• 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:AT510320A1
    申请号:T0141310
    申请日:2010-08-24
    公开日:2012-03-15
    发明作者:Andreas Mag Sternecker
    申请人:Kba Moedling Ag Maschf；
    IPC主号:
    专利说明:

    The invention relates to a hydro-dynamic pressure machine with at least one rotatably mounted in a frame impeller, which has a hub and associated blades, and which defines in operation a water level as the difference between an upper water level and an underwater level, and one with the impeller via a Gearbox coupled electric motor-generator-machine.
    Hydropower dynamic pressure machines are known from AT 404 973 B and AT 501 575 Al. The impeller is arranged transversely to the flow direction in a channel. The hub of the impeller can replace a weir, which in hydraulic engineering is understood to mean a reservoir that closes off a flow region. Depending on the design weirs can be overflowed or flowed through as needed, the section of the channel in the direction of flow above the weir as upper water and the section of the channel below the weir is referred to as underwater. In the past, weirs with low stowage heights were only provided for damming water as required; Starting from this it was proposed in AT 404 973 B or AT 501 575 A1 to use the dynamic pressure for energy generation. For this purpose, the inflowing water drives the blades of the impeller, which is connected to the motor-generator machine. In generator operation, a braking torque is built up, and there is a conversion of the mechanical power into an electrical useful power, which is supplied to an energy storage or fed into a power grid. This type of hydro-electric machine has the advantage that the generator is driven by the pressure of the flowing water. Accordingly, both the flow velocity of the channel and the potential level corresponding to the water level are used to generate energy in the sense of high efficiency with high absorption capacity.
    The output power and the achievable efficiency depend i.a. from the upper water level, i. from the upstream water level of the channel relative to the hub of the impeller. The headwater level affects the amount of water available to drive the impeller. It has already been proposed (see http://de.wi-kipedia.org/wiki/Staudruckmaschine and the previously unpublished earlier application AT A 1195/2010), the upper water level
    - 2 - in order to continuously adjust the current upper water level to the upper water level setpoint.
    More specifically, in a dynamic pressure machine, the amount of water flowing from the upper water through the system into the underwater per unit of time, usually called the intake capacity, depends on the speed of the impeller. Since the water flow is expediently not offered a possibility to avoid the impeller arranged across the entire channel, the entire water flows through the dynamic pressure machine. At a high speed of the impeller is a high absorption capacity of the dynamic pressure machine, with a larger amount of water is transported by the blades to the underwater side and thus the head water level is reduced; conversely, reducing the speed of the impeller results in a lower absorption capacity of the ram pressure machine, so that less water flows through the ram pressure machine and as a result the head water level increases. To comply with the predetermined head water level, which is aimed at a certain power output or optimum efficiency, thus the rotational speed of the impeller can be influenced, which can be accomplished via the braking torque of the motor-generator machine. To reduce the speed of the impeller, the braking torque of the generator can be increased; on the other hand, to achieve a higher speed of the impeller to achieve a greater absorption capacity of the dynamic pressure machine, the braking torque of the motor-generator machine can be reduced. Such influencing is relatively expensive in a conventional dynamic pressure machine with a motor-generator machine control technology.
    Another disadvantage of the known hydropower dynamic pressure machines results from the fact that in case of failure of the motor-generator machine, the dynamic pressure machine fails until the motor-generator machine is repaired or replaced. It would also be desirable, moreover, in the case of, for example, in AT 501 575 Al addressed module design depending on the power of the impeller to allow an adjusted overall generator power, which in the known dynamic pressure machines only by
    Replacement of the motor-generator machine, i. by attaching a motor-generator machine with adapted to the drive power generator power, can be accomplished.
    It is an object of the invention to propose a hydro-dynamic pressure machine as stated above, with which not only such a power adjustment in a modular design of the dynamic pressure machine can be realized in a simple manner, but also a total failure of the hydropower in case of failure Motor-generator machine can be avoided, and further in a simple manner, operation in an optimal generator power range depending on the head water level or possibly underwater level, ie in particular from the water level or the difference between the upper water level and underwater level is possible.
