rate maintained energy E F system, the outflow energy E 2 (t · m /
sec) = (S 2 × V 20 ) × [the specific energy E of the water flow per unit time unit flow rate at the water depth H]
FH {1 × ρ × g × (H + 10.33m Aq )}] exists, the action of gravity on the atmosphere and the water flow at the drain, and the flow direction of gravity on the atmosphere and the water flow outside the drain. Deviation due to the action on the water flow and the specific energy E FH = 1 × ρ × g × (H + 10.33 m of the water flow per unit time unit flow rate at the water depth H.
And Aq), and the water outlet static pressure P S2 is sucked out flowing water of the flow rate maintained energy E F system from the drain outlet of said predetermined flow rate as an upper limit in water of the water outlet static pressure P S2, change the water flow By having a flow rate maintaining action that allows the water to flow away without leaving, the inflow energy E can be obtained when the axial flow turbine has no load.
1 (t · m / sec) = (predetermined flow rate S 1 × V 10 ).
× [The specific energy E FH of the water flow per unit time unit flow rate 1 at the water depth H {1 × ρ × g × (H + 1
0.33 m Aq )}] = The outflow energy E 2 is passed through the penstock together with the predetermined amount of flowing water flowing in from the inflow port and flowing out from the drainage port, and the loaded axial flow turbine is , Turbine drive energy E
T = {the water turbine inlet flow velocity V running water kinetic energy of the water wheel drive energy E T system at a predetermined flow rate of G1o} - {waterwheel outlet flow velocity V TO (m / se in the axial direction of the outlet of the shaft running water wheel
When consuming the flowing water of the kinetic energy of the water wheel drive energy E T system at a predetermined flow rate of c)} it is located at any position between the drain port and the axis running water car outlet, at the depth H of the above The specific energy E FH = 1
× ρ × g × (H + 10.33m Aq ) and the intrinsic total pressure P
FH = ρ × g × (H + 10.33m Aq ) and the drain port static pressure P S2 traced back as described above and the dynamic pressure of the water speed V 2 supplied from the upstream side as described above are The acting water flow cross-sectional area is the water turbine outflow water flow cross-sectional area S G2I
By being n times the required rear flow maintaining the flow velocity V C2O of 1 / n of the specific energy E FH running water in the water depth H of the unit time unit passing flow per the aforementioned the flow maintaining the flow velocity V G2i Rear reduced cross-sectional water flow area S obtained in
In C2O , supplemental kinetic energy E for maintaining the rear flow rate
C2O ≧ [rear flow rate maintenance flow velocity V C2O = {(S 2 × V
20 ) / S C2O } kinetic energy of flowing water at a predetermined flow rate]
× [1-[{(the inflow energy E 1 −the water turbine drive energy E T ) gives the flow velocity V C2O0 } 2 / {the inflow energy E 1 to the running water passing through the rear reduced water passage sectional area S C2O] The rear flow rate maintaining flow velocity V C2O } 2 ] given to the flowing water passing through the rear reduced water flow cross-sectional area S C2O ]]
Is the kinetic energy of the turbine outflow velocity V TO and the outflow loss compensation pressure (predetermined flow rate) × (dynamic pressure of the water velocity V 2 ).
Are supplied from the upstream side and are artificially supplied to the flowing water of the flow rate maintaining energy E F system of the predetermined flow rate that receives the static pressure P S2 of the water outlet and the flow rate maintaining action by the water flow outside the drain port, by maintaining the flow velocity in the rear reduced water passage cross-sectional area S C2O to said rear flow maintaining the flow velocity V C2O, the flow rate maintained energy E F = the water turbine driving energy E T in a form change places with consumption of the water turbine drive energy E T The specific energy E FH at the water depth H per unit time unit flow rate 1 is added to the flowing water of the flow rate maintaining energy E F system in the penstock at the water depth H, which is generated and traces back to the axial flow turbine. = 1 × ρ × g × (H + 10.33m
The outflow energy E 2 = (S 2 ×) based on Aq )
V 20 ) × [the specific energy E at the water depth H
FH {1 × ρ × g × (H + 10.33m Aq )}] is maintained, and the inside of the axial flow turbine is rotated while the runner is rotated in the circumferential direction to the running water of the predetermined flow rate over the entire length of the penstock. Including the existing turbine drive energy E T , which is present in the air, the inflow energy E based on the action of gravity on the atmosphere and the water flow.
