WO2013020578A1

WO2013020578A1 - Turbine generator

Info

Publication number: WO2013020578A1
Application number: PCT/EP2011/063584
Authority: WO
Inventors: Henning Kern; Christina Pfeuffer
Original assignee: Aktiebolaget Skf
Priority date: 2011-08-08
Filing date: 2011-08-08
Publication date: 2013-02-14
Also published as: EP2742232A1

Abstract

The invention relates to a turbine generator (1), in particular water turbine generator for generating electricity from a water flow, comprising a turbine impeller (3), an electric generator (5) and a support means (17) which defines a mutual position of turbine impeller (3) and generator (5) relative to one another, and a gear (25) for transmitting a torque from the turbine impeller (3) to a shaft (27) of the generator (5), and further comprising a bearing (33) which comprises an outer ring connected to the support means (17) and an inner ring (37) connected to the turbine impeller (3), which inner ring surrounds a flow guided through the turbine impeller (3).

Description

turbine generator

The invention relates to a turbine generator, in particular a water turbine generator for generating electricity from a water flow, comprising a turbine runner and an electric generator.

US 2009/0115193 A1 describes a water turbine generator in which a water flow drives a turbine runner connected to a plurality of generators. The hydro turbine generator can be used in flowing waters, such as rivers, streams, canals, tidal coves or oceans. On the circumference, the turbine wheel surrounds a ring gear that meshes with four gears that sit on the shafts of the generators. Due to the direct bearing of the turbine impeller on the shafts of the generators, the bearing forces of the turbine impeller must be absorbed by the generators. In addition, at least three generators are necessary to be able to store the turbine wheel at all.

US 7,218,011 B2 describes a turbine runner supported by bearings which may be supported by magnetic bearings. By Gehäuseröhren a proppant is formed. The bearings are designed as slide bearings or split bearings, which can be supported by magnetic bearings at higher rotational speeds. FR 2 795 140 AI describes a turbine wheel which is mounted by means of ball bearings. The turbine wheel is supported on a concrete foundation of a riverbed.

EP 1 885 047 A1 describes magnetic bearings for supporting a plurality of turbine runners.

The object of the invention is to provide a water turbine generator in which the bearing of the turbine runner is improved.

The object of the invention is achieved by a turbine generator, in particular a water turbine generator for power generation from a water flow, comprising a turbine runner, an electric generator and a support means by which a mutual position of the turbine runner and generator is determined to each other, and a transmission for transmitting a torque of the turbine runner on a shaft of the generator, further comprising a bearing having an outer ring connected to the support means and an inner ring connected to the turbine runner, which surrounds a guided through the turbine runner flow, the bearing having a double row tapered roller bearing.

In that the bearing surrounds the flow guided by the turbine runner, it is possible to dispense with internals to be provided within the flow for supporting the turbine runner. Since there are no disturbing the flow internals, the efficiency of the turbine generator can be improved. The bearing can be designed as a rolling bearing. By supporting the turbine runner on the bearing, the bearing forces of the turbine runner need not be absorbed by the shafts of the generators, whereby the life of the turbine generator may be increased. The inner ring may surround the outer contour of the turbine runner. The inner ring can lie in the axial plane of the turbine runner. Alternatively, the inner ring may be disposed at an axial distance from the turbine runner. The turbine runner can also be arranged between two or more inner rings and / or bearings, in particular rolling bearings.

The turbine generator may include a support ring connecting the turbine runner to the ring of irons. Depending on the conditions of use and space, the support ring can be designed differently. The support ring may be attached to a turbine ring connecting the radially outer ends of the blades of the turbine runner. The turbine ring may in particular be manufactured in one piece with the blades or the turbine runner. The turbine ring may have an inner circumferential wall, which is shaped streamlined in accordance with the flow.

The inner ring of the bearing can be connected, for example by means of a fit fit, in particular interference fit with the support ring. Alternatively or additionally, the support ring can be connected by means of releasable fastening means with a flange of the turbine runner. A releasable attachment can be done for example by means of screws. The flange may be an annular flange, which may in particular extend radially away from the circumference of the turbine runner.

In one embodiment of the invention, a drive sprocket may be connected to the support ring. The drive sprocket may substantially extend on a diameter corresponding to the support ring. The drive sprocket may be made separately or integrally with the support ring. For example, the teeth of the drive sprocket may extend radially outward and thus form a spur gear. Alternatively, the teeth of the drive sprocket may extend in an axial direction, for example in the form of a bevel gear.

In a further embodiment, the transmission may have a meshing with the drive sprocket pinion, which by means of a shaft to the generator connected is. The pinion need not necessarily sit directly on the output shaft of the generator, but can sit on a separate shaft which is coupled to the generator.

