JP3869168B2 - Driving method of pump turbine - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to an operation method of a pump turbine, and more particularly, to an operation method of a pump turbine that operates while suppressing cavitation generation at a high head during pumping operation or at a low head during power generation operation.
[0002]
[Prior art]
Recent hydroelectric power plants have an upper pond and a lower pond. In many cases, a hydroelectric power generation operation is performed by using the water stored in the upper pond during the day and the water stored in the lower pond is returned to the upper pond at night. In this case, the hydraulic machine that performs the pumped-storage power generation operation uses a Francis-type turbine runner having a high ability to handle a large amount of stored water.
[0003]
As shown in FIGS. 9 and 10, this Francis-type turbine runner is integrally formed with 6 to 7 runner vanes 3 between a disc-shaped runner crown 1 and a runner band 2, and the runner vanes 3. The runner vane 3 is formed into a spiral shape and the length thereof is increased to make the length of the runner vane 3 longer, and the speed increase flow during the power generation operation can be dealt with favorably while mainly dealing with the deceleration flow of the pump operation. In addition, the hydraulic performance is not degraded.
[0004]
[Problems to be solved by the invention]
The Francis turbine runners shown in FIGS. 9 and 10 have relatively high hydropower performance compared to other types of runners, but still have some problems, one of which is during pumping operation and power generation operation. There is a time cavitation problem.
[0005]
Conventionally, in the Francis type turbine runner, as shown in FIG. 11, the inflow water W flows into the runner vane 3 at the inflow angle α ₁ from the turbine inlet side when the power generation operation is at a low head, whereas the runner vane 3 has a mounting angle. If β ₁ and an angle shift of β ₁ > α ₁ between the inflow angle α ₁ and the mounting angle β ₁ occurs, cavitation CAV is likely to occur on the pressure surface HP side of the runner vane 3. Yes.
[0006]
In addition, during the low power operation of the power generation operation, the inflow water W that flows into the runner vane 3 due to the reduced amount of the inflow water W is affected by the centrifugal force generated during the runner rotation, and the runner band The secondary flow is generated at the outlet side of the runner vane 3, and the secondary flow vortex accompanying the generation of the swirling flow is generated at the outlet side of the runner vane 3, resulting in a decrease in pump turbine efficiency and an increase in hydraulic pulsation.
[0007]
In the Francis type turbine runner, as shown in FIG. 12, the inflowing water W flows into the runner vane 3 at the inflow angle α ₂ from the turbine exit side at the time of the high head of the pumping operation, whereas the mounting angle of the runner vane 3 is If β ₂ and an angle shift of β ₂ > α ₂ occurs between the inflow angle α ₂ and the mounting angle β ₂ , cavitation CAV is likely to occur on the suction surface LP side of the runner vane 3. . In this case, in the Francis turbine runner, when the pressure distributions appearing on the pressure surface HP and the negative pressure surface LP of the runner vane 3 are investigated, the pressure distribution indicated by the broken line in FIG. It was in the cavitation generation area CAVZ.
[0008]
Thus, in the conventional Francis type turbine runner, cavitation CAV is generated in the runner vane 3 at the time of a low head of the power generation operation or at the high head of the pumping operation, and some new improvement measures have been demanded.
[0009]
By the way, considering that one of the factors that cause cavitation CAV is the high load per sheet that the runner vane 3 is responsible for, the Francis-type runner has a runner crown 1 and a runner band 2 as shown in FIG. FIG. 15 shows a so-called splitter-type runner vane 4 that is integrally formed between the two runner vanes 3a having a relatively long blade cord and a spiral runner vane 3a having a long blade cord and an adjacent runner vane 3b. In order to shorten the pitch between the runner vane 3a and the adjacent runner vane 3b, a so-called multi-blade runner vane 5 in which another spiral runner vane 3d having a long blade cord is arranged is disclosed in, for example, Japanese Patent Laid-Open No. 57-126666. , Japanese Utility Model Publication No. 59-11170, Japanese Utility Model Publication No. 61-188486, etc. It has been published in.
[0010]
Of the various characteristics of the splitter-type runner vanes 4 and multi-blade runner vanes 5 published in these publications, as shown in FIG. 16, for example, the pressure distributions appearing on the pressure surface HP and the suction surface LP are as follows. It has been found that the pressure width is narrower than the pressure distribution of the conventional runner vane indicated by the broken line and does not enter the cavitation generation region CAVZ.