1 = The outflow energy E 2 and the inherent total pressure P FH = ρ × g × (H + 10.33 m Aq ) at the water depth H, and the artificial total pressure P due to the artificial energy for maintaining the flow velocity in balance with the resistance = {(The inflow / outflow loss compensation pressure)-
(Loss pressure)} is added to the intrinsic total pressure P FH to determine the total flow pressure P F = (intrinsic total pressure P FH + manual total pressure P) from the inlet to the drain outlet. It dropped to the drain outlet static pressure P S2 while maintaining the flow rate maintained action flow of the waste water extraoral has found the flow maintaining energy E F system of the predetermined flow rate with the outflow energy E 2 in the pressure pipe Of the flowing water is sucked into the water flow of the drain outlet static pressure P S2 from the drain at the predetermined outflow velocity V 20 and is allowed to flow away without changing the water flow, and the flow rate of the flowing water in the penstock is set to the above. by stabilizing the predetermined flow rate, supplied with three small artificial energy as described above, it is converted into a large the water turbine driving energy E T of gravity acting on the flow of fluid and the flow rate maintained energy E F The above A class 3 permanent motion engine that drives an axial water turbine to maintain the predetermined flow rate of the flowing water in the penstock is realized, and the turbine output capacity (kW) = {predetermined flow rate (S 1 × V 10 )}.
X {g x (H + 10.33 m Aq )} x turbine efficiency-
{(Inflow / outflow loss compensation pressure energy) + {Predetermined flow rate (S 1 × V 10 )} × ( Dynamic pressure of water velocity V 2 ) + (Replacement kinetic energy for rear flow rate maintenance E C2K )} ÷ (of artificial energy A method of converting gravitational force acting on a fluid flow into kinetic energy, which is characterized by obtaining electric power efficiency. 2. The method for converting gravity acting on a fluid flow into kinetic energy according to claim 1, wherein a gradient water channel and a water flow at a low water level end of the gradient water channel are pumped by a water pumping means. Circulation at high water level
A circulating water channel having a condensate channel is provided, a water pressure pipe is installed in the gradient water channel, and a change in the water velocity of the gradient water channel due to the installation of the water pressure pipe is canceled by adjusting the gradient distribution of the gradient water channel. The amount of circulation / condensation by pumping of the pumping means is adjusted so that the water velocity becomes substantially constant over the entire length of the gradient channel, and the gradient channel has the effect of gravity on the atmosphere and the water flow and the water depth H (m). Water speed V H (m / se
c), a pressure bias due to the action of gravity in the flow direction on the atmosphere and the atmosphere that acts on each part of the water stream and balances the resistance to each part of the water stream and maintains the water velocity V H at the water depth H; Inherent total pressure P FH of water flow at the depth H based on the action of gravity on the water flow and intrinsic static pressure P SH + intrinsic dynamic pressure P KH = [ρ × g × (H + 10.33 m Aq ) −
{Ρ × (V H ) 2 ÷ 2}] + {ρ × (V H ) 2 ÷ 2} =
ρ × g × (H + 10.33m Aq ) (t / m 2 ) and the characteristic of the water flow at the water depth H per unit time unit flow rate 1 (m 3 / sec) based on the action of gravity on the atmosphere and the water flow energy E FH = (specific kinetic energy E KH corresponding to the unique dynamic pressure P KH) + (the unique static P specific pressure energy E PH corresponding to the SH) = 1 (m 3 / se
c) × [ρ × g × (H + 10.33m Aq ) − {ρ ×
(V H ) 2 ÷ 2}] (t / m 2 ) +1 (m 3 / sec)
× {ρ × (V H ) 2 ÷ 2} (t / m 2 ) = 1 × ρ × g ×
A method for converting gravity acting on a fluid flow into kinetic energy, which comprises forming a water flow having (H + 10.33 m Aq ) (t · m / sec). 3. The method for converting gravity acting on a fluid flow into kinetic energy according to claim 1, wherein the penstock extends over a difference in water level between an upstream side and a downstream side of a muzzle orifice provided in the water flow. Or, there is a water level difference between the water surfaces 2
One of the installed straddling between water flow, the water level difference, used as all or part of the water wheel drive energy E T or / and the inflow and outflow loss compensation pressure, water turbine inlet water passage cross-sectional area S G1o and waterwheel outlet flowing water passing through (the waterwheel outlet water passage cross-sectional area S G2i - by adjusting the cross-sectional flow area S G2i, (running water waterwheel inlet static pressure P STI passing through the water turbine inlet water passage cross-sectional area S G1o) Water turbine outlet static pressure PSTO ) = inflow / outflow loss compensation pressure + dynamic pressure of water velocity V 2 A method of converting gravity acting on a fluid flow into kinetic energy. 4. The effect of gravity on the atmosphere and the wind speed V
H (m / sec) is balanced with resistance to movement of each part of the atmosphere and movement of each part of the atmosphere, and the bias of pressure in the direction of the wind accompanied by the action of gravity on the atmosphere maintaining the wind speed V H , and the gravity on the atmosphere. The inherent total pressure P FH of the wind at the wind speed V H based on the action of the following: intrinsic static pressure P SH + intrinsic dynamic pressure P KH =
[Ρ × g × 10.33 m Aq − {ρ A × (V H ) 2 ÷
2}] + {ρ A × (V H ) 2 ÷ 2} = ρ × g × 10.3.
