JP2020094546A - Cross-flow water turbine - Google Patents

Abstract

To provide a cross-flow water turbine for small scale hydraulic power capable of suppressing vibration and noise of a water turbine main body by eliminating a branch pipe and a discharge valve by controlling an opening of a release valve obtained by providing one of guide vanes with a function as the discharge valve, and discharging water in a manner of not contributing to rotation of a runner, and being manufactured and constructed while suppressing costs of discharge facility.SOLUTION: In a cross-flow water turbine having a conduit pipe, a discharge pipe, a casing, a runner, a guide vane, and a housing having a flow channel communicated with the discharge pipe from the casing, the guide vane is divided into a plurality of guide vanes, and at least one guide vane is applied as a release valve. When water flow of which a flow rate is adjusted by an opening of the guide vane, is first water flow, and water flow of which a flow rate is adjusted by an opening of the release valve, is second water flow, the first water flow rotates and drives the runner, and the second water flow is discharged to the discharge pipe without rotating and driving the runner.SELECTED DRAWING: Figure 5

Description

The present invention relates to a cross flow turbine. More specifically, by controlling the opening of the release valve that causes a part (one) of the multiple guide vanes to function as a discharge valve, and by discharging so as not to contribute to the rotation of the runner, The present invention relates to a cross-flow turbine for small-scale hydropower, which can be manufactured and constructed by eliminating pipes and discharge valves and suppressing the cost of discharge equipment.

In recent years, interest in natural energy has increased, and solar power generation, wind power generation, or hydraulic power generation has been in the spotlight.

In particular, as a measure to prevent global warming, which is one of the conservation of the global environment, reduction of greenhouse gas emissions represented by carbon dioxide is required in power generation as well. Power generation is receiving attention again. Furthermore, hydropower is capable of stable power generation throughout the day and night, with a high facility utilization rate of 50-90%, capable of generating 5-8 times the amount of electricity compared to solar power generation, and fluctuations in output. There are many advantages such as low system stability and no impact on power quality.

As a hydroelectric power generation device, a water-channel type small hydroelectric power generation is attracting attention as a device for generating electric power without constructing a dam. This small hydroelectric power generation is required to have a structure capable of efficiently generating power even with a low head and small flow rate. So far, hydroelectric power generation equipment may become an important pillar for stabilizing the power system. Therefore, as various types of turbines, multi-faceted research and development is being carried out such as Francis turbines for small hydropower, pump reversal turbines, horizontal propeller turbines, and cross-flow turbines.

Japanese Patent Application Laid-Open No. 58-67972 (Patent Document 1) and Japanese Patent Application Laid-Open No. 59-138767 (Patent Document 2) disclose a cross flow turbine with guide vanes so that the amount of water flowing into a runner can be adjusted. Different configurations are disclosed.

In addition, JP-A-64-87876 (Patent Document 3), JP-A-8-165981 (Patent Document 4) and JP-A-4-347376 (Patent Document 5) disclose a plurality of cross-flow turbines. A technique for controlling the flow rate using a guide vane divided into two is disclosed.

Further, as disclosed in JP-A-54-160935 (Patent Document 6), JP-A-61-291778 (Patent Document 7) and JP-A-63-173853 (Patent Document 8). Generally, a turbine needs to discharge water to the downstream side through the turbine even when the turbine is stopped. In particular, when the turbine is stopped, it is often necessary to discharge (release) a required amount of water on the downstream side.

The structure of a conventional water turbine corresponding to such a case will be described with reference to FIG.

