WO2009074283A2

WO2009074283A2 - Water wheel

Info

Publication number: WO2009074283A2
Application number: PCT/EP2008/010427
Authority: WO
Inventors: Hermann Riegerbauer
Original assignee: Hermann Riegerbauer
Priority date: 2007-12-11
Filing date: 2008-12-09
Publication date: 2009-06-18
Also published as: WO2009074283A3; AT506106B1; AT506106A1

Abstract

The invention relates to an undershot or breast-shot water wheel with a horizontal hub, wherein blade arrangements for converting motion energy and optionally also positional energy of the flowing water into a rotational movement of the water wheel are provided along the periphery of the wheel, characterized in that the blade arrangements (15) each comprise an outer (a) and at least one inner (b, c) paddle blade (23), wherein the inner paddle blades (b, c) are offset from the periphery of the wheel inward and against the direction of flow (1) of the water (7).

Description

water wheel

The invention relates to a unterschlächtiges or mittelschlachtiges waterwheel with horizontal hub, wherein along the Radumfanges blade arrangements for the implementation of movement and possibly also the potential energy of the water flow are provided in a rotational movement of the water wheel. Furthermore, the invention relates to a hydroelectric power plant with one or more such water wheels.

Water wheels have been in use for a very long time. Such water wheels were used in particular for the power supply of mills and hammer mills. Both undershot and overshot water wheels are set up only for a relatively low speed and the energy utilization of the water flow is poor. The technological development of such water wheels had therefore largely come to an end, as by the development of turbines of various types high efficiency and high speeds could be achieved, which subsequently made the production of electric power economically reasonable.

However, there is a constant and growing demand for small power plants, which allow power generation with only minor intervention in the natural watercourse, so that now a further development of water wheels has made sense again.

Known undershot or mittelschlächtige waterwheels have predominantly one-piece continuous blades, which are unfavorable in terms of flow conditions. When immersing the blades in the water flow and also when the blade emerges from the water flow, energy losses occur and water volumes are uselessly displaced or raised. As a result, the efficiency is greatly reduced and the achievable speeds are low. If the through blades are closed to the hub of the water wheel out, there is also a suction effect when running out of water, which further inhibits the water wheel.

BESTATIGUNGSKOPIE The object of the invention is therefore to provide a water wheel and a power plant working therewith, which allows better efficiency and higher speeds.

According to the present invention, this object is achieved in that the blade assemblies each comprise an outer and at least one inner blade lamination, wherein the inner blade louvers are offset from the Radumfang inwardly and against the flow direction of the water flow.

Other features of the waterwheel are that each blade lobe is bent, with the convex curvature directed in the direction of rotation of the waterwheel. Thus, the concave side of each blade is exposed to the flow of water. Furthermore, each blade lamella can have a flow end facing the wheel circumference and an outflow end pointing to the rotation axis, which lies in the connection plane to the rotation axis with a maximum angle deviation of + 10 °, preferably + 5 °. The height of each blade lamella corresponds to about 50% to 100% of the water flow depth. Preferably, each blade assembly comprises two or more blade blades arranged along a curved line whose convex curvature is directed against the direction of rotation of the water wheel. This arc line has a radius about D x%, where D is the diameter of the water wheel. Subsequently, the blade assemblies are in the same sectors of the water wheel with the inner angle ß, which is equal to 15 ° or 30 °, preferably 15 °. In addition, each blade assembly may have a connecting blade disposed along the circumference of the water wheel between adjacent blade assemblies and which lies on a curved line 27 that includes the adjacent blade blades and whose convexity is directed in the direction of rotation of the water wheel. Furthermore, the diameter of the water wheel is preferably about 8 to 12 times the depth of the water flow. The connecting blades are advantageously arranged in the height of the middle blade lamination with each arrangement of three blade blades per blade assembly. In the arrangement of three blade blades, the innermost blade blade with its inflow surface is preferably in a plane which divides the angle ß and passes through the axis of rotation.