[0011]
When the splitter type runner vane 4 and the multi-blade type runner vane 5 are used to examine the PH characteristics (relationship between the turbine output P and the head H) of a so-called real pump / turbine by a model test, a broken line in FIG. It was found that the operating range can be expanded to the cavitation generation limit line shown by the solid line, compared to the cavitation generation limit line using the conventional runner vane shown in. In FIG. 17, Ht _max indicates the maximum head, Ht _nor indicates the reference head, and Ht _min indicates the minimum head.
[0012]
Further, since the HQ characteristic (relationship between the pump head H and the flow rate Q characteristic) is characterized by the mounting angle β _{1 of} the runner vane 3, the outer diameter D _{1 of} the runner vane 3, and the number of runner vanes 3, usually the runner vane If the mounting angle β ₁ of 3 and the outer diameter D ₁ of the runner vane 3 are the same as those of the conventional runner vane, the lift increases by the amount of runner vanes.
[0013]
However, in order to obtain characteristics comparable to those of a conventional pump turbine runner having relatively excellent HQ characteristics, the mounting angle β ₁ of the runner vane 3 is made small. It was also found that the cavitation performance is improved compared to the runner, so that the operating range in the low output region can be expanded when the power generation operation has a low head.
[0014]
As described above, although the splitter type runner vane 4 and the multi-blade type runner vane 5 have excellent performance capable of expanding the cavitation prevention limit, the pump turbine including the splitter type runner vane 4 or the multi-blade type runner vane 5 is incorporated. And practical operation combining a pump turbine incorporating a conventional runner vane has not been found yet.
[0015]
The present invention has been made by paying attention to such points, and by using a pump turbine incorporating a splitter-type runner vane or a multi-blade type runner vane, the limit for preventing cavitation is increased, and the operating range is widened and stable compared to the prior art. It is an object of the present invention to provide a driving method of a pump turbine that can be operated.
[0016]
[Means for Solving the Problems]
As described in claim 1, the operation method of the pump turbine according to the present invention includes a plurality of pump turbines arranged in parallel in a water channel connecting the upper pond and the lower pond, and among the plurality of pump turbines, At least one pump turbine is installed with either a splitter-type runner vane or a multi-blade type runner vane, and during the operation of either one of the low head of power generation operation and the high head of pumping operation, the above A pump turbine incorporating one of a splitter type runner vane and a multi-blade type runner vane is preferentially operated.
[0017]
In order to achieve the above object, the pump turbine according to the present invention includes a splitter type runner vane and a multi-blade type runner vane. In the pumping operation, the pump is operated when the actual water level difference exceeds a predetermined minimum pumping water level difference.
[0018]
In order to achieve the above object, the pump turbine according to the present invention includes a splitter type runner vane and a multi-blade type runner vane. In the power generation operation, the operation is performed when the actual water level difference is lower than a predetermined power generation reference water level difference.
[0019]
In order to achieve the above object, the pump turbine operation method according to the present invention comprises a plurality of pump turbines arranged in parallel in a water channel connecting the upper pond and the lower pond as described in claim 4. Of the plurality of pump turbines, at least one of the pump turbines incorporates either a splitter type runner vane or a multi-blade type runner vane, and the splitter type runner vane and the multi-blade type are incorporated at the time of partial load during power generation operation. One of the runner vanes is to perform a partial load operation on a pump turbine incorporating one of them, and the remaining pump turbine to perform a rated operation, and as a whole perform an operation that satisfies a load adjustment command from the system. Is.
[0020]
In order to achieve the above object, the pump turbine operation method according to the present invention includes a plurality of pump turbines arranged in parallel in a water channel connecting the upper pond and the lower pond as described in claim 5. Of these multiple pump turbines, at least one pump turbine is incorporated with either a splitter type runner vane or a multi-blade type runner vane, and either one of the splitter type runner vane or the multi-blade type runner vane is installed. The built-in pump turbine is equipped with a variable speed gear, and should be operated with priority during either one of the low head of power generation operation, high head of pumping operation, or partial load of power generation operation. It is characterized by.
[0021]
DETAILED DESCRIPTION OF THE INVENTION
DESCRIPTION OF EMBODIMENTS Hereinafter, an embodiment of an operation method of a pump turbine according to the present invention will be described with reference to the drawings and reference numerals attached to the drawings.
