• 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:

    公开号:AT510321A1
    申请号:T0141410
    申请日:2010-08-24
    公开日:2012-03-15
    发明作者:Dietmar Dipl Ing Ulm
    申请人:Kba Moedling Ag Maschf；
    IPC主号:
    专利说明:

    1
    The invention relates to a hydraulic motor with an impeller having a hub connected to blades, which is supported by the axis of rotation of the impeller, projecting from opposite end faces of the hub shaft means, and with an electric motor-generator machine, which via a transmission with the shaft means can be coupled.
    From AT 404 973 B and AT 501 575 Al hydroelectric machines in the form of dynamic pressure machines are known in which the impeller is mounted in a channel so that the hub can accumulate the water in the channel. Thus, upstream of the impeller a comparatively high head water level and downstream a low subsea level is obtained. By attached to the hub blades pockets are formed for transporting the water, wherein in operation, the water pressure causes a torque about the axis of rotation of the impeller. The impeller is connected to a generator, which converts the mechanical power of the impeller into an electrical output. The power reduction can be done directly on the impeller shaft; According to AT 501 575 A1, the torque of the impeller is removed by means of a toothed belt on a peripheral guide disk of the impeller. At the end faces of the impeller rigid frame plates are arranged, which have bearings for the impeller.
    If no possibility to compensate for axle or angle errors is provided, a two-sided storage of the impeller of the machine is a static overdetermination. Since the impeller shaft occurring in operation lateral forces can not escape in this case, occur significant constraining forces, which mainly from the camps must be included. However, overloading the bearings can cause damage to the bearings or impeller shaft. Known hydropower machines that can not compensate for axial or angular errors are therefore prone to external influences and have a comparatively high degree of wear.
    Accordingly, the object of the present invention is to provide a hydraulic machine of the type mentioned, which in a constructively simple manner constraining forces - can avoid or compensate at the bearings.
    This object is achieved in the hydraulic motor of the type mentioned in that an end face of the hub is formed by a deformable side wall.
    The deformable, in particular membrane-like side wall of the hub allows an inclination of the waveguide connected to the verformba ren side wall. Accordingly, the shaft means can be offset or tilted in operation by a certain angle relative to the axis of rotation, so that transverse forces introduced into the shaft means are compensated by a deflection of the deformable side wall transversely to its longitudinal extension plane. In addition, axial forces acting on the shaft means can be switched off via deformation of the side wall. Thus, the bearings of the shaft means are spared. If the side wall is elastically deformable, a sensitively responsive to induced forces arrangement is achieved; In addition, it is ensured that the side wall returns to its original position after a momentary load peak. Due to the deformable design of the side wall, the impeller can wobble during operation, whereby the constraining forces occurring are minimized. Thus, only comparatively weak constraining forces are transmitted to the bearings assigned to the shaft means, so that the wear of the system in continuous operation can be significantly reduced. In addition, damage to the shaft means due to plastic deformation of the shaft means causing loads is prevented. The hydropower machine is thus much less sensitive ge compared to external influences and mounting or adjustment tolerances.
    To achieve a structurally simple, partially-saving design, it is advantageous if the deformable side wall is connected to a provided for torque transmission to the gear shaft stub, the element in a rigid transmission, in particular a hollow shaft of the transmission is stored. The stub shaft is non-rotatably connected to the particular designed as a hollow shaft gear member which is mounted in suitable storage means. The transmission has translation means, for example gearwheels, which provide for a suitable gear ratio of the speed supplied by the shaft element in.... * * * * * * Λ - 3 - * * * ♦ an appropriate for the operation of the motor-generator-machine higher speed are set up. This embodiment has the advantage that on the transmission side, a separate bearing for the stub shaft can be saved. The integration of the bearing means in the transmission, a structurally simple construction can be realized with relatively low production costs. The deformable side wall of the hub ensures that constraining forces are weakened or avoided on the rigid transmission element via elastic deformation of the side wall.