The hydroelectric power plant according to the invention is characterized in that it has at least one waterwheel with at least some of these features. The arrangement of the water wheel with a horizontal hub means that the individual vane fins between the vertically disposed Radwangen lie substantially horizontally, although within the scope of the invention, the vane blades are also oblique to the Radwangen or may have a deviating from the line shape. The respective outer blade lamellae are those which are arranged closest to the wheel circumference or directly on the wheel circumference. The inner vane lamellae are those that have a lesser or least radial distance from the hub.

The blade assemblies preferably extend between two or more wheel cheeks. These may be disc-shaped or designed as a strut construction. It may also be formed as a centrally disposed disc, the two sides of which the blade assemblies extend. Thus, it is not necessary that the Radwangen physically present as discs.

The respective water depth is the depth of the water flow, which allows an optimal work of the water wheel and for which the water wheel is designed. The effective water depth is the immersion depth of the water wheel in the water flow.

The high rotational speed of the water wheel resulting from the invention allows a higher immersion depth of the water wheel in the rear water. As the wheel dips deeper, the fall of the water in the inlet of the wheel increases.

A smooth running behavior can be achieved by dividing the space between the wheel cheeks and interposing the correspondingly shortened fins on the circumference. Thus, the waterwheel can also have the feature that it is formed by joining two water wheels into a single water wheel with three Radwangen and that the blade assemblies of the two Wasserradhälften are offset in their rotational position to each other. The use of the water wheel according to the invention may of course also be useful if not the optimal water flow depth, but a smaller or larger water depth is present.

In the following the invention will be described in more detail by means of exemplary embodiments.

Figure 1 is a section through a hydroelectric plant and Figure 2 is a section along the line H-II in Figure 1. Figure 3 is a plan view of this hydroelectric power plant. Figure 4 shows schematically the flow conditions on the waterwheel and Figure 5 shows the scheme of the arrangement of the vane blades between the Radwangen of the waterwheel. Figure 6 is a side view of a single blade lamella. Figure 7 shows in detail a construction scheme for the arrangement of the vane blades in the waterwheel.

In the figures 1 to 3, a power plant is shown schematically. The water flow flows in the direction of the flow direction 1 into the water inlet channel 2, which has a sedimentation tank 3. An overflow channel 4 is provided to receive excess water or to steer the entire water flow by means of a weir (8, 9) on the water wheels 5. In this example, two water wheels are arranged next to each other. But it may also be provided only a single waterwheel or a plurality of water wheels next to each other.

The blade assemblies 15 between the respective Radwangen 12 are indicated only schematically by straight lines.

The water channel has in a known manner via an accelerator section 6, which prefers an increase in the bottom of the water inlet and a subsequent sloping route for the watercourse and serves to increase the flow rate and the generation of a defined water flow.

FIG. 3 shows the schematic plan view of this power plant, the associated weirs 8, 9 being shown only schematically.

In Figure 4, the watercourse is shown schematically, wherein the height ratios and slopes of the flow path are not drawn to scale. The water flow has in the water inlet channel an inlet water depth he, which decreases along the accelerator section 6 and the water flow depth h, which represents the effective water flow, which exerts its force on the water wheel. Each water wheel has a water flow depth that is optimal for the work of the water wheel and on which the dimensions of the water wheel are turned off. The effective water flow depth corresponds largely to the deepest immersion depth of the outermost lamella of the blade arrangements in the water flow.

After passing through the water wheel, the water flows through the water outlet 10, it is advantageous if the outlet water depth ha does not fall below the water flow depth h. However, due to the rotational movement of the water wheel in the direction of rotation 11 about the axis of rotation 18 and the hub 26, it usually leads to a damming of the leaking water, whereby the outlet water depth ha can also be greater than the water flow depth h, as dashed with ha 'is located.

FIG. 5 shows the diagram of the blade arrangements according to the invention, with only the blade arrangements lying below being shown for the sake of simplicity. It goes without saying that the blade arrangements are provided symmetrically around the waterwheel along the circumference.

The inflowing water is indicated by the arrow for the flow direction 1. The inner circle 13 shows the effective water depth h, which, however, acts only in the region of the lowest point X on the water wheel. The outer circle is the circumference 14 of the Radwangen 12 and therefore also of the water wheel fifth

The blade assemblies 15 are provided along the entire wheel circumference 14 and are symmetrical in wheel sectors 16, the wheel sectors preferably occupy an angle ß of 30 ° or 15 °, more preferably 15 °. The latter angle gives 24 blade arrangements.