[0022]
FIG. 1 is a schematic layout diagram of pump turbines for explaining a first embodiment of the operation method of the pump turbine according to the present invention.
[0023]
In general, in a hydroelectric power plant, a plurality of pump turbines A, B, and C are arranged in parallel at a middle position of a water channel 20 that connects the upper pond 7 and the lower pond 8, and the stored water from the upper pond 7 flows into the lower pond 8 during the daytime. When a plurality of pump turbines A, B, C are driven to generate electricity and the stored water from the lower pond 8 is pumped up to the upper pond 7 at night with surplus power, the plurality of pump turbines A, B, C is driven to perform pumping operation to recycle energy resources.
[0024]
Of the plurality of pump turbines A, B, C, for example, the first pump turbine A is a runner vane, which is a combination of runner vanes 3a, 3b with long blade cords and runner vanes 3c with short blade cords shown in FIG. The multi-blade runner vane 5 in which a large number of runner vanes 3a, 3b, and 3d having long blade cords shown in FIG. 15 or the multi-blade runner vane 5 shown in FIG. 15 is incorporated, and the remaining second pump turbine B and third pump turbine C are the conventional type. The runner vane 6 is incorporated.
[0025]
As shown in FIG. 2, the pump turbine arranged in this manner is subjected to pumping (pump) operation or power generation (turbine) operation based on the calculation signal of the operation control unit 9.
[0026]
The operation control unit 9 includes a head / head calculation unit 11 and a pump turbine operation selection unit 12, and the receiver 10 receives the water level signal Hst1 from the upper pond 7 and the water level signal Hst2 from the lower pond 8 shown in FIG. Then, the head / head calculator 11 calculates the actual water level difference ΔH of the head or head based on the received signal. At this time, when there is an operation command from the system, the operation control unit 9 calculates the pump water turbine operation selection unit 12 based on the actual water level difference ΔH and operates the first pump turbine A or the second pump turbine. Whether to operate B and the third pump turbine C is selected.
[0027]
Further, the pump turbine operation selection unit 12 incorporates the program shown in FIG. 3, and when there is an operation command from the system, either the pumping operation or the power generation operation is selected in the power generation / pumping operation step ST1, for example, When the pumping operation is selected, the above-described head / head calculation is performed on the pumped minimum water level difference H _0p (the water level difference between the upper pond minimum water level Hst1 _min and the lower pond minimum water level Hst2 _min ) determined in the pumping operation determination step ST2. When the actual water level difference ΔH calculated by the section 11 is matched and the actual water level difference ΔH exceeds, the pumping operation is performed on the first pump turbine A incorporating the splitter type runner vane 4 or the multi-blade type runner vane 5 shown in FIG. Let it be done. When the minimum water level difference H _0p determined in advance in the pumping operation determination step ST2 exceeds the actual water level difference ΔH, the pump turbine operation selecting unit 10 incorporates the conventional runner vane 6 shown in FIG. The second pump turbine B and the third pump turbine C are caused to perform a pumping operation.
[0028]
On the other hand, when the power generation operation is selected in the power generation / pumping operation step ST1 in response to the operation command, the pump turbine operation selection unit 12 determines the power generation reference water level difference H _0t (Kamiike's The above-mentioned actual water level difference ΔH is compared with the water level difference obtained by adding the loss H ₁ of the hydraulic iron pipe system to the reference head difference Ht _nor between the water level and the water level of the lower pond, and the actual water level difference ΔH is greater than the power generation reference water level difference H _pt. When it is lower, the first pump turbine A incorporating the splitter type runner vane 4 or the multi-blade type runner vane 5 shown in FIG.
[0029]
In addition, when the actual water level difference ΔH exceeds the predetermined power generation reference water level difference H _0t in the power generation operation determination step ST3, the pump turbine operation selection unit 12 sets the conventional runner vane 6 shown in FIG. The incorporated second pump turbine B and third pump turbine C are caused to perform power generation operation.
[0030]
As described above, in the present embodiment, when the pumping operation is performed at a high head, the first pump turbine A that incorporates the splitter-type runner vane 4 or the multi-blade runner vane 5 that suppresses the occurrence of cavitation CAV is kept low. When the minimum water level difference H _0p exceeds the actual water level difference ΔH, the second pump turbine B and the third pump turbine C incorporating the conventional runner vane 6 are operated, so that the pump turbine runner is stably operated. The pumping operation with high reliability can be realized.