    To solve this problem, the invention provides a hydro-dynamic ram machine as characterized in the independent claim. Advantageous embodiments and further developments of this dynamic pressure machine are specified in the dependent claims.
    In the present hydro-dynamic ram printing machine is thus provided primarily that adjacent at least one end face of the hub of the impeller fixed to the frame support member with a plurality of slot-like, preferably arranged underwater side receptacles arranged for each machine Ge transmission module is sealed against the impeller, that in at least some shots machine-transmission modules are mounted, of which in each case a drive pinion · meshes with a fixedly mounted on the front side of the hub sprocket, and that the machine-transmission modules associated switching means are provided for selective connection or disconnection of the machine-transmission modules NEN. By providing a plurality of engine-transmission modules whose pinions become a " matrix drive " can complement, e.g. Depending on the width of the impeller, the total drive power (total generator power) can be easily adapted to the particular version of the impeller by attaching more or less machine drive modules to the matrix drive. - 4 - - 4 - ** »* * * ιι * · • · • ·
    Furthermore, by (electrical) switching off individual modules, depending on the water supply, it is possible to operate the individual generators remaining in operation in an optimum power range. The electrically disconnected modules turn then empty without power extraction. This allows the electrical power output to be adapted to the needs of the local water supply.
    Should an engine-transmission module fail (electrically), the hydro-electric machine can continue to operate with the modules still operating, possibly with reduced power, i. it does not fail the entire system, as is the case in the prior art.
    As far as the performance or modular design is concerned, a wide water wheel, given a diameter, delivers more power than a narrower impeller (with the same diameter). As a good approximation, a wheel that is twice as wide (waterwheel) produces twice the torque and twice as much power. With the support part according to the invention for a plurality of machine-gearbox modules, depending on the width of the impeller, the number of modules to be used can be determined, which are mounted in the desired receptacles of the support member. Unused recordings, ie free recordings, in which no machine-gearbox modules are inserted, are sealed in a suitable manner. As a result, with maximum width impellers, the maximum number of machine gearbox modules is attached to the support member, whereas with narrower impellers, fewer machine-gearbox modules can simply be attached to the support member.
    Thus, in the present machine-transmission modules, there is a generator with an integrated transmission, e.g. a planetary gear or spur gear, in front; a drive pinion of this transmission is accessible from the outside, and this drive pinion is in engagement with the ring gear on the hub end face; via the gearbox, the relatively low speed of the impeller is converted into a suitably high speed of the generator.
    Theoretically, it is also conceivable, as the transmission only with the
    - b -
    To provide sprocket meshing pinion gear, if the ratio between sprocket and pinion already sufficient for the speed ratio to the generator. For this purpose, it is particularly advantageous if the ring gear on the hub end side is an internally toothed ring gear, which is thus outside (ie outside of the pinion) and thus has a relatively large diameter and thus a large number of teeth, so that the relatively small pinion, with a small number of teeth ·, can be driven by the ring gear during operation with a comparatively much higher speed.
    In principle, it is of course also possible, for example, if this is necessary for other structural conditions to provide an externally toothed ring gear on the hub end face, in which case the pinion of the machine-gearbox modules outside of this ring gear are present, then compared to a internal gear ring has a smaller diameter, so that the translation can not be as high as an internally toothed ring gear. For a simple, space-saving, compact construction, the support member is preferably plate-shaped, e.g. as a side plate, formed.
    Furthermore, the support member can be easily connected to the frame via at least one bracket projecting from the frame; As already mentioned, the machine-gearbox modules are preferably located on the underwater side of the dynamic pressure machine, and the console, preferably two consoles, project from the underbody side of frame supports and support the supporting part with the required strength. The support member can also be used to support the impeller, i. the supporting part is part of the bearing frame via the console (s).