A blade arrangement basically consists of at least two and, in the present case, three blade blades 23 at the positions a, b, c, which are arranged along a curved line 17. The convex curvature of this arc line is directed against the direction of rotation 11 of the water wheel. It is essential that the inner blade lamellae at positions b, c opposite the outermost blade lamination at a from Radumfang 14 are offset inwards and against the direction of rotation 11 of the water wheel. This causes the blade blades in the sequence a, b, c dive into the water flow and in this order also disappear again from the water flow when the water wheel has rotated.

In the embodiment of FIGS. 5 and 7, scraper blades are further provided as connecting blades 24, which are located between two adjacent outer blade blades a at position d and occupy approximately the same position from the axis of rotation 18 as the second blade blade at b.

As can also be seen from FIG. 5, all the vane lamellae lie at the lowest point X within the effective water flow depth h. The height of each blade lamella is half the water depth h. It should also be noted that each blade lamella has a leading end pointing in the direction of the circumference 14 and a discharge end projecting in the direction of the axis of rotation 18.

All these measures ensure that there is a high rotational speed and maximum efficiency of the water wheel. When immersed in the water flow immediately after a power transmission in the direction of rotation 11, wherein the immersion in the water without or only with low spraying and thus occurs without loss of power. The maximum power transmission from the water flow to the water wheel takes place in the marked X-point. After passing through the X-point, the blades reach a position where they are lifted out of the water. Here, the water between the blades is again allowed to drain easily and without significant loss of power and the arrangement of the blade blades ensures that the increased water volumes are very low. This is also done by the measure that the blades or their blade blades are also open to the inside, so that no suction can occur.

The blade louvres at positions a and b each form a constriction in the direction of the axis of rotation. This constriction acts like a shock absorber that absorbs the power of the water from the outside in and slows it down into the wheel. The blade lamella at the position a creates a negative pressure at the convex rear side, the lamella at b slows down the backwashing of the lamella a. That by the Bucket blades at a and b pressed water flows by gravity towards the negative pressure side, whereby the water remains at the outer edge of the wheel. When emptying the gaps, this mechanism works in reverse order, resulting in accelerated emptying of the water wheel and increased efficiency.

FIG. 6 shows the view of a blade lamella 23, 24 with the inflow end 19 and the outflow end 20. As described above, the outflow end 20 projects in the direction of the axis of rotation 18, the outflow end being straight over part of the blade height 21 and straight Surfaces are also in the direction of the axis of rotation.

The upstream end 10 protrudes in the direction of the circumference of the water wheel and is at an angle to the tangent to the water wheel. A preferred radius for the curvature is the height of the blade lamella. The extension of the straight surface to the discharge end 20 is about B / 3.

FIG. 7 shows the exact construction diagram for the arrangement of the blade lamellae between the two wheel cheeks. The position of the outer blade lamella at a defines the beginning of the sector boundary 22. The third, namely innermost lamella is at c on the arc 25 of half the water depth, exactly in the angular symmetry of the sector. The here also existing second blade lamella is at b exactly between the outermost and innermost blade lamella.

If a connecting lamella is provided at d, this lies with a similar circular arc construction mirror image to the sector boundary 22. All outflow ends lie in the direction of the axis of rotation 18th

The orientation of the outflow ends of the blade blades to the axis of rotation should preferably within maximum angular deviations of + 10 ° preferably + 5 °. LIST OF REFERENCE NUMBERS

1st flow direction

2. Water inlet channel

3. settling tank

4. Overflow channel

5. Waterwheel

6. accelerator section

7. Water

8. Weir

9. Weir

10. Water outlet

11th direction of rotation

12. Radwange

13. Circular line

14. Scope

15. Blade arrangements

16th wheel sector

17th arc line

18. axis of rotation

19th approach

20. Outflowing

21. Height of the blade lamella

22nd sector limit

23. Shovel blades

24. Connecting slats

25. circular arc h / 2

26th wheel hub

27. arc line connection plate he inlet water depth h water flow depth ha, ha 'outlet water depth

X ^' lower point a, b, c, d vane lamella positions

Claims

claims

1. Unterschlächtiges or mittschlächtiges waterwheel with horizontal hub along the Radumfanges blade arrangements for the implementation of the movement and possibly also the potential energy of the water flow in a

Rotary movement of the water wheel are provided, characterized in that the blade assemblies (15) each comprise an outer (a) and at least one inner (b, c) blade lamella (23), wherein the inner blade lamellae (b, c) from the Radumfang inward and are offset from the flow direction (1) of the water flow (7).