The tapered roller bearings may be formed in O arrangement and / or with a pressure angle of 45 °.

In all embodiments according to the invention, the support means may be a housing. The housing may in particular have at least one mating surface for at least one seal. The seal may in particular be rotatably mounted with respect to the housing and the turbine runner. By a rotatable mounting of the seal, the peripheral speed between the sealing lip of the seal and the turbine wheel can be reduced, in particular approximately halved.

By way of example, the seal can be rotatably mounted between the housing and the turbine runner by means of at least three rollers, which are supported both against a first runway on the housing and a second runway on the turbine runner. By means of at least three rollers, the seal can be stored aligned in its coaxial position with respect to turbine runner and housing.

In all embodiments of the invention, the seal may have at least one radial shaft sealing ring, in particular with at least two radial shaft sealing lips, and / or a cartridge seal.

The seal may have at least one outwardly, in particular fluid-tight sealing radial shaft sealing lip, which rests against an inner peripheral side mating surface of the housing.

In one embodiment of the gasket, this may alternatively or additionally be provided with at least one radial shaft seal, which seals outwards, in particular against the flow. having lip which abuts an outer peripheral side mating surface of the turbine runner.

In another embodiment of the seal, this may alternatively or additionally have at least one inwardly, in particular flow-facing sealing radial shaft sealing lip, which rests against an inner peripheral side mating surface of the housing.

In a further embodiment of the seal, this may alternatively or additionally have at least one inwardly, in particular flow-facing, sealing radial shaft sealing lip, which rests against an outer peripheral side mating surface of the turbine runner.

In all embodiments of the gasket, the gasket may have at least two radial shaft sealing lips which are outwardly directed, in particular facing away from the flow, and at least two radial shaft sealing lips which are inwardly facing, in particular facing the flow direction.

In summary, the invention thus provides a turbine generator, in particular a water turbine, which is more compact than known solutions and has a high efficiency and high performance even with a small size. According to the invention, the rotor, that is to say the turbine runner, can be fastened in a large bearing, for example a moment bearing, in particular of the "Nautilus" type or two angular contact ball bearings. Occurring radial and axial forces can be absorbed in this camp. For transmitting the torque from the turbine runner to a generator, no turbine shaft is required. Instead, the torque can be transmitted to the generator via a transmission member attached to the rotating inner ring of the large-scale bearing, such as a toothing. A transmission of the torque can be done for example via a small gear which is connected to the shaft of the generator or sitting on this shaft and picks up the torque. By such a configuration, a very high transmission ratio can be realized, which delivers a high speed at the generator. Thus, the generator can generate a high electrical power even at low speeds of the turbine runner or at low flow velocities of the water flow.

As a result, even waters with low flow velocities can be economically developed by hydroelectric plants with turbine generators according to the invention. Due to the storage according to the invention, an otherwise necessary very long channel for guiding the water can also be much shorter. Due to a compact construction of the turbine generator according to the invention and the bearing according to the invention, it is also possible to achieve a setting of the turbine blades with simpler articulations. An articulation no longer has to be guided through a hollow turbine shaft.

In addition, sealing of the turbine runner can be made simpler. According to the invention, radial shaft seals can be used. The seals, in particular the radial shaft seals can be rotatably supported, i. the radial shaft seals not only move with respect to the turbine wheel, but also with respect to the housing.

Especially with large diameters, the rotationally mounted seals according to the invention can reduce the circumferential speeds at the sealing edges. Especially with large diameters and the expected speeds, the rotationally mounted seals according to the invention also the wear can be kept within limits. The seal according to the invention may have four radial shaft seals. Of the four radial shaft sealing rings, two may be arranged sealingly outwards and two sealingly inwards in each case. The rotating seals can be supported by at least three rollers. The rollers can be located between the rotor and the housing. The rotatably mounted seals can form a sealing cassette together with the rollers. The seal cassette may be driven by the turbine runner in which the rollers roll on the turbine runner and bear against the housing. The peripheral speed of the seal cassette reduces the peripheral speeds at the sealing edges in a non-critical area.

Instead of a single electric generator, it is also possible to provide a plurality of, in particular smaller, electrical generators. The storage according to the invention makes it possible to seal the storage outside the water flow. This means that a normal lubrication of the bearing is possible, which can be selected independently of the flow medium. In addition, maintenance and, where appropriate, disassembly and / or replacement of components of the turbine generator can be carried out more easily. Since with the storage according to the invention due to the omission of a turbine shaft no bending moments must be recorded, but almost exclusively axial forces occur, simpler or smaller gear can be used. The installation position of the turbine generator is also completely variable.