3 m Aq (t / m 2 ) and the specific energy E FH of the wind at the wind speed V H per unit time unit passing flow rate 1 (m 3 / sec) based on the effect of gravity on the atmosphere E FH = (the specific static pressure P SH specific pressure energy E PH) corresponding to + (the unique dynamic pressure P KH corresponding to the unique kinetic energy E KH) =
1 (m 3 /sec)×[ρ×g×10.33 m Aq −
{Ρ A × (V H ) 2 ÷ 2}] (t / m 2 ) +1 (m 3 /
sec) × {ρ A × (V H ) 2 ÷ 2} (t / m 2 ) = 1
Xρ × g × 10.33 m Aq (t · m / sec) in the wind or the force for maintaining the relative motion with the atmosphere and the relative velocity with the atmosphere are the effects of gravity on the atmosphere. In the moving body in the atmosphere that can be treated as the wind velocity V H accompanied by the deviation of the pressure in the wind direction, the inlet of the ventilation cross-sectional area S 1 (m 2 ) is introduced into the wind velocity V 1 (m / se).
c), an axial wind turbine near the center, and an exhaust port with a ventilation cross-sectional area S 2 (m 2 ) of wind speed V 2 (m / sec).
The wind cross section S 1 corrected by the change of ρ A due to the flow velocity by installing the wind pressure pipe at the position
S 2 is calculated by (S 1 ×
The predetermined inflow velocity V 10 ) = (S 2 × predetermined outflow velocity V 20 equal to or less than the wind velocity V 2 ) (m 3 / sec) = (predetermined flow rate at which required output is obtained), and from the inflow port The ventilation cross-section area S G1O (m) is set so that the circulating air is accelerated to flow into the axial flow turbine at a wind turbine inflow velocity V G1O (m / sec).
2 ) to reduce the ventilation cross-sectional area from the exhaust port to the axial flow wind turbine in the circumferential direction toward the axial flow wind turbine while maintaining the flow rate of the circulating air flowing out from the axial flow wind turbine. Wind turbine outflow ventilation cross-sectional area S G2I (m 2 ) that passes at a flow velocity V G2I (m / sec) = the wind turbine inflow ventilation cross-sectional area S G1O is gradually reduced to a larger ventilation cross-sectional area. By connecting to the outlet in the circumferential direction in a state of being deflected in the circumferential direction, the axial flow wind turbine has no load, and the inflow / outflow loss compensation pressure and the dynamic pressure of the wind speed V 2 artificially supplied as described later. Is in a state of maintaining a predetermined flow rate described later in balance with the resistance to the circulating air, or the inflow / outflow loss compensation pressure and the wind speed V 2 of the axial flow wind turbine with a load and being artificially supplied as described later. Dynamic pressure in circulating air Resistance commensurate with maintaining a predetermined flow rate will be described later, further, the state artificially supplied rear flow maintained refill kinetic energy E C2K as described below is supplemented with consumption of the wind turbine drive energy E T below Then, the circulating air is accelerated with a decrease in the ventilation cross-sectional area and flows into the axial wind turbine, and the circulating air passing through the axial wind turbine is decelerated with the increase in the ventilation cross-sectional area from the exhaust port. Outflowing, and as these speeds up and slow down, the intrinsic static pressure P SH of each part of the wind pressure pipe based on the action of gravity on the atmosphere is directed toward the axial wind turbine from both the inlet and the exhaust port. By symmetrically reducing the pressure, the action of gravity on the atmosphere outside the inflow port causes the specific energy E FH = 1 × ρ × g × 10 per unit time unit flow rate of the circulating air in the wind pressure tube. .33m Aq As the intrinsic total pressure P FH = ρ × g × 10.33 m Aq , which acts from the inlet to the outlet of the axial flow wind turbine, and the action of gravity on the atmosphere outside the drainage outlet causes the flow in the wind pressure pipe. Exhaust that constitutes the (specific static pressure P SH ) / (the specific total pressure P FH ) of the specific energy E FH = 1 × ρ × g × 10.33 m Aq per one unit time unit flow rate of the air Mouth static pressure P S2 = the above-mentioned specific total pressure P FH − at the exhaust port
The intrinsic dynamic pressure P KH at the exhaust port = the intrinsic total pressure P FH at the exhaust port−the dynamic pressure of the wind speed V 2 = [{ρ × g × 10.33 m
Aq }-{ρ A × (V 2 ) 2 ÷ 2}] so as to trace back from the exhaust port to the outlet of the axial wind turbine, and the wind turbine drive energy between the inlet and the outlet of the axial wind turbine. and all of the inflow loss pressure (t / m 2) generated in the circulated air of the predetermined flow rate of the E T system, distribution of the predetermined flow rate maintained energy E F system between the outlet and the exhaust port of the axial flow wind turbine The total outflow loss pressure (t / m 2 ) generated in the air is set to 0
Inflow / outflow loss compensation pressure energy (t · m / se) to generate inflow / outflow loss compensation pressure (t / m 2 )
c) = (S 1 × V 10 ) × (inflow / outflow loss compensation pressure), and (the predetermined flow rate) × (the dynamic pressure of the wind speed V 2 ), the action of gravity on the atmosphere in the natural wind. the associated pressure deviation in the direction of the wind, and the specific total pressure P FH and as corresponding to the difference between the exhaust port static pressure P S2, distribution air in the wind turbine drive energy E T system of the wind pressure pipe artificially supplied to the predetermined flow rate the flow rate maintained to compensate the outflow losses pressure generated in the distribution air energy E F system from the upstream side and the specific total pressure with balancing the resistance of the wind pressure pipe for circulation of air By compensating for the difference between P FH and the exhaust port static pressure P S2 from the upstream side,