    To easily mount the machine-gearbox modules on the support part, it is advantageous if these modules are attached to the support part via flange connections. In the case of free recordings of the support member, these free receptacles of the support member are preferably closed by blind flanges. • ·
    - 6 -
    In order to enable the best possible power adjustment, it is advantageous if the supporting part contains more than three receptacles for machine n-gear module e. But it is also possible in principle to provide only two or three shots. For proper operation of the dynamic pressure machine, it is further preferred if seals, for example, between the support part and the Na-ben end face, e.g. Lip seals, against water inlet on the one hand and oil outlet on the other are arranged; or when between the support member and a wheel-while seals against water inlet on the one hand and the oil outlet on the other are arranged. For a possible automatic power adjustment, for optimal operation of the dynamic pressure machine and in particular of the generators, it is further favorable if the switching means to a control unit, e.g. with PLC module, which in turn is connected to a level sensor, preferably a head-water level sensor, to control switching means for shutting down individual engine-transmission modules at a comparatively low water level (e.g., predetermined in the order of shutdown).
    The invention will be further elucidated on the basis of preferred embodiments, to which, however, it should not be restricted, and with reference to the drawing. In detail in the drawing:
    Fig. 1 is a perspective view of a hydropower dynamic pressure machine according to the invention, and seen from the underwater side, wherein the side of the impeller with the machine Ge transmission modules is visible;
    Figure 2 is a similar perspective view of the underwater side of the dynamic pressure machine of Figure 1, but now from the other side, opposite to the side where the machine-gearbox modules are mounted;
    3 shows an oblique view of the dynamic pressure machine according to FIGS. 1 and 2 from the upper water side;
    Fig. 4 is a side view of the dynamic pressure machine according to Figures 1 to 3, wherein the side with the machine-gearbox modules is visible.
    5 is an elevational view of the dynamic pressure machine according to FIGS. 1 to 4 seen from the upper water side;
    Fig. 6 is a side view of the ram pressure machine similar to Fig. 4, but with the stationary frame and the storage frame of the ram pressure machine cut away, substantially along line VI-VI in Fig. 5; FIGS. 7A and 7B show two embodiments with regard to the arrangement of the sprocket on the end face of the hub of the dynamic pressure machine, namely once with internal teeth (FIG. 7A) and once with external teeth (FIG. 7B);
    8 shows a partial view, partially broken away, of the dynamic pressure machine according to FIGS. 1 to 4, wherein in particular the bearing of the impeller and a design of an externally toothed ring gear on the hub are illustrated; 9 and 10 are partial sectional views in the region of the seal between the module support member and the hub (detail IX in FIG. 9) or between the module support member and the impeller shaft (detail X in FIG. 10); and
    Fig. 11 is a block diagram illustrating an electric circuit including a control unit for turning on and off the electric machines (generators) depending on the water level.
    In Fig. 1 and 2, a hydro-dynamic machine 1 with an impeller 2 is seen from the underside seen schematically illustrated. Figs. 3 and 5 show this dynamic pressure machine 1 seen from the upper water side.
    The impeller 2 has a cylindrical hub 3, whose axis is simultaneously the axis of rotation of the impeller 2, also called rotor. At this hub 3 are at the axial ends of annular Abdeckschei.ben 4 fixedly mounted, which limit the width of the impeller 2. Cover disks 4 allow an advantageous sealing of the impeller 2 in a bearing frame 5 with the aid of sheets 7 shown in FIGS. 3 and 5, attached to a stationary frame 6 on the upper side, and sealing lips 8 fastened thereto.
    At the periphery of the wheel hub 3 suitably shaped blades 9 are mounted, e.g. screwed and / or welded to form bags for water transport, i. absorb the water pressure and cause a torque around the wheel axle.
    The vanes 9 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.
    The frame 5 supporting the impeller 2 has an overall rectangular shape with two vertical supports 10, 11 and a lower support 12 and an upper support 13 around the impeller 2. The carriers 10 to 13 are preferably formed from rectangular in cross-section mold tubes, whereby a simple, lightweight, yet stable construction of the frame 5 is achieved, which also allows easy adaptation to different dimensions, in particular widths of wheels 2. In this regard, reference should be made to the prior unpublished application AT A 1193/2010, the contents of which are incorporated herein by reference.