[0031]
Further, in the present embodiment, when the power generation operation has a low head, the first pump turbine A incorporating the splitter type runner vane 4 or the multi-blade type runner vane 5 that suppresses the generation of cavitation CAV is operated, and a predetermined power generation standard is set. When the actual water level difference ΔH exceeds the water level H _0t , the second and second pump turbines B and C incorporating the conventional runner vanes 6 are operated, so that the pump turbine runner can be operated stably. And a highly reliable power generation operation can be realized.
[0032]
By the way, when the amount of cavitation erosion with respect to the operation time was examined, as shown in FIG. 4, the distribution line of the cavitation erosion amount indicated by the solid line in this embodiment is different from the distribution line of the conventional power generation erosion amount indicated by the broken line. Therefore, it was found that the operating time of the cutting allowance limit in the amount of cavitation erosion of the runner of the pump turbine can be extended by about 1.7 times compared with the conventional one.
[0033]
Moreover, it was recognized that the life of the pump turbine runner can be extended by about 2.2 times as compared with the conventional one as the operation time is extended, as shown in FIG.
[0034]
In this embodiment, the first pump turbine A incorporating the splitter-type runner vane 4 or the multi-blade runner vane 5, and the second pump turbine B and the third pump turbine C incorporating the conventional runner vane 6 are provided. Although described as an example of combination, the present invention is not limited to this example. For example, a variable speed pump turbine incorporating a splitter type runner vane 4 or a multi-blade type runner vane 5 and a second runner vane turbine B and a conventional runner vane turbine 6 incorporating a conventional runner vane 6 are used. Three pump turbines C may be combined.
[0035]
Recently, a variable speed machine that can be operated with high efficiency by controlling a winding induction generator with a cycloconverter and changing the rotational speed of the pump turbine runner arbitrarily over a wide range and changing its rotational speed according to the head and head. The variable-speed pump turbine incorporating this is drawing attention.
[0036]
This embodiment pays attention to such points, and the second pump turbine B in which the conventional runner vane 6 is incorporated in the variable speed pump turbine in which the splitter type runner vane 4 or the multi-blade type runner vane 5 is incorporated. The third pump turbine C is combined to improve hydraulic performance.
[0037]
According to the PH (water turbine output-head) characteristic curve during the power generation operation by the model test, as shown in FIG. 6, the first, second and third pump turbines A incorporating the conventional runner vanes 6 are used. , B, and C, when cavitation CAV is generated when the maximum output Pt reaches 50% Pt, the conventional runner vane 6 is added to the first pump turbine A incorporating the splitter type runner vane 4 or the multi-blade type runner vane 5. It was found that when the second pump turbine B and the third pump turbine C incorporating the above are combined, power generation CAV is generated at 37% Pt with respect to the maximum output Pt. Therefore, it was found that the first pump turbine A incorporating the splitter type runner vane 4 or the multi-blade type runner vane 5 can expand the operating range by about 13% compared with the conventional pump turbine A.
[0038]
Further, according to the PH curve of the actual pump / turbine, the cavitation CAV generated when the first, second, and third pump turbines A, B, and C incorporating the conventional runner vane 6 are in the power generation operation and The pump turbine in which the variable speed pump turbine incorporating the splitter type runner vane 4 or the multi-blade type runner vane 5 is combined with the second pump turbine B and the third pump turbine C incorporating the conventional runner vane 6 is in power generation operation. When comparing with the cavitation CAV that occurs at the time, it was found that the pump of the variable speed pump turbine can be expanded by about 20%.
[0039]
Further, according to the PH (pump input-head) characteristic curve during pumping operation by the model test, as shown in FIG. 7, the first, second and third pumps incorporating the conventional runner vanes 6 are used. The second pump turbine B and the second pump turbine B incorporating the conventional runner vane 6 and the variable speed pump turbine incorporating the splitter type runner vane 4 or the multi-blade runner vane 5 and the inflow water reverse flow phenomenon generated by the turbines A, B and C. Comparing with the inflow and backflow phenomenon generated by the pump turbine in which the three pump turbines C are combined, it was found that the pump of the variable speed pump turbine can be expanded by about 3%.