Flow rate maintained energy E F to be generated by the consumed change places the form of the flow rate maintained energy E F based wind turbine drive energy E T below the distribution of air as described later, the flow rate maintained energy E F system flow within the air Wind turbine drive energy E described later
The predetermined flow rate is maintained by going back to the axial-flow wind turbine in a manner that replaces the consumption of T , and the flow velocity of each part of the wind pressure tube is set to a specific water speed V (m / sec) = (the predetermined flow rate S 1 × V 10 ) / (aeration cross-sectional area of each part corrected for changes in ρ A due to flow velocity), and the circulating air per unit time unit passing flow rate 1 of each part in the wind pressure tube is the same as the natural wind, The specific energy E FH (tm · sec) = (specific pressure energy E PH corresponding to the specific static pressure P SH ) based on the action of gravity on the atmosphere described above +
(Natural kinetic energy E corresponding to the above-mentioned intrinsic dynamic pressure P KH
KH ) = 1 × [ρ × g × 10.33 m Aq − {ρ A ×
(V H ) 2 ÷ 2}] + 1 × {ρ A × (V H ) 2 ÷ 2} =
And that to have a 1 × ρ × g × 10.33m Aq , regardless of whether the load of the axial flow wind turbine, the flow of air the flow rate maintained energy E F system, the outflow energy E 2 (t ·
m / sec) = (S 2 × V 20 ) × [the specific energy E FH of the wind per unit time unit flow rate at atmospheric pressure]
{1 × ρ × g × 10.33 m Aq }] exists, the bias of the pressure in the direction of the wind accompanied by the action of gravity on the atmosphere at the exhaust port and the action of gravity on the atmosphere outside the exhaust port. And the specific energy E FH of the wind per unit flow rate per unit time at atmospheric pressure E FH = 1 × ρ × g × 1
0.33 m Aq and the exhaust port static pressure P S2 suck the circulating air of the flow rate maintenance energy E F system into the wind of the exhaust port static pressure P S2 from the exhaust port with the predetermined flow rate as the upper limit. In addition, when the axial-flow wind turbine has no load, the inflow energy E has the effect of maintaining the flow rate that allows the wind to flow away without leaving any change.
1 (t · m / sec) = (predetermined flow rate S 1 × V 10 ).
× [The above-mentioned specific energy E FH of wind per unit time unit passing flow rate at atmospheric pressure E FH {1 × ρ × g10.33
m Aq }] = The outflow energy E 2 is passed through the wind pressure pipe together with the predetermined amount of circulating air flowing in from the inflow port and flowing out from the exhaust port, and the loaded axial flow wind turbine is a wind turbine. Drive energy E
T = {Windmill inflow velocity V G1O of a predetermined flow rate of wind turbine drive energy E T Kinetic energy of the circulating air of the system}-{Windmill outflow velocity V TO (m / s at the axial outlet of the axial wind turbine)
ec) when the wind turbine driving energy E T system kinetic energy of the circulating air of a predetermined flow rate} is consumed, it is located at an arbitrary position between the outlet of the axial wind turbine and the exhaust port, and at the above-mentioned atmospheric pressure. The characteristic energy of the wind E FH = 1
× ρ × g × 10.33 m Aq and the intrinsic total pressure P FH = ρ
Xg × 10.33 m Aq is defined by the exhaust port static pressure P S2 traced as described above and the ventilation cross-sectional area on which the dynamic pressure of the wind speed V 2 supplied from the upstream side acts as described above. Since the wind turbine outflow ventilation cross-sectional area S G2I is n times, the necessary specific energy E FH of the circulating air per unit time unit passing flow rate 1 is the rear flow rate of 1 / n of the flow rate maintaining flow rate V G2I. In the rear reduced ventilation cross-sectional area S C2O obtained with the maintenance flow velocity V C2O , the supplemental kinetic energy for maintaining the rear flow amount E C2K ≧ [rear flow maintenance flow velocity V
C2O = {(S 2 × V 20 ) / S C 2 O } kinetic energy of the circulating air at a predetermined flow rate] × [1-[{(the inflow energy E 1 −the wind turbine drive energy E T ) is the rear reduction ventilation cutoff. Velocity V given to the circulating air passing through the area S C2O
C2O0} 2 / {the said rear flow maintained velocity V C2O inflow energy E 1 has on the circulation air passing through the rear reduced ventilation cross-sectional area S C2O} 2]], wherein the kinetic energy of the wind turbine outlet flow velocity V TO outflow loss compensation pressure and (predetermined flow rate) × the flow rate maintained energy E F system of the predetermined flow rate (the wind speed V 2 of the dynamic pressure) and is supplied from the upstream side and receiving said flow maintenance action by the wind of the exhaust extraoral artificially supplied to a distribution air, said rear reduced ventilation cross-sectional area S C2O
By maintaining the flow velocity at the rear flow rate maintenance flow velocity V C2O at a flow rate, the flow maintenance energy E F = the wind turbine drive energy E in lieu of consumption of the wind turbine drive energy E T.
