• 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 impeller blade for a hydraulic fluid machine, turbine, pump or pump turbine consisting of a hub and the impeller blades without outer ring, wherein the impeller blades are rotatably or fixedly secured to the hub and have a bar on the outer diameter. It is primarily characterized in that the bar has a variable height, wherein the height of the bar is larger following the leading edge and then goes back to a nearly constant height. The invention also relates to a Antikavitationsleiste for an impeller blade of a hydraulic fluid machine, which has a variable height, wherein the height of the bar is larger following the leading edge and then goes back to a nearly constant height. The greater height of the ledge at the beginning allows the cavitating vortex to be displaced away from the impeller blade and the anti-cavitation ledge into free space, greatly reducing cavitation damage.
    公开号:AT518291A1
    申请号:T50143/2016
    申请日:2016-02-26
    公开日:2017-09-15
    发明作者:WEISSER Marco；Keller Markus；WALLIMANN Henrik；FISCHER Pascal；Sallaberger Manfred
    申请人:Andritz Hydro Gmbh；
    IPC主号:
    专利说明:

    Impeller blade of a hydraulic fluid machine with anti-cavitation bar and anti-cavitation bar for an impeller blade
    The invention relates to an impeller blade of hydraulic turbomachines, turbines, pumps or pump turbines consisting of a hub, the impeller blades without outer ring. The impeller blades may be rotatably or fixedly secured to the hub and have at the outer diameter of a bar / lip.
    Hydraulic turbomachines generally have an impeller equipped with a number of blades for energy transfer. These impeller blades may be fixedly or rotatably connected to the hub and may be constructed with or without the outer rim. For wheels without outer ring a bar / lip can be attached to the outer diameter.
    With the help of adjustable vanes, the flow of water and thus the power is regulated or completely closed. The flow direction may be radial, axial or diagonal. The impeller blades may be rotatably connected via a pin to the hub and have an adjustable position. This allows the turbine to be adapted to different load conditions in such a way that optimum efficiency is always achieved. The most common type of turbine with adjustable impeller blades is a Kaplan turbine in which the pegs of the impeller blades are mounted perpendicular to the shaft.
    It follows that for each operating point of the turbine plant there is an optimal opening of the vanes and an optimal position of the impeller vanes in order to maximize the energy generated with the amount of water present. There is a gap between the impeller blade and the surrounding impeller shell, which leads to loss of water. In the flow through this gap, it also leads to vortex formation. In the vortices, vapor pressure and thus cavitation can occur and cause cavitation damage to surfaces. In order to improve the cavitation behavior, many different forms of impeller blades have been devised, e.g. in US 5,226,804 an impeller blade having an enlarged area at the inlet edge. Also, there is the possibility of attaching a bar on the outer diameter of the impeller blade called Kavitationsleiste or Antikavitationleiste, in order to reduce the flow through the gap and thus the vortex formation and cavitation damage.
    However, well-known anti-cavitation bars can not completely solve the problem. Thus, the invention has set itself the task of an impeller blade of a hydraulic
    To create turbomachine with a Antikavitationleiste, which significantly reduces the Kavitationsschaden.
    The invention is therefore characterized in that the bar has a variable height, wherein the height of the bar is larger following the leading edge and then goes back to a nearly constant height. Under variable height is understood to mean a different height over the length of the bar. The greater height of the ledge at the beginning allows the cavitating vortex to be displaced away from the impeller vane and groin into free space, greatly reducing cavitation damage.
    A favorable embodiment of the invention is characterized in that the bar is integrated with the impeller blade, welded orangeschraubt.
    An advantageous development of the invention is characterized in that a number of inserts of cavitation-resistant material in the strip is then arranged on the first higher part, wherein the inserts can be welded or screwed to the impeller blade. These inserts greatly extend the life of the impeller blade and anti-cavitation bar. Such inserts may e.g. made of stainless steel, e.g. X 5 CrNi 13.4, or particularly cavitation resistant metals (eg, strain hardenable stainless austenitic iron-based alloys or cobalt-chromium-tungsten alloys), and are secured to the impeller vane by welding or screwing. Thus, these inserts can be replaced at regular intervals without affecting the impeller blade and thus the efficiency and performance of the hydraulic machine, such as turbine.