The water turbine 100 shown in FIG. 1 is provided with a water conduit 102 that guides a water stream 101, a casing 103 to which the water stream is supplied, a runner 104 that is disposed in the casing 103 and rotates by the water stream 101, and a branch pipe 105 to which the water stream 101 is supplied. It is configured by a discharge valve 107 that is closed when the water flow 101 is not discharged, and is opened when the water flow 101 is discharged, and a discharge pipe 106 that discharges the water flow 101 discharged from the discharge valve 107 to the outside. When the water turbine 100 is operating, the water flow 101 passes through the water conduit 102 and is guided into the casing 103 to rotate the runner 104. However, when the water turbine 100 is stopped, the water flow 101 'Stops. Instead, the water stream 101 is guided to the branch pipe 105 as a water stream 101 ″. When the discharge valve 107 is opened, the discharge pipe 106 discharges the discharged water (not shown) to the downstream side. The turbine shown in FIG. 1 is mainly a Francis turbine.

Next, an external perspective view of the cross-flow turbine 110 having two guide vanes will be described with reference to FIG. 2 is an external perspective view (overall view) of the crossflow turbine 110 in which the casing 113 and the housing 117 of the crossflow turbine 110 are removed so that the inside of the crossflow turbine 110 can be seen.

As shown in FIG. 2, runners 114a and 114b of the cross flow turbine 110 are provided with runner vanes 114d, which are blades having both ends fixed between the end plates 114f on both sides, in the circumferential direction. The water wheel shaft (axial center) 114c is fixed to the shaft 114e and is rotatably formed. At the same time, the runners 114a and 114b are housed in the casing 113 and the housing 117. Further, the guide vanes 115a and 115b are divided by a partition plate 119. The guide vanes 115a adjust the flow rates on the left side in the figure and the guide vanes 115b adjust the flow rates on the right side in the figure (the guide vanes 115a and 11b will be described in detail later). Thus, the split guide vane type cross-flow turbine 110 is rotated by the water whose runners 114a and 114b flow in via the water conduit (inlet tube) 112. Then, the water obtained by rotating the runners 114a and 114b is discharged through the discharge pipe (draft pipe) 116. In the figure, 120 is an air introduction valve, and 121 is a bearing frame.

Next, FIG. 3 shows a schematic diagram of the internal structure of the cross section of the main part of the cross-flow turbine 110 having two guide vanes, and FIG. 4 shows a schematic diagram of the internal structure of the cross-section of the main part of the cross-flow turbine 110. Explain. A water conduit (water supply pipe) 112 is communicatively connected to an inlet of a casing (runner cover) 113 of the cross flow turbine 110. Further, the inlet of the housing 117 is connected to the outlet of the casing 113. The outlet of the housing 117 is communicatively connected to the inlet of the discharge pipe 116. Further, the two runners 114a and 114b are tandemly coupled (in side-by-side arrangement) to each other. In addition, the guide vanes 115a and 115b rotate about the guide vane shaft 115c as a rotation axis.

Then, as shown in FIG. 4, when the opening degree of the guide vane 115a is increased, the water flow in the upper water passage 111a of the guide vane 115a and the lower water passage 111b of the guide vane 115a in the water conduit 112 and the casing 113 is It is controlled according to the opening degree of the vane 15a. The same applies when the opening of the guide vane 115b is lowered.

Further, a water turbine shaft (rotating shaft) 114c extending in the horizontal direction is coaxial with the shaft cores of the runners 114a and 114b, and two runners 114a and 114b are rotatably installed. The two runners 114a and 114b have runner vanes 114d, which are a plurality of arcuate blades, arranged on the circumference of the runners 114a and 114b at substantially equal pitches.

Further, a guide vane 115a and a guide vane 115b corresponding to the two runners 114a and 114b are arranged on the water conduit 112 side.

A partition plate 119 is provided between the guide vanes 115a and 115b. A corresponding lever (not shown) and a link (not shown) are connected to the guide vanes 115a and 115b, respectively. The opening degree of the guide vanes 115a and 115b can be independently controlled by operating a lever and a link using a drive system (not shown). In this way, the flow rate of the flowing water flowing from the water conduit 112 is adjusted by the two guide vanes 115a and 115b. Then, the running water is applied to the runners 114a and 114b with an impact force or a reaction force, and then the running water is discharged to the discharge pipe 116.