[0040]
FIG. 8 is a schematic operation block diagram of a schematic pump turbine for explaining a second embodiment of the operation method of the pump turbine according to the present invention.
[0041]
In the present embodiment, the first pump turbine A incorporating the splitter type runner vane 4 or the multi-blade runner vane 5 has priority over the second pump turbine B and the third pump turbine C incorporating the conventional runner vane 6. Thus, power generation operation load adjustment is performed.
[0042]
Generally, when the command from the system is a power generation operation and the required output amount Pj from the system is the sum of the maximum outputs of the first pump turbine A, the second pump turbine B, and the third pump turbine C, the operation is performed. The unit issues a 100% output operation command to all pump turbines to operate them.
[0043]
However, when a load adjustment command is issued from the system during the 100% output operation, some of the first pump turbine A, the second pump turbine B, and the third pump turbine C receive an operation stop command. For the remainder, for example, load adjustment of partial load operation with 50% output is often performed.
[0044]
In this case, all the pump turbines A, B, and C incorporating the conventional runner vanes 6 are considered to some extent in consideration of the operation frequency in such partial load operation from the viewpoint of equipment reliability during partial load operation. Although the operation is performed to keep the water pressure pulsation low, there is still a limit, and it is difficult to keep the water pressure pulsation low in the entire operation range.
[0045]
The present embodiment takes such points into consideration. As shown in FIG. 8, when there is a load adjustment command from the system, for example, a required output amount Pj, the operation command unit 13 sends a required output amount Pj to the computing unit 14. Or given. At this time, the arithmetic unit 14 is given a drop ΔH between the water level Hst _{1 of} the upper pond and the water level Hst ₂ of the lower pond detected by the water level detector 15.
[0046]
The calculation unit 14 calculates the load distribution ratio based on the required output amount Pj and the drop ΔH, and the second pump turbine B and the third pump turbine that incorporate the conventional runner vane 6 based on the calculation signal. Let C perform the rated operation, cause the first pump turbine A incorporating the remaining splitter-type runner vanes 4 or multi-blade runner vanes 5 to perform the partial load operation, and perform the operation corresponding to the total required output amount Pj for each pump. Water turbines A, B, C are used. Specifically, the arithmetic unit 14, while the respective guide vanes of the second pump turbine B and the third pump-turbine C (not shown) providing the opening signal X _2, the first pump-turbine A the guide vanes, giving opening signal X ₁ to be the X _2> X _1, the output P ₁ of the output P ₂ and the first pump-turbine a second pump turbine B and the third pump-turbine C And the opening degree of the guide vane is corrected to match the predetermined output of each pump turbine A, B, C.
[0047]
Thus, in this embodiment, when shifting from the rated power generation operation to the partial load power generation operation, the second pump turbine B and the third pump turbine C incorporating the conventional runner vane 6 are rated operation with high turbine efficiency. Since the first pump turbine A incorporating the splitter type runner vane 4 or the multi-blade type runner vane 5 performs the partial load power generation operation and performs the operation satisfying the required output amount Pj from the system as a whole, the cavitation CAV It is possible to cause each of the pump turbines A, B, and C to perform a stable operation with low occurrence of. The first runner pump turbine A incorporating the splitter type runner vane 4 or the multi-blade type runner vane 5 may be a variable speed pump turbine.
[0048]
【The invention's effect】
As described above, the operation method of the pump turbine according to the present invention includes a splitter type runner vane or a multi-blade type runner vane in at least one of a plurality of pump turbines installed in parallel at an intermediate position between the upper pond and the lower pond. In addition, a conventional runner vane is incorporated into the remainder, and a pump turbine with a splitter type runner vane or multi-blade type runner vane is given priority when the head of power generation is low, at the high head of pumping operation, or when adjusting the power generation load. When operating and the inflowing water is stable, a pump turbine incorporating a conventional runner vane is operated to keep cavitation low. Combined with the improvement, the life of the pump turbine runner can be maintained longer than before.
[0049]
In addition, the operation method of the pump turbine according to the present invention includes a variable speed machine for a pump turbine incorporating a splitter type runner vane or a multi-blade type runner vane at the time of a low head of a power generation operation, at a high head of a pumping operation, at the time of adjusting a power generation load. Since the combined variable speed pump turbine is operated preferentially, the operating range can be further expanded as compared with the conventional case, and stable operation can be maintained high.