    The invention also relates to a Antikavitationsleiste for an impeller blade of a hydraulic turbomachine hub, to which the impeller blade is rotatably or firmly attached, wherein the Antikavitationleiste is arranged on the outer diameter of the impeller blade. It is characterized in that the Antikavitationleiste has a variable height, wherein the height of the bar is larger following the leading edge and then goes back to a nearly constant height. The greater height of the ledge at the beginning allows the cavitating vortex to be displaced away from the impeller blade and the anti-cavitation ledge into free space, greatly reducing cavitation damage.
    A favorable development of the invention is characterized in that further parts are provided with greater heights over the length of the Antikavitationleiste. This allows the turbulence streams along the edge of the impeller blade to be moved away from the edge into free space, virtually eliminating cavitation damage.
    An advantageous embodiment of the invention is characterized in that a number of inserts of cavitation-resistant material in the strip is then arranged on the part or parts with a greater height. These inserts greatly extend the life of the impeller blade and anti-cavitation bar.
    A favorable embodiment of the invention is characterized in that the inserts are welded to the blade, wherein they can also be screwed to the blade. As a result, these inserts can be replaced at regular intervals without affecting the impeller blade and thus the efficiency and performance of the turbine. Such inserts may e.g. made of stainless steel, e.g. X 5 CrNi 13.4, or particularly cavitation resistant metals (for example, strain hardenable stainless austenitic iron-based alloys or cobalt-chromium-tungsten alloys).
    The invention will now be described by way of example with reference to the drawings, in which:
    Fig. 1 is an overview of a Kaplan turbine as an example of a hydraulic turbomachine
    2 a flow channel with an impeller blade,
    3 shows an impeller blade with anticavitation strip according to the prior art,
    4 shows an impeller blade with a variant of an anti-cavitation strip according to the invention, FIG. 5 with an alternative variant according to the invention, and FIG. 6 shows a variant of the invention with inserts in the anti-cavitation strip.
    FIG. 1 shows an overview of a turbine installation using the example of a Kaplan turbine 1 as an example of a hydraulic turbomachine. The Kaplan turbine 1 has an impeller 2 which rotates about the axis 4 under the force of the incoming water 3. The impeller is fixed to a shaft 5, which is connected to a generator 6. Via a pressure pipe 7, the water of a spiral 8 is supplied, which supplies the water flow 3 via a stator with guide vanes 9 to the impeller 2 of the turbine 1. The guide vanes 9 can in each case be designed to be rotatable about an axis 10 in order to be able to regulate the flow of water well. Following the impeller 2 of the turbine 1 is a suction pipe 11 through which the water is supplied to a river or another underwater. The impeller has a hub 12 and a number of impeller blades 13, here four impeller blades are shown on. The impeller blades 13 are rotatably attached to the hub 12 by means of a flange 14. Thus, by the rotation of the impeller blades 13, an optimal performance of the turbine 1 can be achieved.
    Fig. 2 shows the flow channel for an impeller blade 13 which is fixed to the hub 12. Starting from the spiral 8, the water flows through the channels 15 between the guide blades 9. At the outer diameter of the impeller blade 13 is a Antikavitationsleiste 16 to see the prior art.
    In Fig. 3, an impeller blade 13 is shown with a flange 14. Here, the leading edge 17 of the impeller blade 13 and the trailing edge 18 of the impeller blade 13 can be seen, as well as the pressure side 19 and the suction side 20. In the region of the outer diameter of the impeller blade on the suction side 20 a Antikavitationleiste 16 is mounted according to the prior art. The leading edge of the strip 16 here has an angle of approximately 30 °. The cavitation damage is here, in the middle between the leading edge 17 and the exit edge 18 of the impeller blade 13 on the anti-cavitation particularly pronounced.