Here, the length (width) of the guide vane 115a in the axial direction is L, and the length (width) of the guide vane 115b is L'. The flow rates when the guide vanes 115a and 115b are fully opened are L/(L+L') and L'/(L+L') with respect to the maximum flow rates flowing into the runners 114a and 114b.

On the other hand, the turbine operation efficiency is different when the flow rate is controlled by the guide vanes 115a or 115b, but generally, the turbine operation is performed by switching the guide vanes 115a and 115b according to the desired flow rate. It is possible to drive a water turbine with high efficiency.

JP 58-67972 A JP-A-59-138777 JP-A-64-87876 JP-A-8-165981 JP-A-4-347376 JP-A-54-160935 Japanese Patent Laid-Open No. 61-291778 JP-A-63-173853

Conventionally, a water turbine used in a hydroelectric power plant has a structure in which a pipe that flows into the water turbine and a pipe that flows into a water discharge port are separated, and a branch pipe for discharge is added in the middle of a water pipe.

Such a configuration is not suitable for small-scale hydroelectric power generation because not only manufacturing cost and construction cost increase but also maintenance cost increases.

The present invention has been made based on the above circumstances, the object of the present invention is to control the opening of the release valve that has a function as a discharge valve in one of the guide vane is a plurality of, In addition, it is intended to provide a cross-flow turbine for small-scale hydroelectric power generation, which can be manufactured and constructed by suppressing the cost of the discharge facility by discharging the branch pipe and the discharge valve by discharging so as not to contribute to the rotation of the runner. ..

The above object of the present invention is to provide a water conduit, a discharge pipe, a casing having an inner surface shape for guiding inflow water from the water conduit, a rotatably supported inside the casing, and a rotation axis arranged laterally. A housing having a runner, a guide vane arranged in the casing so that the opening can be changed in order to adjust the flow rate of the water flow in the casing, and a flow path communicating from the casing to the discharge pipe. And a guide flow vane divided into a plurality, at least one of the guide vanes is a release valve, a water flow whose flow rate is adjusted by the opening of the guide vane is a first water flow, A water flow whose flow rate is adjusted by the opening degree of the release valve is referred to as a second water flow, the first water flow drives the runner to rotate, the second water flow does not drive the runner to rotate, and the discharge pipe It is achieved by being released to.

Further, the above-mentioned object of the present invention is a release valve opening sensor that detects an actual opening of the release valve, a cross flow turbine drive control unit that calculates a control amount based on the actual opening, and A jet brake is disposed by further comprising a release valve driving servomotor that rotates the release valve based on a control amount, or a jet brake is arranged so as to penetrate the surface of the housing, and the jet brake is used to run the runner. More effectively achieved by braking the rotational movement of the.

Also, a power generation system using a cross-flow turbine, in which a jet brake is arranged so as to penetrate the surface of the housing, and the jet brake is used to brake the rotational motion of the runner, the system being connected to the cross-flow turbine. It is more effectively achieved by controlling the jet brake so that the rotation speed of the runner that occurs when the load is cut off does not exceed the yield strength of the generator.

Further, the above-mentioned object of the present invention is a power generation system using any of the above cross-flow turbines, comprising a generator connected to the cross-flow turbine, wherein the rotation speed of the runner that occurs at the time of load shedding is This can be achieved more effectively by controlling the opening of the release valve so that the yield strength of the generator is not exceeded.

ADVANTAGE OF THE INVENTION According to the cross flow turbine which concerns on this invention, the opening degree of the release valve which made one sheet of the guide vane carry out the function as a discharge valve is controlled, and it discharges so that it may not contribute to rotation of a runner. As a result, the branch pipe and the discharge valve can be eliminated, vibration and noise of the turbine main body can be suppressed, and the manufacturing and construction can be performed while suppressing the cost of the discharge facility.