    In order to ensure the required stability of the hydraulic motor during operation, it is favorable if the deformable side wall opposite end face of the hub is formed by a substantially rigidly arranged during operation side wall. Thus, each one (elastically) deformable and a rigid side wall are arranged on the front sides of the hub, in order to obtain a responsive to the axis and angular displacements occurring during operation arrangement, without affecting the stability of the water engine as a whole.
    In order to be able to compensate for a misalignment of the shaft means as a result of forces occurring during operation on the end opposite the transmission of the hub, it is advantageous if a connected to the rigid side wall stub shaft is mounted in a self-aligning bearing.
    In order to ensure the rigidity of the side wall during operation, it is advantageous if the rigid side wall with stiffening elements, in particular stiffening angles, is connected. To increase the rigidity of the side wall, alternatively or additionally, a wall thickness increased relative to the deformable side wall may be provided.
    Conveniently, the deformable side wall is formed by a metal sheet, in particular a steel sheet, which preferably has a thickness (thickness) of between 2 mm and 15 mm. The thickness of the steel sheet depends on the dimensions of the hydroelectric power plant, with a wall thickness of 6 mm to 15 mm being expedient for impeller diameters of more than 1 × 4 × m. For smaller wheels with a diameter of 0.5 m to 1 m wall thicknesses of 2 mm to 6 mm have been found to be advantageous.
    For the transmission of forces between the shaft means and the side walls of the hub, it is favorable if on the side walls comparatively small fastening plates are mounted, which are fixed to the respective stub shaft, e.g. by positive engagement and welding, are connected. The non-rotatable connection between the stub shafts and the mounting plates can generally be done in a positive or non-positive manner. The mounting plates are preferably rigid. On the deformable side wall bending zones are formed in particular all around the rigid mounting plate, which are in operation to compensate for dislocations of the shaft means transversely to the longitudinal extension plane of the side wall bendable.
    For supporting the impeller, it is advantageous if the transmission is fastened by means of an adapter device to a bearing frame comprising the impeller. The adapter device may in particular have attached to lateral frame parts Anschraubhülsen which are preferably connected to a in operation, the generator-gear unit bearing adapter bar. Preferably, the adapter bar has free attachment points, which can serve to adapt to different types of transmission.
    According to a preferred embodiment of the invention, the impeller for operation of a ram-pressure machine during operation defines a water level height as the difference between an upper water level and an underwater level. The preferably over the entire width of a channel arranged ram pressure machine forms a weir, which dammed the channel with the specified water level height.
    The invention will be explained below with reference to illustrated in the drawings, particularly preferred embodiments, to which, however, it should not be limited. Specifically, in the drawing: * φ f Φ Φ * Φ I Φ · «* * * * * * * #
    Fig. 1 is a perspective view of an impeller of a hydraulic machine designed as a dynamic pressure machine;
    Fig. 2a is a perspective view of a hydraulic motor with the impeller shown in Figure 1, viewed from the underside.
    2b is a perspective view of the hydraulic engine of Figure 2a from the upstream side, wherein the attachment of the motor-generator machine is visible on a bearing frame.
    Fig. 3 is a side view of the hydraulic machine illustrated in Figs. 1 and 2;
    Fig. 4 is a sectional view of the hydropower machine along the line A-A in Fig. 3, from which the axis of rotation of the impeller defining shaft means in the manner of stub shafts are visible;
    Fig. 5 is a detail view of detail B illustrated in Fig. 4 with a circle showing the mounting of a shaft stub for torque transmission on the motor-generator machine in a hollow shaft of the transmission;
    Fig. 6 is a detail view of the detail C illustrated in Fig. 4 with a circle showing the bearing of the opposite stub shaft in a self-aligning bearing; and
    Fig. 7 is a front view of the hydropower machine, from which the deflection of a deformable side wall of the impeller hub connected to the transmission-side stub shaft can be seen schematically. FIG. 1 diagrammatically illustrates an impeller 1 for a hydraulic machine 2 designed as a dynamic pressure machine, this impeller 1 being intended for storage in a bearing frame 3 (FIGS. 2a, 2b). The impeller 1 according to FIG. 1 has a cylindrical hub 4 whose axis of rotation x-x extends through from FIG.