    The vertical supports 10, 11 carry wheel bearings 14 (only one of these bearings is visible in Fig. 2, the other is concealed in Figs 1 to 3, but see also Fig. 8), wherein the wheel bearing 14 according to FIG is fastened to a bracket 15 projecting from the bracket 15, as shown in FIG. 2 can be seen. This attachment of the bearing 14 is provided in the preferred embodiment on the downstream side (underwater side) of the dynamic pressure machine 1.
    The vertical supports 10, 11 are provided on their outsides, that is, on the side facing away from the impeller 2, with E 'guide roller units (or other guide elements ensuring a low-friction displacement of the frame 5 in the stationary machine frame 6), cf. 1 to 3, so as to raise or lower the frame 5 relative to the frame 6, for example for maintenance purposes or to adapt the impeller height to the respective underwater level, with the aid of a suitable to enable Hubverrichtung not shown in detail; see. the mentioned A 1193/2010; the raising or lowering of the frame 5 is schematically illustrated in Fig. 3 with a double arrow 5 '.
    3, which shows the upstream side or upstream side of the dynamic pressure machine 1, a curved crop pan 17, which is arranged in the lower region of the rotor 2 and is shown by means of holders 18A attached to the vertical supports 10, 11, is shown. 18B is attached to the frame 5 and has a curvature which is adapted to the path of movement of the impeller 2 and the blades 9 thereof. With the aid of this bolster plate 17, the water can thus be introduced tangentially into the lower area around the impeller 2, so that it can be located on the underwater side (FIGS. 1 and 2) on the underside of the impeller 2 in a discharge area 19 (FIG. 2). leaking above the lower support 12 and drains.
    The arrangement with the sealing lips 8 and further with the cropping plate 17 ensures that the water of the channel is optimally utilized for the generation of electrical energy, i. the efficiency of the dynamic pressure machine 1 shown is thereby additionally improved.
    The described frame 5 for supporting the impeller 2 allows a modular principle for the dynamic pressure machine 1, wherein by means of the carrier 10 to 12 in a simple manner to the respective size (width or diameter) of an impeller 2 adapted bearing frame 5 can be assembled , Suitable for this purpose is then provided in the channel stationary arranged frame 6.
    In order to meet this modular principle also with regard to the means for generating electricity, a matrix arrangement with a plurality of modules 20, each containing an electric machine (generator motor) and a transmission integrated therewith, are provided. From Fig. 1, three such modules 20, each with a gear 21 and a machine or a generator 21 ', can be seen. These modules 20 are fixedly attached to a frame 5 fixedly connected Tragteii 22 which is arranged on the front side of the hub 3 of the impeller 2, but does not rotate with this hub 3, but with the aid of brackets 23, 24 with one of the vertical Support of the frame 5, as shown in FIG. 1 with the vertical support 11 shown there on the left, is rigidly connected. The support member 22 is plate-shaped or disc-shaped in the illustrated embodiment, said disc-shaped support member 22 as shown in FIG. 1 is radially inside and adjacent to the annular cover plate 4 on this side, which in turn is fixed to the hub 3 of the impeller, as mentioned above.
    The support member 22, also called circular disc, side plate or motor plate, has a plurality of slot-like receptacles 25 for each machine-a transmission module 20, wherein it is not necessary to mount 25 corresponding modules 20 in all recordings. Thus, in the example of FIG. 1, a module 20 is to be mounted in each of three receptacles 25. The two intermediate free slot receptacles 25 that do not accommodate modules 20, s. 1, are tightly closed, for example with the aid of blind flanges 26. The modules 20 in turn are connected in a corresponding manner via schematically shown in FIGS. 1 and 9 flange 27 with the support member 22.
    In this way, depending on the size, i. Width and diameter of the impeller 2 more or less modules 20 are mounted so as to optimally recover electrical energy from the kinetic energy of the impeller 2, with optimum efficiency.