T is generated and traced back to the axial flow wind turbine, and the flow rate maintenance energy E F in the wind pressure tube at atmospheric pressure is added to the flowing air of the F system, and the specific energy E per unit time unit flow rate of the flowing air E FH = 1 × ρ × g × 10.33 m
The outflow energy E 2 = (S 2 × V 20 ) based on Aq
× [said characteristic energy E FH {1 × ρ × g × 10.33
m Aq }] is maintained, and the circulating air of the predetermined flow rate over the entire length of the wind pressure pipe is
The inflow energy E 1 based on the action of gravity on the atmosphere, including the wind turbine drive energy E T that exists by rotating inside the axial wind turbine while rotating the runner in the circumferential direction.
The outflow energy E 2 and the intrinsic total pressure P of the wind at atmospheric pressure
FH = ρ × g × 10.33 m Aq is present, and the distribution of the artificial total pressure P = {(the inflow / outflow loss compensation pressure) − (loss pressure)} by the artificial energy that maintains the flow velocity in balance with the resistance is calculated. the specific total pressure P total pressure distribution air added to FH P F = (specific total pressure P FH + human total pressure P) is the exhaust port while maintaining a predetermined flow toward the exhaust port from the inlet dropped to static pressure P S2, the flow maintains action winds the exhaust extraoral has found a predetermined flow rate the flow rate maintained energy E F system circulation air of having said outflow energy E 2 at the wind pressure pipe, the exhaust The flow rate of the circulating air in the wind pressure pipe is stabilized at the predetermined flow rate by sucking it into the wind of the exhaust port static pressure P S2 at the predetermined outflow velocity V 20 and letting it flow away without leaving any change in the wind. By doing so, In response to the supply of three small artificial energies, the gravity acting on the fluid flow is converted into the large wind turbine drive energy E T and the large flow maintenance energy E F to drive the axial wind turbine to drive the axial wind turbine. A third class permanent motion engine that maintains the predetermined flow rate of the circulating air is realized, and the wind turbine output capacity (kW) = {predetermined flow rate (S 1 × V 10 )}.
X {g x 10.33 m Aq } x wind turbine efficiency-{(inflow / outflow loss compensation pressure energy) + {predetermined flow rate (S 1 x
V 10 )} × (dynamic pressure of wind velocity V 2 ) + (replacement kinetic energy for rear flow rate maintenance E C2K )} ÷ (power efficiency of artificial energy) How to convert to energy. 5. A water (wind) turbine inflow water (air) cross-sectional area S
G1O is made larger than the water (wind) turbine outflow water (air) cross-sectional area S G2I so that the water (wind) turbine inflow water (air) cross-sectional area S
Smaller than the flow rate maintained the flow velocity V G2i water (wind) car inflow velocity V G1o in the water (wind) car outlet water passage (gas) cross-sectional area S G2i in G1o, motion of the water (wind) car inflow velocity V G1o A part of the inflow / outflow loss compensation pressure of the artificial energy and the dynamic pressure of the water (wind) speed V 2 are partially shared by the difference between the pressure and the dynamic pressure of the flow rate maintenance flow velocity V G2I .