    Fig. 4 shows an impeller blade 13 with a Antikavitationsleiste 16 'according to the invention. The impeller blade again has an inlet edge 17, an outlet edge 18 and a pressure side 19 and suction side 20. The Antikavitationleiste 16 'is shown here in section. It can be seen starting from the leading edge 17 of the impeller blade 13 is a very flat leading edge 21 of the Antikavitationleiste 16 'of about 10 ° - 60 ° (shown about 20 °) and then an inflated part 22, which is about 10% - 45% of Length of Antikavitationleiste 16 'makes up. Shown is a length of about 20 - 25% of the total length of the bar. Subsequently, the height of the anti-cavitation bar 16 'returns to its original height. The height of the portion 22 projecting beyond the remainder of the anti-cavitation bar may amount to approximately 30-120% of the height (represented by approximately 75%) of the anti-cavitation bar 16 ', i.e., approx. the total height of the elevated part 22 is about 130-220% of the height of the anti-cavitation bar 16 '. The Antikavitationleiste 16 'can be molded to the impeller blade 13, be welded orangeschraubt. When manufacturing the impeller blade 13, the part of the Antikavitationleiste 16 'mitgegossen and milled out accordingly. As soon as major damage has occurred due to cavitation, the anti-cavitation bar is replaced and a new anti-cavitation bar 16 'is welded or screwed to the impeller blade 13. The over-inflated portion 22 displaces the cavitating vortex away from the impeller vane and anti-cavitation shelf, thereby greatly reducing cavitation damage to the anti-cavitation bar 16 'and impeller vane 13 in the critical area.
    In Fig. 5, a further variant of the invention is shown. As in the variant according to FIG. 4, the anti-cavitation strip 16 "has an entry edge 21 which has an angle of approximately 10 ° -60 ° (shown approximately 20 °). Subsequently, a plurality of regions 22, 22 'and 22 "are provided which cause an elevation, i. greater height than the height of the anti-cavitation strip per se, wherein the elevation in the individual parts 22, 22 ', 22 "is equal or different in size. Thus, it is shown here that the elevation of the second part 22 'is greater than that of the first part 22 and that of the third part 21 "less than that of the first part 22. Thus, the particular conditions of cavitation and the severity of cavitation damage particularly well taken into account in the different places.
    Fig. 6 shows a variant of the invention of a Antikavitationsleiste 16 'with a higher portion 22 at the beginning and with inserts 23, 23', 23 ", 23 '", 23 ^ which are then arranged on the higher part 22. This is followed by another part of the anti-cavitation bar 16 '. The inserts 23, 23 ', 23 ", 23'", 23lv are therefore an integral part of the Antikavitationleiste. They can be welded to the position, but also screwed there and can thus be replaced at regular intervals without the impeller blade 13 and thus affect the efficiency and performance of the hydraulic turbomachine, such as turbine. The inserts 23, 23 ', 23 ", 23", 23lv can, depending on the position and stress by the Kavitationskräfte from the same cavitation resistant material such. stainless steel, e.g. X 5 CrNi 13.4, or particularly cavitation-resistant metals (for example, work hardening stainless austenitic iron-based alloys or cobalt-chromium-tungsten alloys) or consist of different materials to account for the different cavitation conditions. The Antikavitationleiste 16 'here has a very flat entrance edge 21 of about 10 ° - 60 ° (shown about 20 °) and then an inflated part 22, which accounts for about 10% - 45% of the length of the Antikavitationleiste 16'. Shown is a length of about 20 - 25% of the total length of the bar. Subsequently, the height of the anti-cavitation bar 16 'returns to its original height. The height of the portion projecting beyond the remainder of the anti-cavitation bar may be approximately 30-120% of the height (represented by approximately 75%) of the anti-cavitation bar 16 ', i.e., approx. the total height of the elevated part 22 is about 130-220% of the height of the anti-cavitation bar 16 '. Fig. 6 shows an impeller blade 13 in contrast to Figs. 4 and 5 from the bottom (suction side 20) in order to show the Antikavitationleiste 16 'better. The viewer facing side is therefore the part of the impeller sch on egg 13, which lies on the hub side.