    From Fig. 4 is a side view of the arrangement of the impeller 2 of the dynamic pressure machine 1 in the frame 6 (the frame 5 is not visible in Fig. 4) illustrated, wherein it is shown that the modules 20 and receptacles 25 in the support member 22 at the Underwater page 28 of the dynamic pressure machine 1 are present; the upper water side is indicated in Fig. 4 at 29, and further the direction of rotation of the impeller 2 is indicated by an arrow 20. Furthermore, it can also be seen in the representation according to FIG. 4 that a further bearing 31 for the shaft of the impeller 2 is mounted centrally on the carrier 11. This bearing 31, like the bearing 14, is preferably a self-aligning bearing; Axial and angular errors can be compensated by the self-aligning bearings.
    From the upstream side view of the dynamic pressure machine 1 according to FIG. 5 are again de.r mounted in the frame 6 rectangle frame 5, the impeller 2 with the blades 9, further the sheets 7 with the sealing lips 8 and the cropping tray 17 can be seen.
    In a sectional view along the line VI-VI in Fig. 5 then the arrangement of the receptacles 25 for machine gearbox modules 20 in the side plate support member 22 can be seen in Fig. 6; Furthermore, connecting parts 32 for connecting the supporting part 22 with the brackets 23, 24, thus with the frame 5, can be seen.
    In FIGS. 7A and 7B, the end face of the hub 3 can be seen, wherein it is shown that a toothed rim 33 (FIG. 7A) or 33 '(FIG. 7B) is fixedly attached to these hub end faces.
    In the case of Fig. 7A, the ring gear 33 is an internally toothed ring gear having a relatively large diameter, and with this internally toothed ring gear 33 meshing three drive pinions 34, which belong to the three machine-gearbox modules 20 as shown in FIGS. 1, 2 and 4, wherein the ring gear 33 with the respective drive pinion 34 already form a gear to increase the speed. In certain cases, the resulting translation may already be sufficient to drive the generators 21 'of the modules 20 at a suitable rotational speed, so that further gear parts in the gears 21 of the modules 20 can be dispensed with. The gear 21 is then formed in each case only by the ring gear 33 and the associated pinion 34. As a rule, however, further toothed wheels will be present in order to provide an additional (in the case of FIG. 7A, however, relatively small) ratio (secondary ratio) for driving the rotor of the generator 21 '.
    In the case of FIG. 7B, the toothed rim 33 'is externally toothed, wherein the drive pinions 34 of the machine-gear module 20 (see FIG. 1) are present radially outside this toothed ring 33'. As can be seen here, the transmission ratio is smaller than in the case of FIG. 7A, so that here a comparatively larger secondary ratio in the transmission 21 of the respective module 20 is required.
    It can be seen here that an internally toothed ring gear 33, as shown in Fig, 7A, is generally preferable, since a smaller secondary translation - if any - is required in the module 20, and since lower tooth forces irr. Gear operation act.
    For reasons of constructive circumstances, however, an external toothing may sometimes be necessary, and as can be seen in FIG. 7B, this is entirely possible in the present dynamic pressure machine 1.
    From the partial view in Fig. 8, the bearings 14, 31 for at the hub 3 of the impeller 2 frontally mounted stub shaft 35, 36 can be seen. In this case, the one bearing, namely the bearing 14, on the side facing away from the modules 20 Stinseite, for example, be designed as a self-aligning bearing. The opposite bearing 31, for the other stub shaft 36, is connected for example via a rigid mounting plate 37 with a provided as Na-ben end face 38 plate.
    Furthermore, inner stiffeners 39 on the Na-ben end faces can still be seen from FIG. 8. These stiffeners 39 can be provided for receiving bending moments, which originate from the distances between the bearings 14, 31 and the mounting plates 37 at the hub end faces 38.