5. A method for converting gravity acting on a fluid flow according to 3 or 4 into kinetic energy. 6. When the water (wind) turbine load fluctuates, or
When the water (wind) speed fluctuates, according to the expected maximum value of the fluctuating water (wind) wheel load or the fluctuating water (wind) speed,
Predetermined flow rate, artificial energy inflow / outflow loss compensation pressure energy and {predetermined flow rate (S ₁ × V ₁₀ )} × {(wind) speed V
₂ dynamic pressure} and supplemental kinetic energy E _C2K for maintaining rear flow rate
And _{adjusting the} water (wind) _turbine inflow water (air) cross-sectional area S _G1O and the water (wind) _turbine outflow water (air) cross-sectional area S _G2I ,
Water (wind) _turbine inflow water (air) cross-sectional area S _G1O water (wind) _turbine inflow velocity V _G1O and water (wind) _turbine outflow water (air)
A flow maintaining the flow velocity V _G2i of the cross-sectional area S _G2i maintained at a predetermined value, the match output of water (wind) car load and water (wind) speed, the rotational speed of the water (wind) car to a predetermined value A method for converting gravity acting on a fluid flow according to claim 1, 2, 3 or 4 into kinetic energy, which is maintained. 7. When a speed governor is added to the output side of an axial water (wind) turbine to reduce the water (wind) speed, a predetermined flow rate and an artificial energy inflow / outflow loss compensation pressure energy {predetermined Flow rate (S ₁ × V ₁₀ )} × {dynamic pressure of water (wind) speed V ₂ } and supplemental kinetic energy for rear flow rate maintenance E _C2K are adjusted according to fluctuations in water (wind) speed, and artificial energy is adjusted. Is compensated for the loss generated in the _penstock to be consumed in the _penstock, and the water (wind) _turbine inflow water (air) cross-sectional area S _G1O and the water (wind) _turbine outflow water (air) cross-sectional area S _The lowered axial flow water (wind) _turbine is driven by the reduced water (wind) _turbine inflow velocity V _G1O and the flow maintenance flow velocity V _G2I determined by _G2I and the adjusted predetermined flow rate, and the axial flow water (wind) _turbine is lowered. The adjusted speed is adjusted to the specified speed by the speed governor and output, and the output of the water (wind) wheel is adjusted to the water (wind) speed. Method of converting gravitational force acting on fluid flow according to kinetic energy to claim 1, 2, 3 or 4 to. 8. A water (wind) _turbine is used to supply rear outflow loss compensation pressure energy for compensating the rear outflow loss energy generated between the rear reduced water flow (air) cross-sectional area S _C2O and the drainage (air) port to zero. from the supply to the drive energy E _T system running water (flow air), acting on the fluid flow according to said rear reduced water flow according to claim 1, 2 were transferred to the feed in (air) cross-sectional area S _C2O, or 4 A method of converting gravity into kinetic energy. 9. The effect of gravity on the atmosphere and the water flow, the water velocity V _H (m / sec) at the water depth H (m), and the resistance to each part of the water flow that acts on each part of the water flow and the water depth H is balanced.
At the water depth V, the inherent total pressure P _FH of the water flow at the water depth H based on the bias of the pressure on the air and the water flow maintaining the water velocity V _H due to the action of gravity in the flow direction and the action of gravity on the atmosphere and the water flow. = Specific static pressure P _SH + Specific dynamic pressure P _KH = [ρ ×
g × (H + 10.33m _Aq ) − {ρ × (V _H ) ² ÷
2}] + {ρ × (V _H ) ² ÷ 2} = ρ × g × (H + 1
0.33 m _Aq ) (t / m ² ) and a unit time unit flow rate 1 (m ³ / based on the action of gravity on the atmosphere and water flow)
specific energy E of the water flow at the water depth H per sec)
_FH = (the unique static _P specific pressure energy corresponding to the _{SH E} PH) + (the inherent dynamic pressure _P inherent kinetic energy corresponding to ^{_{KH E KH) = 1 (m}} 3 / sec) × [ρ × g ×
_{(H + 10.33m Aq) - {} ρ × (V H) 2 ÷ 2}]
(T / m ² ) +1 (m ³ / sec) × {ρ × (V _H ) ²
÷ 2} (t / m ² ) = 1 × ρ × g × (H + 10.33 m
_Aq ) (t · m / sec) in a water stream that circulates on a global scale, such as ocean currents and tidal currents, in a water stream that flows through a gradient such as a river or open channel, or relative to water In the moving body above or underwater, the force for maintaining the motion and the relative velocity with water can be treated as the pressure bias due to the action of gravity on the flow direction of the atmosphere and the water flow and the water velocity V _H , and the cross-sectional area S Flow velocity V ₁ (m / sec) at the inlet of ₁ (m ² ).
At an arbitrary water depth H ₁ (m), and the axial flow turbine provided near the central portion is arranged at a water depth H (m), and the water cross-section S ₂
The water discharge port of (m ² ) is arranged at the water depth H of water velocity V ₂ (m / sec) or at a water depth H ₂ (m) deeper than that, and the water passage cross-sections S ₁ and S ₂ are set to the water turbine described later. Based on the formula of the output capacity, (S ₁ × predetermined inflow velocity V ₁₀ ) = (S ₂ × water velocity V ₂