Furthermore, when a generator is connected to the cross-flow turbine according to the present invention, the rotational speed (rotational speed) of the runner is crossed by the jet brake that suppresses the rotational increase (unrestrained speed) of the turbine runner when the load is cut off. It can be protected so that it does not exceed the yield strength of the flow turbine or generator.

Then, if it is possible to increase the rotation speed of the runner in a range that does not exceed the proof stress of the crossflow turbine or the generator, not only can the crossflow turbine and the power generation equipment using the crossflow turbine be downsized, It is possible to expand the applicable range of the cross flow turbine.

It is a figure which shows the structure of the conventional water turbine which has a discharge valve. It is an external appearance perspective view of a cross-flow turbine having two conventional guide vanes. FIG. 5 is a view (plan cross-sectional view) in the V direction of the cross-flow turbine shown in FIG. 2, and is a schematic view of an internal structure of a main-section plane cross section of the cross-flow turbine. FIG. 4 is a vertical cross-sectional view of the cross-flow turbine shown in FIG. 2 taken along the cutting line AA shown in FIG. 3, and is a schematic view of an internal structure of a main-section vertical cross-section of the cross-flow turbine. It is an external appearance perspective view of the cross-flow water turbine which concerns on the 1st Embodiment of this invention. FIG. 6 is a view (plane cross-sectional view) in the direction V of the cross-flow turbine shown in FIG. 5, and is a schematic view of an internal structure of a main-section plane cross section of the cross-flow turbine. FIG. 7 is a vertical cross-sectional view of the cross-flow turbine shown in FIG. 5 taken along the cutting line AA shown in FIG. 6, showing the internal structure of the main-section vertical cross-section of the cross-flow turbine when the opening of the release valve is low. FIG. It is a longitudinal cross-sectional view which cut|disconnected the cross flow turbine shown in FIG. 5 along the cutting line BB shown in FIG. 6, and is a schematic diagram of the internal structure of the principal part longitudinal cross section of the said cross flow turbine. FIG. 8 is a diagram showing a state of water flow in the water channel when the opening degree of the release valve is high in the schematic view of the cross-flow turbine shown in FIG. 7. It is a schematic diagram which shows an example of the internal structure of the principal part longitudinal cross section about the cross-flow turbine which concerns on the 2nd Embodiment of this invention, and is a figure which shows a mode that the jet brake penetrated the housing. It is a block diagram which shows an example of the cross-flow turbine which concerns on the 3rd Embodiment of this invention.

The cross-flow turbine according to the embodiment of the present invention controls the opening degree of the release valve in which a part (one) of the plurality of guide vanes functions as a discharge valve, and does not contribute to the rotation of the runner. By thus discharging, the branch pipe and the discharge valve can be eliminated, vibration and noise of the crossflow turbine main body can be suppressed, and manufacturing and construction can be performed while suppressing the cost of the discharge facility.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

(First embodiment)
An external perspective view of the cross-flow turbine 10 according to the first embodiment will be described with reference to FIG. In addition, FIG. 5 is an external perspective view of the crossflow turbine 10 in which the casing 13 and the housing 17 of the crossflow turbine 10 according to the first embodiment are partially removed so that the inside of the crossflow turbine 10 can be seen ( It is an overall view), and an external perspective view of the cross-flow turbine 10 according to the first embodiment is shown in correspondence with FIG. 2 showing a conventional example. The description of the components common to the cross flow turbine 10 according to the first embodiment and the conventional cross flow turbine 110 as shown in FIG. 2 is omitted, but the cross flow according to the first embodiment is omitted. The components of the water turbine are given different symbols to clearly distinguish them from the components of the conventional cross-flow turbine.

In contrast to the conventional cross-flow turbine 110 shown in FIG. 2, in the cross-flow turbine according to the first embodiment shown in FIG. 5, one of the two guide vanes is used as the release valve 15a, and the downstream side of the release valve 15a. The space is different in that the runner 14b is not provided on the turbine shaft 14c, and the release valve 15a has a function as a discharge valve, but is substantially the same in other respects.