    Fig. 9 shows in a detail section corresponding to the detail IX in Fig. 8, the region of the seal between the support member 22 and the wheel hub 3. It is illustrated that between the hub 3 and the support member 22 (motor plate or side plate) a Oil space 40 is provided, said oil space 40 or space between the support member 22 and hub 3 is to seal accordingly. Specifically, here a seal 41, in particular lip pendulum, provided to prevent ingress of water into the space 40, and another seal 42, in particular lip seal, which lies axially further inward, serves to an oil outlet from the oil chamber 40 to prevent. As can be seen further from FIG. 9, the respective toothed rim, for example the internally toothed ring gear 33 (see also FIG. 7), can be fastened by means of bolts or similar fastening means 43 to the end face 38 or to a flange part 44 of the hub 3 firmly connected thereto be connected.
    Fig. 10 shows the detail X of FIG. 8 and concretely the area of a rolling bearing 45 for centering the support member or side plate 22 relative to the shaft 36 and further a corresponding part of the oil chamber 40, with a seal 42 'against oil leakage on the one hand a seal 41 'against water ingress on the one hand between the support member 22 and the shaft or the stub shaft 36th
    In Fig. 11, a plurality of strands 51, 52, 53, etc. are each shown with a generator 21 'of a module 20 as described above. The generators 21 'are preferably asynchronous generators, even if synchronous generators could also be used. The generators of the individual strings 51, 52... 53 supply their electrical energy to frequency converters 54, which are connected via switches PWR1, PWR2... PWRn to a regenerative converter 55-in normal operation-to supply current to this grid via this regenerative converter 55 56 to deliver. The switches PWR1, PWR2... PWRn form switching means 57 which belong to a control unit 58 with, for example, a PLC control module 59. This PLC module 59 is connected to a level sensor 60 for water level determination, for example, (only) the upper water level is detected. If appropriate, however, it is also possible to detect the upper water level and the underwater level or the level difference, with a specific level difference leading to optimum operation of the dynamic pressure machine 1. At constant underwater level, it is sufficient to detect the head water level, then by raising the speed of the impeller 2 of the dynamic pressure machine 1 and thus the absorption capacity of the dynamic pressure machine 1, for example, a too deep sunken upper water level to raise again or too high · · * * »» ♦ * »I · ft - 14 -
    Lowering the headwater level through increased water transport through the dynamic pressure machine 1 back to the optimum level value. In this connection, it is favorable if individual generators 21 'can be switched on or off in a larger number of generator / transmission modules 20 (see FIG. 1), for which purpose the switching means 57 are provided in connection with the SPS control module 59 are. Now, if the detected water level is relatively low, one or more generators 21 'may be turned off via the control unit 59 and the corresponding one or more switches PWRi so as to reduce the water flow rate and increase the upper water level again. In this way, operation of the (remaining) individual generators 21 'in an optimum power range can be achieved. The electrically disconnected generators 21 'turn then empty without power extraction. A mechanical separation of the unused generators 21 'is indeed theoretically possible, but not essential.
    Apart from the automatic on and off of generators 21 ', as described with reference to FIG. 11, it is of course also conceivable individual generators 22 by hand with the help of switching means 57 on or off, such as when long-lasting changes in the Water levels are given in prolonged drought or prolonged periods of rain.
    The described matrix arrangement with several machine gearbox modules 20 also provides, apart from the above-described operational optimization, also the advantage that in the event that a generator module fails, the water engine 1 continues to work with the still working modules 20, if necessary reduced power, can continue to operate. In the case of prior art hydropower machines with only a single generator, by contrast, if the generator fails, the entire system fails.
    权利要求:
    Claims (10)
    [1]
    * *

    Claims 1. A hydro-dynamic ram machine (1) comprising at least one impeller (2) rotatably mounted on a frame and having a hub (3) and associated blades {9}, and in operation a water level as a difference between an underwater level and an underwater level, and with a to the impeller (2) via a gearbox (21) coupled electric motor-generator Maschinc (21 '), characterized in that adjacent at least one end face of the hub (3) of the impeller a with the frame (5) fixedly connected support member (22) with a plurality of slot-like, preferably underwater side arranged receptacles (25) for each machine (21 ') - transmission (21) module (20) is arranged, which supporting part (22) relative to the impeller (2) is sealed, that in at least some receptacles (25) machine transmission modules (20) are fixed, each of which a drive pinion (34) with a fixed to the front side of the hub (3) appropriate gearwheel (33, 33 ') meshes, and that the machine-gearbox modules (20) switching means (57} are assigned for selectively switching on and off of the engine-transmission modules (20).