[Brief description of the drawings]
FIG. 1 is a schematic arrangement of pump turbines for explaining a first embodiment of a method for operating a pump turbine according to the present invention.
FIG. 2 is a schematic operation control block diagram for explaining a first embodiment of a pump turbine operation method according to the present invention.
FIG. 3 is a flowchart incorporated in a pump-turbine operation sorting unit for explaining a first embodiment of a pump-turbine operation method according to the present invention.
FIG. 4 is a cavitation erosion amount distribution diagram comparing conventional and the present invention.
FIG. 5 is a life diagram of a pump-turbine runner that compares the prior art and the present invention.
FIG. 6 is a diagram showing an operation region in which a conventional power generation operation is compared with the present invention.
FIG. 7 is a diagram showing an operation region in which the conventional and the present invention are compared in pumping operation.
FIG. 8 is a schematic operation control block diagram for explaining a second embodiment of the operation method of the pump turbine according to the present invention.
FIG. 9 is a plan sectional view showing a conventional Francis type pump turbine runner.
10 is a half sectional view of FIG. 9;
FIG. 11 is a diagram for explaining cavitation occurring in a runner vane during power generation operation.
FIG. 12 is a diagram for explaining cavitation generated in a runner vane during pumping operation.
FIG. 13 is a distribution diagram of pressure generated in a runner vane at a high head during pumping operation.
FIG. 14 is a plan sectional view showing a splitter type runner vane in which long runner vanes and short runner vanes are combined.
FIG. 15 is a plan sectional view showing a multi-blade runner vane in which a large number of long runner vanes are shortened and arranged.
FIG. 16 is a partial diagram in which a conventional runner vane is compared with a splitter type runner vane or a multi-blade type runner vane.
FIG. 17 is a diagram in which the operating width of a conventional runner vane during water turbine operation is compared with the operating width of a splitter type runner vane or a multi-blade type runner vane.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Runner crown 2 Runner band 3, 3a, 3b, 3c, 3d Runner vane 4 Splitter type runner vane 5 Multi-blade type runner vane 6 Conventional runner vane 7 Upper pond 8 Lower pond 9 Operation control part 10 Receiver 11 Lift / head calculation part 12 Pump Water wheel operation selection unit 13 Operation command unit 14 Calculation unit 15 Water level detector 20 Water channel

Claims (5)

Multiple pump turbines are placed in parallel in the waterway connecting the upper pond and the lower pond,
Of these multiple pump turbines, install at least one of the splitter type runner vane and the multi-blade type runner vane into at least one pump turbine.
At the time of either one of the low head of the power generation operation and the high head of the pumping operation, the pump turbine incorporating one of the splitter type runner vanes and the multi-blade type runner vanes is preferentially operated. A method for operating a pump turbine, characterized by   A pump turbine incorporating one of a splitter type runner vane and a multi-blade type runner vane is operated when the actual water level difference exceeds a predetermined minimum pumped water level difference during pumping operation. Item 2. A method for operating a pump turbine according to item 1.   A pump turbine in which one of a splitter type runner vane and a multi-blade type runner vane is incorporated is operated when the actual water level difference is lower than a predetermined power generation reference water level difference during power generation operation. The operation method of the pump turbine according to claim 1. Multiple pump turbines are placed in parallel in the waterway connecting the upper pond and the lower pond,
Of these multiple pump turbines, install at least one of the splitter type runner vane and the multi-blade type runner vane into at least one pump turbine.
At the time of partial load of power generation operation, let the pump turbine incorporating either one of the splitter type runner vanes or multi-blade type runner vanes perform partial load operation, let the remaining pump turbines perform rated operation, and from the system as a whole An operation method for a pump-turbine characterized by performing an operation that satisfies the load adjustment command. Multiple pump turbines are placed in parallel in the waterway connecting the upper pond and the lower pond,
Of these multiple pump turbines, install at least one of the splitter type runner vane and the multi-blade type runner vane into at least one pump turbine.
Pump turbines that incorporate either a splitter-type runner vane or a multi-blade type runner vane incorporate a variable speed gear, and at the time of low heading of power generation operation, at the high head of pumping operation, or at the time of partial load of power generation operation , A driving method of a pump-turbine characterized by preferential driving during either one of the driving operations.

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