Further, FIG. 6 is a view (plan cross-sectional view) in the V direction of the cross-flow turbine 10 shown in FIG. 5, showing a schematic diagram of an internal structure of a main-section plane cross-section of the cross-flow turbine 10. As shown in FIG. 6, no runner is provided on the turbine shaft 14c in the space downstream of the release valve 15a. Therefore, in the cross flow turbine 10, the amount of water discharged to the discharge pipe 16 can be adjusted based on the opening degree of the release valve 15a. That is, the release valve 15a can be made to function as a discharge valve. As shown in FIG. 6, the guide vane 15b and the release valve 15a of the cross flow turbine 10 are partitioned by a partition plate 19, and both ends of the runner 14b are fixed between the end plates 14f on both sides. A runner vane 114d, which is a blade, is arranged in the circumferential direction. Further, the guide vane 15a and the release valve 15a rotate about the guide vane shaft 15c as a rotation axis.

7 is a vertical cross-sectional view of the cross-flow turbine 10 taken along the cutting line AA shown in FIG. 6, and shows a schematic diagram of the internal structure of the main-section vertical cross-section of the cross-flow turbine 10. As shown in FIG. 7, when the opening degree of the release valve 15a is reduced to approach the vertical plane to the vertical direction, the flowing water channel G is narrowed or closed. As shown in FIG. 7, when the opening degree of the release valve 15a is lowered, the water flow in the upper water passage 11a of the release valve 15a and the lower water passage 11b of the release valve 15a in the water conduit 12 and the casing 13 is the same as that of the release valve 15a. Is restricted or stopped by Therefore, the inflow of the water flow is restricted or prohibited in the areas A and A'in the casing 13 and the housing 17. That is, by lowering the opening of the release valve 15a, the discharge of the discharge pipe 16 can be limited or prohibited.

Further, FIG. 8 is a vertical cross-sectional view of the cross-flow turbine 10 taken along the cutting line BB shown in FIG. 6, and shows a schematic diagram of the internal structure of the main-section vertical cross-section of the cross-flow turbine 10. Further, when the opening degree of the release valve 15a is increased to be slightly horizontal to the horizon, the flowing water channel G widens. As shown in FIG. 8, when the opening of the guide vane 15b is increased, the water flow in the upper water passage 11a of the guide vane 15b and the lower water passage 11b of the guide vane 15b in the water conduit 12 and the casing 13 is the same as the guide vane 15b. It is controlled according to the opening degree of. Therefore, the water flow can enter the areas A and A'in the casing 13 and the housing 17, and at the same time, the energy of the water flow colliding with the runner vanes 14d of the runner 14b causes the runner 14b to rotate. That is, by increasing the opening of the guide vane 15b, the runner 14b rotates and the water flow is discharged to the discharge pipe 16.

Next, FIG. 9 shows a state of water flow in each water channel when the opening degree of the release valve 15a is high in the schematic diagram of the cross-flow turbine according to the first embodiment shown in FIG.

Then, when the opening degree of the release valve 15a is sufficiently high, the water flow in the upper water passage 11c of the release valve 15a and the water flow in the lower water passage 11d of the release valve 15a enter the regions A and A'without substantial resistance. Then, the water flow is discharged to the discharge pipe 16 without rotating the runner 14b.

Therefore, when the cross-flow turbine 10 according to the first embodiment is connected to a generator (not shown), it is possible to suppress an increase in rotation (unrestrained speed) of the runner 14b when the load is cut off. As a result, the rotation speed of the runner 14b can be protected so as not to exceed the proof stress of the generator connected to the cross flow turbine 10.

As described above, in the cross-flow turbine 10 according to the first embodiment, when the opening degree of the release valve 15a is the lowest, the lower water passage 11a of the release valve 15a and the lower water passage 11b of the release valve 15a. Since the water flow cannot enter the regions A and A'in the casing 13 and the housing 17, it does not collide with the runner vanes 14b of the runner 14b and does not contribute to the rotation of the runner 14b.