    [2]
    Second hydro-dynamic machine according to claim 1, characterized in that the supporting part (22) plate-shaped, e.g. as a disc or side plate is formed.
    [3]
    3. Hydropower dynamic pressure machine according to claim 1 or 2, characterized in that the supporting part (22) with the frame (5) via at least one cantilevered by the latter console (23, 24) is connected.
    [4]
    4. Hydropower dynamic pressure machine according to one of claims 1 to 3, characterized in that the machine gear modules (20) via flange (27) on the support member (22) are attached.
    [5]
    5. Hydropower dynamic pressure machine according to one of claims 1 to 4, characterized in that free receptacles (25) of the supporting part (22) by blind flanges (26) are closed. • * • * · m • · - 16 -
    [6]
    6. Wasserkrait back pressure machine according to one of claims 1 to 5, characterized in that the toothed rim (33) on the hub Stirnseitc an internally toothed ring gear.
    [7]
    7. Hydropower dynamic pressure machine according to one of claims 1 to 6, characterized in that the Tragteii (22) contains more than three receptacles (25) for machine-gearbox modules (20).
    [8]
    8. Hydropower dynamic pressure machine according to one of claims 1 to 7, characterized in that between the support part (22) and the hub-face side seals (41, 42), e.g. Lip seals, against water inlet on the one hand and oil outlet on the other are arranged.
    [9]
    9. Hydropower dynamic pressure machine according to one of claims 1 to 8, characterized in that between the support member (22) and an impeller shaft (36) seals (41 ', 42') are arranged against ingress of water on the one hand and oil outlet on the other.
    [10]
    A hydro-dynamic ramming machine according to any one of claims 1 to 9, characterized in that the switching means (57) are connected to a control unit (58), e.g. with a PLC module (59), which in turn is connected to a level sensor (60), preferably an upstream level sensor, in order to switch off at a comparatively low water level switching means (PWR1 ... PWRn) for switching off individual machine / transmission modules ( 20).
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    AT404973B|1997-04-01|1999-04-26|Brinnich Adolf|HYDROPOWER PRESSURE MACHINE|
    US6616403B1|2002-04-08|2003-09-09|Matt H. Smith|Floating electric generator|
    AT501575A1|2005-12-27|2006-09-15|Brinnich Adolf|HYDRO POWER JAM PRESS|
    BE1017531A3|2007-03-27|2008-11-04|Jonghe D'ardoye Baldwin De|METHOD FOR USING HYDRAULIC ENERGY AND CROSSING SYSTEM|
    WO2010083590A1|2009-01-22|2010-07-29|Howard Harrison|Modular generator system for wind turbines|
    SK288244B6|2009-03-30|2015-02-03|VLADIMĂŤR MĂśLLER|Floating water wheel especially a multifunction power generator|AT512973B1|2012-05-22|2015-09-15|Franz Berthiller|Wasserradanlage|
    US20190277243A1|2016-11-08|2019-09-12|Te-Lu Tseng|Generator device|
    法律状态:
    2018-05-15| PC| Change of the owner|Owner name: HPSA HYDROPOWER SYSTEMS GMBH, AT Effective date: 20180326 |
    2019-04-15| MM01| Lapse because of not paying annual fees|Effective date: 20180824 |
    优先权:
    申请号 | 申请日 | 专利标题
    ATA1413/2010A|AT510320B1|2010-08-24|2010-08-24|HYDRO POWER JAM PRESS|ATA1413/2010A| AT510320B1|2010-08-24|2010-08-24|HYDRO POWER JAM PRESS|
    PCT/AT2011/000331| WO2012024704A1|2010-08-24|2011-08-03|Hydropower dynamic-pressure machine|
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