2. Waterwheel according to claim 1, characterized in that each blade lamella (23, 24) is bent, wherein the convex curvature is directed in the direction of rotation (11) of the waterwheel.

3. Water wheel according to claim 1 or 2, characterized in that each blade lamella (23, 24) has a wheel circumference (14) facing the inflow end (19) and an axis of rotation (18) facing outflow end (20).

4. Water wheel according to one of claims 1 to 3, characterized in that the outflow ends (20) in the connection plane to the rotation axis (18) with maximum angular deviation ± 10 °, preferably ± 5 °.

5. Waterwheel according to one of claims 1 to 4, characterized in that the height (21) of each blade lamella (23, 24) corresponds to about 50% of the water depth (h).

6. Water wheel according to one of claims 1 to 5, characterized in that each blade assembly (15) has three or more blade blades (23, 24) which are arranged along a curved line (17) whose convex curvature against the direction of rotation (11) the water wheel is directed.

7. Waterwheel according to claim 6, characterized in that the arc line (17) has a radius about D x VA, where D is the diameter of the water wheel.

8. Waterwheel according to one of claims 1 to 7, characterized in that the blade assemblies (15) lie in the same sectors of the water wheel with the inner angle ß.

9. Waterwheel according to one of claims 1 to 8, characterized in that ß equal to 15 ° or 30 °, preferably 15 °.

10. Waterwheel according to one of claims 1 to 9, characterized in that each blade assembly (15) additionally comprises a connecting blade (24) which is arranged along the circumference (14) of the water wheel (at d) between adjacent blade lamellae (23).

11. Water wheel according to one of claims 1 to 10, characterized in that the connecting blades (24) lie on a curved line (27), which comprise the adjacent blade blades (23 at c, a) and their convex curvature in the direction of rotation (11) of the Water wheel are directed.

12. Waterwheel according to one of claims 1 to 11, characterized in that the diameter (D) of the water wheel is about 8 to 12 times the depth (h) of the water flow (7).

13. Water wheel according to one of claims 1 to 13, characterized in that the connecting blades (24) are arranged in the height of the middle blade lamination (at b) in the arrangement of three blade blades (23) per blade assembly (15).

14. Water wheel according to one of claims 1 to 13, characterized in that in the arrangement of three blade blades (23), the innermost blade blade (c) lies in a plane which halves the inner angle ß of the sector and through the axis of rotation (18).

15. Water wheel according to one of claims 1 to 14, characterized in that it is formed by joining two water wheels to a single water wheel with a flush hub and that the blade assemblies of the two Wasserradhälften are offset in their rotational position to each other.

16. Waterwheel according to one of claims 1 to 15, characterized in that the blade assemblies (15) between Radwangen (12) are arranged.

17. Waterwheel according to one of claims 1 to 16, characterized in that the beginning of the sector boundary (22) by the position of the outer blade lamella (a) is defined, the innermost lamella (at c) on the circular arc (25) of half

Water depth lies in the angular symmetry of the sector and, where appropriate existing second blade lamella (at b) between the outermost and innermost blade lamella.

18. Water wheel according to claim 17, characterized in that the connecting lamella (24) in a circular arc (25) analogous circular arc construction is mirror image of the sector boundary (22).

19. Hydroelectric power station, characterized in that it comprises at least one water wheel according to one of claims 1 to 18.

20. A hydroelectric power plant according to claim 19, characterized in that for increasing the flow rate and generating a defined water flow, a sloping acceleration section (6) is provided and that the water flow has a water depth which corresponds at least to the depth of the effective water flow, the water wheel on its Exercise power.