In the cross flow turbine 10 according to the first embodiment, when the opening degree of the release valve 15a is between the lowest opening degree and the highest opening degree, the lower water passage 11a of the release valve 15a and The amount of the water flow in the upper water passage 11b of the release valve 15a passes through the regions A and A'in the casing 13 and the housing 17 without contributing to the rotation of the runner 14b, and the water flow is discharged to the discharge pipe 16. On the other hand, depending on the opening degree of the guide vane 15b, the lower water channel (not shown) of the guide vane 15b can contribute to the rotation of the runner 14b by the energy that collides with the runner 14b.

That is, the crossflow turbine 10 according to the first embodiment controls the opening degree of the release valve 15a, so that the water flow entering the water channels 11c and 11d in the regions A and A′ surrounded by the casing 13 and the housing 17. The amount of water can be controlled.

In this way, by independently adjusting the respective openings of the release valve 15a and the guide vane 15b, the amount of water flow discharged without contributing to the rotation of the runner 14b and the amount of water flow contributing to the rotation of the runner 14b. Can be controlled.

(Second embodiment)
Next, a cross-flow turbine 20 according to the second embodiment of the present invention will be described with reference to FIG.

The crossflow turbine 20 according to the second embodiment is different from the crossflow turbine 10 according to the first embodiment in that a jet brake 21 having a bent pipe (cylindrical) appearance is provided. However, other configurations are almost the same. Therefore, the same components as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted. Note that FIG. 10 is a vertical cross-sectional view cut across the substantial center of the jet brake 21, and is a schematic diagram of an internal structure of a main-part vertical cross-section of the crossflow turbine 20.

In the cross-flow turbine 20 according to the second embodiment, the jet brake 21 penetrates the surface of the casing 13 and is arranged with the injection port facing the runner 14b. Then, the running water injected from the jet brake 21 collides with the back surface of the runner vane (runner blade) 14d. The collision energy (jet force) brakes the rotation of the runner 14b.

In the cross-flow turbine 20 according to the second embodiment, the rotational speed of the runner 14b exceeds the proof stress of the cross-flow turbine 20 by the jet brake 21 that suppresses the rotational increase (unrestrained speed) of the runner 14b when the load is cut off. You can protect it from being protected.

(Third Embodiment)
Next, FIG. 11 shows a block diagram of a hydraulic cross-flow turbine 30 according to a third embodiment of the present invention.

The crossflow turbine 30 according to the third embodiment drives the release valve driving servomotor 31a with respect to the crossflow turbine 10 according to the first embodiment or the crossflow turbine 20 according to the second embodiment. A cross flow turbine drive control unit 32 for controlling the amount of flowing water by adjusting the opening of the release valve 15a and driving the guide vane driving servomotor 31b to adjust the opening of the guide vane 15b. However, other configurations are almost the same. Therefore, the same components as those of the first and second embodiments are designated by the same reference numerals, and the description thereof will be omitted.

As shown in FIG. 11, the cross-flow turbine 30 according to the third embodiment includes a release valve driving servomotor 31a, a guide vane driving servomotor 31b, and an opening for detecting the actual opening degree of the release valve 31a. Degree sensor 35a, an opening sensor 35b for detecting the actual opening of the guide vane, and a release valve drive based on the opening of the release valve 15a and the opening of the guide vane 15b measured by the opening sensors 35a and 35b. The servo motor 31a and the guide vane driving servo motor 31b are provided with a cross flow turbine drive control unit 32 that independently controls the openings of the release valve 15a and the guide vane 15b.

Specifically, an opening sensor 35a and an opening sensor 35b for detecting the actual opening of the release valve 15a and the actual opening of the guide vane 15b are provided in the release valve 15a and the guide vane 15b, respectively. ..