    • * * * * * * # ** I «♦« · * * · «* * · # ·« · »# - 6 - 4 until Fig. 7 shows a stubby shaft means 5. The end faces of the hub, 2 '> egrenzen the width of the rotor or impeller 1 and seal the impeller 1 in the bearing frame 3 from.
    At the periphery of the wheel hub 4 are further suitably shaped blades 6, e.g. welded to form bags for water transport, i. to absorb the water pressure and to cause a torque about the wheel axis x-x. The vanes 6 of the impeller 1 may have, in addition to the V-shaped arrangement shown, other arrangements, such as simple oblique arrangements (see, for example, AT 404 973 B), and may also have a curvature depending on the objective.
    In Fig. 2a is a dynamic pressure water engine 2 with such an impeller 1, as shown in Fig. 1, seen from the underside seen schematically illustrated. The impeller 3, in operation, determines a water level height as the difference between an upstream headwater level and a downstream underwater level; the dynamic pressure machine 1 can be arranged across the width of a channel to accumulate the channel with the specified water level. For example, according to FIG. 2a, the impeller 1 is mounted in a bearing frame 3 having a generally rectangular shape, which according to FIGS. 2a and 2b has two vertical supports 7, 8 and a lower support 9 and an upper support 10 around the impeller 1 is formed around. The carriers 7 to 10 are preferably formed from rectangular in cross-section mold tubes.
    The impeller 3 is coupled to an electric motor-generator machine 11. In generator operation, the braking torque of the motor-generator machine 11 is used to convert the kinetic energy of the impeller 1 into electrical energy. The motor-generator machine 11 has a transmission 12, with which the speed of the impeller 1 supplied by the shaft means 5 is converted into a higher speed for the electric generator.
    FIG. 2 b shows the hydraulic engine 2 seen from the side of the motor-generator machine 11. The vertical support 8 of the - 7 - • *
    Bearing frame 3 has an adapter device 14 with attached to the carrier 8, in particular screwed adapter sleeves 15 which are connected to a mounted on the motor-generator machine 11 adapter bar 16, in particular screwed. The adapter device 14 allows an exact adjustment of the motor-generator-machine 11 and the transmission 12; In addition, the adapter strip 16 is compatible with different types of gear depending on the application.
    As can be seen from FIGS. 4 to 7, the shaft means 5 carrying the impeller 1 are formed by stub shafts 17, 17 ', which in each case project outwards from the end faces of the hub 4 in the axial direction. The stub shafts 17, 17 'are fixedly connected to mounting plates 18, which are fixedly attached to the end faces of the hub 4. For rotatably supporting the shaft stub 17, 17 'bearing means 19 are provided, which are arranged on both sides of the hub 4. The bearing means 19 are supported via the adapter device 14 by the vertical support 8 or by a projecting bracket 13 from the vertical support 7 of the bearing frame 3. The shaft stub 17 is used for torque transmission from the impeller 1 to the transmission 12, which translates the speed supplied by the shaft stub 17 in an appropriate for the operation of the motor-generator machine 11 speed. For this purpose, the transmission 12 has gear means not shown in detail, which may be formed for example by cooperating gears.
    As can be seen in detail from FIG. 5, the bearing means 19 which supports the transmission-side stub shaft 17 is formed by a hollow shaft 20 which is arranged in the gear 12 and which is non-rotatably connected to the stub shaft 17 via a positive, frictional or non-positive connection. Accordingly, provided for supporting the stub shaft 17 bearing means 19 in the transmission 12 and in the motor-generator-machine 11 is integrated; The motor-generator-machine 11 thus simultaneously acts as a drive and bearing unit. Advantageously, accordingly, a separate bearing for the transmission-side stub shaft 17 can be saved.