The following predetermined outflow velocity V ₂₀ ) (m ³ / sec) = (predetermined flow rate at which required output is obtained) is set, and the water flow cross-sectional area from the inflow port toward the axial flow turbine is Speed up and flow velocity of water turbine inflow V _G1O (m / se
In c), it is reduced to a turbine inflow water cross-sectional area S _G1O (m ² ) so as to flow into the axial water turbine, and the water cross-sectional area from the drain port to the axial water turbine is set to the axial water turbine. towards waterwheel outlet water passage cross-sectional area S _{G2I (m 2)} which is flowing water flowing out from the axis running water wheel while deflected circumferentially passes at a rate maintaining the flow velocity V _{G2I (m /} sec) and ⁼ the water turbine inlet passage A hydraulic pipe connected to the axial outlet of the axial flow _turbine in a state of being circumferentially deflected, which is gradually reduced to a water cross sectional area S _G1O and has a larger water cross sectional area, the inlet and the axial flow water. and all of the inflow loss pressure (t / m ²⁾ generated in running water of the predetermined flow rate of the water turbine drive energy E _T system between car outlet, the flow rate maintained energy E _F between said shaft running water vehicle exit the drain outlet Outflow loss pressure (t / m) generated in flowing water of the predetermined flow rate of the system Inflow / outflow loss compensation pressure energy (t · m / sec) for generating inflow / outflow loss compensation pressure (t / m ² ) for compensating all of ² ) and 0 =
(S ₁ × V ₁₀ ) × (compensation pressure of inflow / outflow loss) and {predetermined flow rate (S ₁ × V ₁₀ )} × (dynamic pressure of water speed V ₂ ) are the turbine driving energy E _T in the hydraulic pipe. In the front flow rate maintaining pressurized water supplying means for supplying to the flowing water of the system, and in the rear reduced water flow cross-sectional area S _C2O at any position between the outlet of the axial flow _turbine and the drain port, supplemental kinetic energy for maintaining the rear flow rate is provided. E _C2K ≧ [rear flow rate maintenance flow velocity V
_C2O = {(S ₂ × V ₂₀ ) / S _{C 2 O} } kinetic energy of flowing water at a predetermined flow rate] × [1-[{(the inflow energy E _{1 −the} water wheel drive energy E _T ) is the rear reduction water interruption. said rear flow maintained velocity _V ^{C2O} 2]]} where the flow velocity _{V C2O0}} ² / {the inflow energy _{E 1} to give the flowing water passing through the area _{S C2O} gives the flowing water passing through said rear reduced water passage cross-sectional area _{S C2O,} wherein and a predetermined flow rate of the flow maintaining energy E _F system rear flow maintains pressure pumping water means for supplying running water, water wheel output capacitance (kW) = {a predetermined flow rate (S ₁ × V _10)}
X {g x (H + 10.33 m _Aq )} x turbine efficiency-
{(Inflow / outflow loss compensation pressure energy) + {Predetermined flow rate (S ₁ × V ₁₀ )} × ( _Dynamic pressure of water velocity V ₂ ) + (Replacement kinetic energy for rear flow rate maintenance E _C2K )} ÷ (of artificial energy A device for converting gravity acting on a fluid flow into kinetic energy, which is characterized by obtaining electric power efficiency. 10. The action of gravity on the atmosphere and the wind velocity V _H
( _M / sec) is a bias of pressure in the direction of the wind accompanied by the effect of gravity on the atmosphere that acts on each part of the atmosphere and balances the resistance to the movement of each part of the atmosphere and maintains the wind speed V _H ;
The intrinsic total pressure P _FH of the wind at the wind velocity V _H based on the action of gravity on the atmosphere = intrinsic static pressure P _SH + intrinsic dynamic pressure P _KH = [ρ
_{× g × 10.33m Aq - {ρ} A × (V H) 2 ÷ 2}]
+ {Ρ _A × (V _H ) ² ÷ 2} = ρ × g × 10.33 m
_Aq (t / m ² ) and the specific energy E _FH of the wind at the wind speed V _H per unit time unit passing flow rate 1 (m ³ / sec) based on the action of gravity on the atmosphere E _FH = (the specific static pressure P
Specific kinetic energy _E KH) = 1 corresponding to the unique pressure energy _E PH) + (the inherent dynamic pressure _{P KH} corresponding to _SH
(M ³ /sec)×[ρ×g×10.33m _Aq − {ρ
_A × (V _H ) ² ÷ 2}] (t / m ² ) +1 (m ³ / se
c) × {ρ _A × (V _H ) ² ÷ 2} (t / m ² ) = 1 × ρ
Xg × 10.33 m _Aq (t · m / sec), or a wind accompanied by the force of maintaining the relative motion with the atmosphere and the relative velocity with the atmosphere accompanied by the action of gravity on the atmosphere. In the moving body in the atmosphere that can be treated as the bias of pressure in the direction of and the wind speed V _H , the inlet of the ventilation cross-sectional area S ₁ (m ² ) is introduced into the wind speed V ₁ (m / se).
c), an axial wind turbine near the center, and an exhaust port with a ventilation cross-sectional area S ₂ (m ² ) of wind speed V ₂ (m / sec).