Next, the opening degree sensor 35a and the opening degree sensor 35b output the actual opening degree of the release valve 15a and the guide vane 15b to the control unit 32a of the cross flow turbine drive control unit 32, respectively.

Then, the control unit 32a outputs to the drive unit 32b a control command value calculated using the actual opening amounts of the release valve 15a and the guide vane 15b. The drive unit 32b outputs a control signal to the release valve driving servomotor 31a and the guide vane driving servomotor 31b based on the control command value. By the control method as described above, the cross flow turbine drive control unit 32 is operated until the opening sensor 35a and the opening sensor 35b detect the opening of the target release valve 15a and the opening of the target guide vane 15b, respectively. Controls the release valve driving servomotor 31a and the guide vane driving servomotor 31b. Thus, the amount of water flowing in the discharge pipe 16 and the amount of water flowing in the rotation of the runner 14b can be controlled together without contributing to the rotation of the runner 14b.

As described above, the cross-flow turbine according to each embodiment of the present invention uses the water flow in which the amount of water is adjusted by the opening degree of the release valve in which one of the plurality of guide vanes functions as a discharge valve. By providing the runner so as not to rotate, the following special effects are achieved.

The release valve 15a according to each of the embodiments of the present invention can also have the function of a conventional discharge valve such as a discharge pipe or a branch pipe.

The cross-flow turbine according to each embodiment of the present invention and the power generation equipment using the same can reduce the water energy ejected from the release valve and suppress the vibration and noise of the main body of the cross-flow turbine. Also, the rotation of the runner (unrestrained speed) that occurs when the load is cut off can be protected so as not to exceed the proof stress of the generator or power generation equipment.

Furthermore, in the cross-flow turbine according to the embodiment of the present invention, the rotation of the runner can be braked by adding a jet brake that causes the water flow to collide with the back surface of the runner blade.

If it is possible to increase the rotation speed of the runner within the range that does not exceed the proof stress of the cross-flow turbine or the generator, not only can the turbine cross-flow turbine and the power generation equipment using the cross-flow turbine be downsized. , It is possible to expand the range of application of power generation equipment using cross flow turbines.

Although the embodiments of the present invention have been described with reference to the examples, each embodiment is a preferable example, and other configurations or structures having similar effects and characteristics are within the scope of the present invention. ..

Needless to say, the present invention is not limited to the above embodiments, and various modifications can be made without departing from the scope of the present invention.

In each of the embodiments of the present invention, one of the two guide vanes is used as the release valve, but three or more guide vanes may be provided. In such a case, one of N (N is an integer of 3 or more) guide vanes may be used as a release valve. Further, as a generalization, the guide vanes may be used as a release valve up to the maximum number (N-1) of the N (N is an integer of 2 or more) guide vanes. The positional relationship with the valve may be freely selected.

Further, in each of the embodiments of the present invention, the entire surface of one guide vane is used as the release valve, but a part of one guide vane may be used as the release valve. In this case, the flowing water that has passed near the part may be discharged without rotating the runner.

The shape and material of the release valve 15a are substantially the same as those of the guide vanes 15b. The material of the release valve and the guide vane according to the embodiment of the present invention is not particularly limited and may be made of metal or synthetic resin, but is light and thin and has excellent strength, for example, a vinyl chloride plate, A synthetic resin plate such as glass fiber reinforced plastic, carbon fiber reinforced plastic, boron fiber reinforced plastic, FRP (Fiber Reinforced Plastics) such as aramid fiber reinforced plastic, aluminum or stainless steel is suitable.

Further, when a cast steel product is selected as the material of the guide vanes, a JIS (Japanese Industrial Standard) SC450 carbon steel cast product or a JIS-SCS1 stainless steel cast steel product is suitable.