    As can be seen from FIG. 6, the bearing means 19 are in contact with the bearing means 19 at the end of the "* I" "* *" "* * * * I *" * * * * * * * * * * * * 9 * * - 8 -
    Gear 13 opposite end face of the hub 4 is formed as a pendulum bearing 21, which allows a misalignment of the shaft stub 17 'mounted therein. The self-aligning bearing 21 has, in a manner known per se, an outer ring 22 and an inner ring 23, between which a rolling element 24 is rotatably mounted.
    The mounted on opposite end faces of the hub 4 bearing means 19 allow stable support of the impeller 1, but have over a cantilevered, cantilevered impeller 1 on the disadvantage of a static ÜberbeStimmung on. The rotatably connected to the hub 4 shaft means 5 are constantly exposed during operation in the direction of the axis of rotation or transversely acting forces which cause 19 constraining forces in the bearing means. In the event of an overload, damage to the storage means 19 or the associated components which may necessitate maintenance or repair of the installation threatens; At least in continuous use a considerable amount of wear would be recorded. In order to avoid these adverse effects, the constraining forces acting on the bearing means 19 during operation should be minimized.
    This is achieved, on the one hand, by the fact that the self-aligning bearing 21 can compensate the resulting constraining forces by means of a corresponding inclination of the shaft element 17 '. On the other hand, the integrated in the transmission 12 hollow shaft 20 which supports the stub shaft 18, a high flexural rigidity, the constraining forces can not yield by deformation. In order to reduce the pressure in the transmission side bearing means 19, i. the hollow shaft 20 of the transmission 12 to be able to compensate for the resulting constraining forces as far as possible, with the provided for transmitting torque to the gear 12 stub shaft 17 end face of the hub 4 is formed by an elastically deformable side wall 25.
    FIG. 7 schematically illustrates how the elastic side wall 25 of the hub 4 is bent in a membrane-like manner during operation transversely to its longitudinal extension plane, in order to obtain an angular offset of the shaft element 17, i. a " tumbling " Movement of the impeller to allow which or which largely eliminates the constraining forces occurring in the hollow shaft 20. The < I * * I * * # I * * «*« »· · II * f · • t» * »« t · ft. »It *« «* * * *« «« «« «* *« · ·· «- 9 -
    Deflection of the deformable side wall 25 is exaggerated in FIG. In operation, a comparatively small deformation of the side wall 25 is sufficient to compensate for the transverse forces on the stub shaft 17. For the compensation of constraining forces as low bending stiffness of the side wall 25 is advantageous, but on the other hand, on the other hand must withstand the forces occurring during operation in the long run. For forming the elastically deformable side wall 25, a metal sheet, preferably a steel sheet, e.g. from mild steel, in particular with a thickness of about 8 mm used.
    As further seen in Fig. 7, the deformable side wall 25 opposite end face of the hub 4 may be formed by a substantially rigid in operation side wall 26; the compensation of the constraining forces is achieved here via the inclination of the shaft member 17 'in the self-aligning bearing 21. To increase the flexural rigidity, the rigid side wall 26 is connected to stiffening angles 27.
    权利要求:
    Claims (9)
    [1]
    1. A hydraulic machine (2) having an impeller (1) which has a hub (4) connected to blades (6), forming from the rotational axis of the impeller (1), from opposite end faces of the hub (4). protruding shaft means (5) is worn, and with an electric motor-generator machine (11) via a transmission (12) with the shaft means (5) can be coupled, characterized in that a front side of the hub (4) by a deformable side wall (25) is formed.
