• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to an adjusting device for the impeller blades (2) of turbines (1) with a hydraulic servo cylinder (5). It is primarily characterized in that in addition to the main servo cylinder (5), a further auxiliary servo cylinder (6) is provided, which is arranged opposite the main servo cylinder (5) and whose lever arm (8) offset from the lever arm (7) of the main servo cylinder (5) on the blade lever (9) is arranged. This can also be carried out an adjustment beyond 180 ° and he intervening dead center of the lever (7) of the main servo cylinder (5) are overcome.
    公开号:AT514994A1
    申请号:T853/2013
    申请日:2013-11-07
    公开日:2015-05-15
    发明作者:Stefan Winkler；Erich Wurm
    申请人:Andritz Hydro Gmbh；
    IPC主号:
    专利说明:

    The invention relates to an adjusting device for the impeller blades of turbines with a hydraulic servo cylinder.
    Blade displacement devices are used e.g. used in Kaplan turbines to always achieve the best efficiency at all flow rates. The adjustment range of the blades for single-flow axial turbines is about 30 °. In reversible axial turbines, which are flowed through in both directions, the adjustment range for optimum blade position increases to about 200 °. This is not feasible with the previous solution with a hydraulic servo cylinder, daier in an angular position occurs a dead center, in which the moment arm of the servo cylinder is zero and thus further adjustment can not be realized.
    Alternative solutions exist insofar as on the one hand a symmetrical blade profile with reduced efficiency is selected, on the other hand the adjusting movement is carried out for example by means of toothed racks.
    The aim of the invention is therefore to offer a solution to the adjustment of the blades also for reversible axial turbines.
    This is done according to the invention in that in addition to the main servo cylinder einweiterer auxiliary servo cylinder is provided, which is arranged opposite to the main servo cylinder and whose lever arm offset from the lever arm of the main servo cylinder is arranged on the blade lever. The offset arms of main servo cylinders and auxiliary servo cylinders allow continuous movement and thus adjustment of the blades beyond 180 °.
    An advantageous development of the invention is characterized in that the cylinders of the main servo cylinder and the auxiliary servo cylinder are arranged on a common piston rod. This allows a compact design can be achieved.
    A favorable embodiment of the invention is characterized in that the angle of displacement between the points of engagement of the levers of the main servo cylinder and auxiliary servo cylinder is between 60 ° and 120 °. Thus, the required effort required for adjustment can be optimized particularly well.
    An advantageous embodiment of the invention is characterized in that the auxiliary servo cylinder has a force of between 10 and 30%, preferably about 20% of the main servo cylinder.
    It has proven to be particularly favorable if the auxiliary servo cylinder assumes the blade adjustment in the region of the dead center of the lever of the main servo cylinder, the auxiliary servo cylinder preferably depressurizing the remaining part of the hub. With a low expenditure of energy, the adjustment can thus be carried out over the entire operating range be enabled.
    The invention will now be described by way of example with reference to the drawings, in which Figs. 1 shows a view of a turbine to which the invention is applied,
    2 shows a section through a turbine hub with the inventive arrangement,
    Fig. 3 a to Fig. 3 e shows the sequence of adjustment of the blades.
    Fig. 1 shows a Kaplanlaufrad 1, which in this example has three wings or impeller blades 2, which are rotatably mounted or pivotally attached to the impeller hub 3. This adjustability ensures that the impeller blades 2 are always in the optimum position for optimum efficiency. The position of the impeller blades 2 is thus always adapted to the water flow. Such an impeller 1 can also be used as an axial impeller in pipelines. Here then, in cases of flow reversal, the problem arises that the impeller generally can be optimally designed in terms of efficiency only for one direction of flow. In order to get round this, impeller blade geometries are often chosen here which, although not optimally adapted for the individual flow direction, are adjusted in total in both directions.
    Fig. 2 now shows the adjusting device according to the invention, here only the impeller hub 3 without the corresponding impeller blades is shown. It is also shown for one impeller blade only, although at the same time it is used for all impeller blades, i. in this case for three blades, is performed. In the engine rotation axis, there is a piston rod 4 on which a main servo cylinder 5 is arranged. On the side opposite the hub 3, an auxiliary servo cylinder 6 is disposed. The lever 7 of the main servo cylinder 5 and the lever 8 of the auxiliary servo cylinder 6 are staggered on the blade lever 9 with the blade ring 9 directly connected to the impeller blade 2 (not shown). The staggered point of application of the levers 7 and 9 may include an angle of 90 ° to 120 ° (shown here are about 90 °).
    3 a to 3 e show the positions of the moving blade 2 and of the servo cylinders 5, 6 for different operating states. Around the adjusting device around the hub 3 is arranged, which is lapped in the operating state of water.
    Fig. 3a shows the turbine operation of the reversible axial turbine with minimum blade opening at which the water comes from the left according to arrow 10 and thus the turbine rotates counterclockwise. The point of application of the lever 7 of the main servo cylinder 5 encloses an angle of -110 ° (corresponds to 250 °) against the cylinder axis.
    3 b shows an operating state of the axial turbine in turbine operation with maximum blade opening, in which case the water flow likewise comes from the left according to arrow 10 and the turbine rotates counterclockwise. The water flow is thus from the upper water to the underwater of the power plant. The angle between the point of application of the lever 7 and the horizontal axis is here -70 ° (corresponds to 290 °), wherein the machine axis of rotation is denoted by 11.