    权利要求:
    Claims (10)
    [1]
    claims
    1. Impeller blade for a hydraulic fluid machine, turbine, pump or pump turbine consisting of a hub and the impeller blades without outer ring, wherein the impeller blades are rotatably or fixedly secured to the hub and the outer diameter of a bar, characterized in that the strip (16 ' ) has a variable height, wherein the height (22) of the strip (16 ') following the leading edge (21) is greater and then goes back to a nearly constant height.
    [2]
    2. impeller blade according to claim 1, characterized in that the strip (16 ') with the impeller blade (13) integrated, welded orangeschraubt.
    [3]
    3. impeller blade according to claim 1 or 2, characterized in that the first higher part (22) then a number of inserts (23, 23 ', 23 ", 23", 23% cavitation resistant material in the strip (16') is arranged.
    [4]
    4. impeller blade according to claim 3, characterized in that the inserts (23, 23 ', 23 ", 23", 23 ^ welded to the impeller blade (13).
    [5]
    5. impeller blade according to claim 3, characterized in that the inserts (23, 23 ', 23 ", 23'", 23 ^ with the impeller blade (13) are screwed.
    [6]
    An anti-cavitation blade for an impeller blade of a turbine with a hub to which the impeller blade is rotatably or fixed, the anti-cavitation blade being disposed on the outer diameter of the impeller blade, characterized in that the anti-cavitation blade (16 ') has a variable height, the height ( 22) of the strip (16 ') after the leading edge (21) is larger and then goes back to a nearly constant height.
    [7]
    7. Antikavitationleiste according to claim 6, characterized in that the bar (16 ') with the impeller blade (13) integrated, welded or screwed.
    [8]
    8. Antikavitationleiste according to claim 6, characterized in that further parts (22 ', 22 ") are provided with greater heights over the length of the Antikavitationleiste (16').
    [9]
    9. anti-cavitation bar according to one of claims 6 to 8, characterized in that the part (22) or the parts (22 ', 22 ") having a greater height then a number of inserts (23, 23', 23", 23 '", 23 of cavitation resistant material in the bar (16') is arranged.
    [10]
    10. Antikavitationleiste according to claim 9, characterized in that the inserts (23, 23 ', 23 ", 23'", 23 welded to the impeller blade (13) or screwed.
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    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US5525269A|1985-03-22|1996-06-11|Philadelphia Gear Corporation|Impeller tiplets for improving gas to liquid mass transfer efficiency in a draft tube submerged turbine mixer/aerator|
    JPS6254280U|1985-09-25|1987-04-03|
    DE19707168A1|1996-03-28|1997-10-02|Voith Hydro Gmbh|Hydraulic turbine with adjustable rotor blades and screened gaps|
    JP2005315216A|2004-04-30|2005-11-10|Toshiba Corp|Axial flow water turbine|
    JP2007291874A|2006-04-21|2007-11-08|Toshiba Corp|Axial flow hydro-turbine runner|
    EP2711557A2|2012-09-20|2014-03-26|Sulzer Pumpen Ag|An impeller for a centrifugal pump|
    WO2014202485A1|2013-06-21|2014-12-24|Alstom Renewable Technologies|Hydraulic machine, self-adjusting device and hydraulic energy conversion installation|CN111706454A|2020-06-03|2020-09-25|浙江富春江水电设备有限公司|Passive blade anti-cavitation structure for axial-flow Kaplan turbine|EP2987956A1|2014-08-18|2016-02-24|Siemens Aktiengesellschaft|Compressor aerofoil|
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