    [2]
    2. Hydropower machine (2) according to claim 1, characterized in that the deformable side wall (25) with a torque transmission to the transmission (12) provided for shaft stub (17) is connected, in a rigid transmission element, in particular a hollow shaft ( 20) of the transmission (12) is mounted.
    [3]
    3. Hydropower machine (2) according to claim 1 or 2, characterized in that the deformable side wall (25) opposite end face of the hub (4) is formed by a substantially rigid during operation side wall (26).
    [4]
    4. Hydropower machine (2) according to claim 3, characterized in that one with the rigid side wall (26) connected to the stub shaft (17 ') is mounted in a self-aligning bearing.
    [5]
    5. Hydropower machine (2) according to claim 3 or 4, characterized in that the rigid side wall (26) with stiffening elements, in particular stiffening angles (27) is connected.
    [6]
    6. Hydropower machine (2) according to one of claims 1 to 5, characterized in that the deformable side wall (25) is formed by a metal sheet, in particular a steel sheet, which preferably has a thickness of between 2 mm and 15 mm.
    [7]
    7. Hydropower machine (2) according to one of claims 2 to 6, characterized in that on the side walls (25, 26) comparatively small mounting plates (.18) are mounted, • * * * * * * * * * * 4 < ♦ · · · · · - - - mit - which are connected to the respective stub shaft (17, 17 ').
    [8]
    8. Hydropower machine (2) according to one of claims 1 to 7, characterized in that the transmission (12) by means of an adapter device (14) on a bearing wheel comprising the bearing frame (3) is fixed.
    [9]
    9. hydraulic machine (2) according to one of claims 1 to 8, characterized in that the formation of a dynamic pressure machine, the impeller (1) defines a water level height during operation as the difference between an upper water level and an underwater level.
    类似技术:
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    同族专利:
    公开号 | 公开日
    WO2012024705A1|2012-03-01|
    EP2609323A1|2013-07-03|
    AT510321B1|2019-08-15|
    EP2609323B1|2014-01-22|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE4313509A1|1992-08-10|1994-02-17|Thomas Dipl Ing Guenther|Water power generation plant - has water-wheel bolted onto gearbox input shaft flange with gearbox casing bolted to strut on wall|
    AT501575A1|2005-12-27|2006-09-15|Brinnich Adolf|HYDRO POWER JAM PRESS|
    DE102009029794A1|2008-06-23|2010-01-14|Christoph Hermesmeier|Water wheel for producing potential energy between back water and under water in retaining dam, has locking shoe protruding with sweep-angle in direction of motion of paddles in arrow shaped manner|
    DE4313905A1|1993-04-28|1994-11-03|Joerg Fricke|Braille display device|
    AT404973B|1997-04-01|1999-04-26|Brinnich Adolf|HYDROPOWER PRESSURE MACHINE|
    WO2004109098A1|2003-06-06|2004-12-16|Harry Pisek|Mobile river power stations|
    WO2008012067A2|2006-07-24|2008-01-31|Johann Hoffmann|Hydroelectric device for a water power installation|
    GB0710318D0|2007-05-30|2007-07-11|Isis Innovation|Water turbine|US9698650B2|2014-06-02|2017-07-04|Regal Beloit America, Inc.|Electric device, gearbox and associated method|
    DE102020112681A1|2020-05-11|2021-11-11|Georg Bachsleitner|Rotating device|
    法律状态:
    2020-04-15| MM01| Lapse because of not paying annual fees|Effective date: 20190824 |
    优先权:
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    ATA1414/2010A|AT510321B1|2010-08-24|2010-08-24|HYDRO POWER JAM PRESS|ATA1414/2010A| AT510321B1|2010-08-24|2010-08-24|HYDRO POWER JAM PRESS|
    PCT/AT2011/000332| WO2012024705A1|2010-08-24|2011-08-03|Water power engine|
    EP11743765.7A| EP2609323B1|2010-08-24|2011-08-03|Water power engine|
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