The cross flow turbine drive control unit 32, which controls the opening degrees of the guide vanes 15b and the release valves 15a of the cross flow turbine 30 according to the third embodiment of the present invention, includes a target guide vane and a target release valve opening degree. Also, the release valve driving servomotor 31a and the guide vane driving servomotor 31b are controlled based on the actual opening of the guide vane 15b and the actual release valve 15a, but PID (proportional integral derivative) calculation control is used. The release valve driving servo motor 31a and the guide vane driving servo motor 31b may be controlled.

For example, in the cross flow turbine 30 according to the third embodiment of the present invention, the cross flow turbine drive control unit 32 is provided with a guide vane drive speed control unit, and a control target value in the guide vane drive servomotor 31b, In response to the detected deviation from the actual rotation speed, the guide vane drive speed control section performs PID (proportional integral derivative) calculation control of the guide vane control target value to control the guide vane drive servomotor 31b. You may.

Similarly, the cross flow turbine drive control unit 32 is provided with a release valve drive speed control unit, which receives a deviation between the control target value of the release valve drive servo motor 31a and the detected actual rotation speed to release the release valve. The release valve drive servomotor 31a may be controlled by subjecting the valve control target value to PID (proportional integral derivative) calculation control. In addition, in the cross-flow water turbine which concerns on the 3rd Embodiment of this invention, it may replace with said PID calculation control, PI calculation control may be used, and another calculation control method may be employ|adopted.

10, 20, 30, 110 Cross-flow turbines 11a, 11c, 111a Upper water channels 11b, 11d, 111b Lower water channels 12, 102, 112 Water conduits 13, 103, 113 Casings 14b, 104, 114a, 114b Runners 14c, 114c Water Axle (shaft part)
14d, 114d runner vanes (runner blades)
14f, 114f End plate 15a Release valve 15b, 115a, 115b Guide vane 15c, 115c Guide vane shaft 16, 106, 116 Discharge pipe 17, 117 Housing 19, 119 Partition plate 21 Jet brake 31a Release valve driving servo motor 31b Guide vane Drive servo motor 32 Cross flow turbine drive control section 32a Control section 32b Drive section 35a, 35b Opening sensor 100 Turbine 101, 101', 101'' Flowing water 105 Branch pipe 107 Discharge valve 114e Shaft 120 Air introduction valve 121 Bearing frame

Claims (5)

A water guide pipe, a discharge pipe, a casing having an inner surface shape for guiding inflow water from the water guide pipe, a runner rotatably supported in the casing, and a rotation axis arranged laterally, and the inside of the casing. A cross-flow turbine having a guide vane arranged in the casing and a housing having a flow path communicating with the discharge pipe from the casing so that the opening can be changed in order to adjust the flow rate of the water flow. There
The guide vane is divided into a plurality,
At least one of the guide vanes is a release valve,
The water flow whose flow rate is adjusted by the opening of the guide vane is referred to as a first water flow,
The water flow whose flow rate is adjusted by the opening degree of the release valve is referred to as a second water flow,
The first water stream drives the runner to rotate,
A cross flow turbine, wherein the second water flow is discharged to the discharge pipe without rotating the runner. A release valve opening sensor for detecting the actual opening of the release valve,
Based on the actual opening, a cross flow turbine drive control unit for calculating a control amount,
The crossflow turbine according to claim 1, further comprising a release valve driving servomotor that rotates the release valve based on the control amount. A jet brake is placed through the surface of the housing,
The crossflow turbine according to claim 1 or 2, wherein the jet brake is used to brake the rotational movement of the runner. A power generation system using the cross flow turbine according to claim 3,
A generator connected to the cross-flow turbine,
A power generation system, wherein the jet brake is controlled so that the rotation speed of the runner that occurs when the load is cut off does not exceed the yield strength of the generator. A power generation system using the cross-flow turbine according to claim 1 or 2,
A generator connected to the cross-flow turbine,
A power generation system characterized in that the opening of the release valve is controlled so that the rotation speed of the runner that occurs when the load is cut off does not exceed the yield strength of the generator.