And the ventilation cross-sections S ₁ and S _{2 in} which the change in ρ _A due to the flow velocity is corrected, based on the formula of the wind turbine output capacity described later, (S ₁ × predetermined inflow velocity V ₁₀ ) = (S ₂ x wind speed V
With ₂ following a predetermined outflow velocity _{V 20) (m 3 / sec} ) = ( required output is set so that a predetermined flow rate) obtained, the ventilation cross-sectional area toward the axial flow wind turbine from the inlet, circulation air And the wind turbine inflow velocity V _G1O (m / s
ec) is reduced to a wind turbine inlet ventilation cross-sectional area S _G1O (m ² ) so as to flow into the axial wind turbine, and the ventilation cross-sectional area from the exhaust port to the axial wind turbine is directed toward the axial wind turbine. The wind turbine outflow aeration cross-sectional area S _G2I (m ² ) = the wind turbine inflow aeration cross-sectional area in which the circulating air flowing out from the axial wind turbine passes at a flow rate maintenance flow velocity V _G2I (m / sec) while being deflected in the circumferential direction. A wind pipe connected to the axial outlet of the axial wind turbine with a larger air flow cross-sectional area in a state of being circumferentially deflected, which is gradually reduced to _{SG 1O} , and between the inlet and the axial wind turbine outlet. Of the inflow loss pressure (t / m ² ) generated in the circulating air of the predetermined flow rate of the wind turbine drive energy E _T system, and the flow rate maintenance energy E _F system between the outlet of the axial flow wind turbine and the exhaust port Outflow loss that occurs in a certain amount of circulating air Total loss (t / m ² ) and 0
Inflow / outflow loss compensation pressure energy (t · m / se) to generate inflow / outflow loss compensation pressure (t / m ² )
c) = (S ₁ × V ₁₀ ) × (inflow / outflow loss compensation pressure)
And {predetermined flow rate (S ₁ × V ₁₀ )} × (dynamic pressure at wind speed V ₂ )
Said wind turbine drive energy E _T based front flow maintains pressure pumping air means for supplying the flow of air in the wind pressure tube and rear reduced ventilation cross-sectional area at an arbitrary position between the outlet of the axial flow wind turbine outlet In S _C2O , the supplemental kinetic energy for rear flow rate maintenance E _C2K ≧ [rear flow rate maintenance flow velocity V
_C2O = {(S ₂ × V ₂₀ ) / S _{C 2 O} } kinetic energy of the circulating air at a predetermined flow rate] × [1-[{(the inflow energy E _{1 −the} wind turbine drive energy E _T ) is the rear reduction ventilation cutoff. _Velocity V given to the circulating air passing through the area S _C2O
C2O0} ² / {the inflow energy _{E 1} is the flow rate maintained energy _{E F} system of the predetermined flow rate the rear flow maintained velocity _V ^{C2O} 2]]} to give the distribution air passing through said rear reduced ventilation cross-sectional area _{S C2O} A rear flow rate maintaining pressurized air blower for supplying to the circulating air, and a wind turbine output capacity (kW) = {predetermined flow rate (S ₁ × V ₁₀ )}
X {g x 10.33 m _Aq } x wind turbine efficiency-{(inflow / outflow loss compensation pressure energy) + {predetermined flow rate (S ₁ x
V ₁₀ )} × (dynamic pressure of wind velocity V ₂ ) + (replacement kinetic energy for rear flow rate maintenance E _{C2 K} )} ÷ (power efficiency of artificial energy) A device that converts kinetic energy. 11. A water pressure pipe or a wind pressure pipe has an inflow portion having a water (air) passage from which the water (air) cross-sectional area is reduced, and a front cylindrical similar space connected to the inflow portion. A plurality of front guide vanes that are present in the front cylindrical similar space and gradually increase the deflection angle in the circumferential direction to gradually reduce the water (air) cross-sectional area of the front cylindrical similar space. _Consists of the water (wind) _turbine inflow water (air) cross-sectional area S _G1O
(M ² ) and water (wind) turbine flow velocity V of flowing water (circulating air)
A front guide vane portion having _G1O (m / sec), and running water (circulating air) that is deflected in the circumferential direction from the front guide vane portion and flows out at the water (wind) _turbine inflow velocity V _G1O.
In response to this, the water (wind) turbine inflow velocity V deflected in the circumferential direction
_{By changing} the direction of _G1O to the axial direction, the circumferential component flow velocity V of the water (wind) _turbine inflow velocity V _G1O
It is rotationally driven in the circumferential direction with kinetic energy of _TK (m / sec), and the water (wind) wheel inflow velocity V _G1O axial component flow velocity or the water (wind) wheel outflow velocity V determined by the load factor.
Water (air) cross-sectional area S _TO (m ² ) at _TO (m / sec)
Flowing water (circulating air) from the water (wind) wheel outlet of
{(Kinematic energy of water (wind) _turbine inflow velocity V _G1O )-
A shaft running water (wind) car with a runner which is driven by a (water (wind) car outflow velocity V _TO kinetic energy) consisting} water (wind) car drive energy E _T, said axis running water (wind) Car Output To the outside, a rear cylindrical similar space connected to the outlet of the axial water (wind) turbine, and a deflection angle in the circumferential direction is the largest at the upstream inlet in the rear cylindrical similar space. , A plurality of rear guide vanes that gradually decrease the deflection angle in the circumferential direction toward the downstream side and gradually increase the water (air) cross-sectional area of the rear cylindrical similar space. At a rear guide vane portion having a water (wind) _turbine outflow water cross-sectional area S _G2I (m ² ) and a flow rate maintenance flow velocity V _G2I (m / sec) of flowing water (circulating air), and at an outlet of the rear guide vane portion. Connect and gradually expand the water flow (air) cross-sectional area Apparatus for converting the kinetic energy of the gravitational force acting on the fluid flow according to claim 9 or 10 and a outlet portion for.