    Fig. 3c now illustrates the critical situation in which the lever 7 of the main cylinder 5 has arrived at the dead center and thus can not apply any force for further adjustment of the blade 2. Thus, according to the invention, about 20 ° before and 20 ° after this position, the main cylinder 5 is depressurized and the auxiliary servo cylinder 6 is activated. Due to the staggered arrangement of the points of attack of the levers 7 and 8, the dead center of the main cylinder 5 together with the lever 7 can thus be overcome. Dierestliche time remains the Hilfsservozylinder 6 depressurized and runs only with.
    In Fig. 3 d, then the pumping operation or a turbine operation in the 2nd direction is shown, in which case the water flow as shown by arrow 12 comes from the right and the direction of rotation of the axial turbine is clockwise. With minimum bucket opening according to FIG. 3 d, the angle of the lever 7 of the main servo cylinder 5 to the horizontal axis is + 70 °.
    If the axial turbine is operated in pumping mode or in turbine mode in the second direction with the maximum blade opening, a position results as shown in FIG. 3 e, with an angle of 110 ° and a flow direction from the right according to arrow 12, which leads to a clockwise direction of rotation.
    The angles of the lever 7 to the axis indicated here are exemplary and may also vary slightly. The lever position at maximum and minimum blade opening is dependent on the blade construction. The area around the dead center can also vary, depending on the displacement angle of the points of application of the levers 7 and 8 and the force that can be applied by the auxiliary servomotor 6. It is essential, however, that in this area the main cylinder 5 is switched without pressure and is switched without pressure outside the area of the auxiliary servo cylinder 6.
    权利要求:
    Claims (7)
    [1]
    1. Adjustment device for the impeller blades of turbines with a hydraulic servo cylinder, characterized in that in addition to the main servo cylinder (5), a further auxiliary servo cylinder (6) is provided, which is arranged opposite the main servo cylinder (5) and the lever arm (8) offset from the lever arm (7) of the main servo cylinder (5) on the blade lever (9) is arranged.
    [2]
    2. Adjusting device according to claim 1, characterized in that the main servo cylinder (5) and auxiliary servo cylinder (6) are arranged on a common piston rod (13).
    [3]
    3. Adjusting device according to claim 1 or 2, characterized in that the displacement angle between the engagement points of the levers (7, 8) of the main servo cylinder (5) and auxiliary servo cylinder (6) is between 60 ° and 120 °.
    [4]
    4. Adjusting device according to one of claims 1 to 3, characterized in that the auxiliary servo cylinder (6) has a force of between 10 and 30%, preferably about 20% of the main servo cylinder (5).
    [5]
    5. Adjusting device according to one of claims 1 to 4, characterized in that the auxiliary servo cylinder (6) in the region of the dead center of the lever of the main servo cylinder (5) takes over the blade adjustment and the main servo cylinder (5) is depressurized.
    [6]
    6. Adjusting device according to claim 5, characterized in that the range is about 20 ° before and about 20 ° after the dead center.
    [7]
    7. Adjusting device according to claim 5 or 6, characterized in that the auxiliary servo cylinder (6) is depressurized the remaining part of the stroke.
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    同族专利:
    公开号 | 公开日
    AT514994B1|2017-07-15|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    GB701173A|1951-08-01|1953-12-16|English Electric Co Ltd|Improvements in and relating to operating gear for adjustable propeller type blades in hydraulic turbines or pumps|
    US2951380A|1957-06-18|1960-09-06|Creusot Forges Ateliers|Device for reversing the blades of a turbine|
    EP2444316A1|2010-10-25|2012-04-25|MT-Propeller Entwicklung GmbH|Hydraulic variable pitch propeller|CN110307111A|2019-05-20|2019-10-08|湖南天尚科技有限公司|A kind of water pump water wheels regulating device|NL84649C|1953-10-26|
    DE10139536A1|2001-08-10|2003-02-20|Bosch Rexroth Ag|Hydraulic drive device, in particular for rotor blade adjustment on a wind turbine|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA853/2013A|AT514994B1|2013-11-07|2013-11-07|Adjustment device for the impeller blades of turbines|ATA853/2013A| AT514994B1|2013-11-07|2013-11-07|Adjustment device for the impeller blades of turbines|
    ATA587/2014A| AT515497B1|2013-11-07|2014-07-24|Adjustment device for the impeller blades of turbines|
    PH12014000297A| PH12014000297A1|2013-11-07|2014-10-24|Adjusting device for turbine rotor blades|
    EP14190803.8A| EP2871356B1|2013-11-07|2014-10-29|Actuating device for the impeller blades of a turbine|
    ES14190803.8T| ES2625157T3|2013-11-07|2014-10-29|Adjustment device for the turbine wheel vanes|
    PT141908038T| PT2871356T|2013-11-07|2014-10-29|Actuating device for the impeller blades of a turbine|
    NZ701717A| NZ701717B|2013-11-07|2014-11-06|Adjusting device for turbine rotor blades|
    AU2014259522A| AU2014259522B2|2013-11-07|2014-11-06|Adjusting device for turbine rotor blades|
    CN201410641672.0A| CN104632685B|2013-11-07|2014-11-07|The regulating device of impeller blade for turbine|
    KR1020140154490A| KR102094985B1|2013-11-07|2014-11-07|Adjusting device for turbine rotor blades|
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