An embodiment of the invention is illustrated by way of example in the accompanying schematic drawings. Show it:

1 is a partial perspective sectional view of an embodiment of a turbine generator according to the invention,

FIG. 2 is a cross-sectional view of the turbine generator of FIG. 1; FIG.

3 is an enlarged partial sectional view of the turbine generator of FIG. 2 through a bearing according to the invention, Fig. 4 is an enlarged partial sectional view of Fig. 3 by a seal according to the invention.

The turbine generator 1 shown by way of example in FIG. 1 has a turbine runner 3 and an electric generator 5. In the embodiment shown, the turbine runner 3 has five blades 7. The blades 7 extend in the radial direction, starting from a central node 9, which lies on a rotation axis 11 of the turbine generator 1, to the outside. The outer ends of the blades 7 are connected to a turbine ring 13. The turbine ring 13 is substantially formed as a pipe section, which may have on its inner wall 15 a sfluid to the flow, such as water, adapted contour.

The turbine generator 1 has a support means 17, which may also be referred to as a housing. The support means 17 comprises in the illustrated embodiment, an annular housing 19 and then an inlet pipe piece 21 and an outlet pipe piece 23. By the support means 17, not only the Strömungsflu- id out, but also determines a mutual position of the turbine runner 3 and generator 5 to each other.

For transmitting a torque, the turbine generator 1 has a transmission 25 shown in FIG. 2. The transmission 25 transmits the torque delivered by the turbine runner 3 to a shaft 27 of the generator 5. The shaft 27 of the generator 5 is connected to an output gear 29 for this purpose. In the illustrated embodiment, the output pinion 29 sits directly on the shaft 27. The output pinion 29 meshes with a drive sprocket 31 which is connected to the turbine runner 3.

In FIG. 3, an inventive bearing 33 is shown in greater detail in an enlarged partial sectional view of the turbine generator 1 of FIG. The bearing 33 is over a support ring 35 connected to the turbine runner 3. The bearing 33 has in the illustrated embodiment, an inner ring 37 and an outer ring 39. Between the inner ring 37 and the outer ring 39 rolling elements 41 are arranged. The outer ring 39 is connected to the support means 17. The outer ring 39 is seated in a bearing seat 43 of the support means 17 and the annular housing 19, for example by means of a fit fit, in particular interference fit.

The bearing 33 may have two angular contact ball bearings or as shown in Fig. 3 may be formed as a double row tapered roller bearing. In particular, the double row tapered roller bearing can have a pressure angle of 45 °. This gives the tapered roller bearing a large span and thus high rigidity. Another advantage of the large pressure angle is the resulting small cone angle of the rolling elements 41. The smaller the cone angle, the lower the friction between the rolling elements 41 and a guide board of the tapered roller bearing. The guide board can be designed tribologically low, so that can set an ideal lubricating film in Wälzkörper- guide board contact.

The Inneming 37 of the bearing 33 is connected by means of the support ring 35 with the turbine runner 3. In the illustrated embodiment, the Inneming 37 of the bearing 33 is connected by means of a fit fit, in particular interference fit with the support ring 35. The inner ring 37 surrounds the outer contour of the turbine runner 3. Thus, the inner ring 37 also surrounds a flow guided through the turbine runner 3. In other words, the turbine runner 3 is arranged completely inside the inner ring 37 in the exemplary embodiment. However, it may be sufficient if the inner contour of the turbine runner 3 is on a smaller diameter than the inner diameter of the inner ring 37. This means that the inner ring 37 need not necessarily sit in the same axial position as the turbine runner 3. The Inneming 37 may for example be arranged axially offset with respect to the turbine runner 3 or it may, for example, two inner rings 37, in particular two bearings 33 in an axial distance from each other be provided, between which the turbine runner 3 is located in an intermediate axial position.

The support ring 35 is connected in the embodiment by means of releasable fastening means 45 with the turbine runner 3. The releasable fastening means 45 can be formed in particular by screws. The support ring 35 is, as shown in Fig. 3, connected to an annular flange 47 of the turbine runner 3. On the support ring 35, the drive sprocket 31 is also attached.

The turbine generator 1 has two seals 49a, 49b in the exemplary embodiment. Each seal 49a, 49b may be formed in the manner of a cassette seal. Each seal 49a, 49b may in particular be rotatably mounted both with respect to the support means 17 or the housing and with respect to the turbine runner 3.

FIG. 4 shows one of the two seals 49a according to the invention in an enlarged partial sectional view. The seal 49a is formed in the illustrated embodiment as a radial shaft seal. The seal 49a has a first radial shaft sealing lip 51a which projects outward, in particular against the flow, and bears against an inner circumferential mating surface 53 of the support means 17 or of the housing. The seal 49a furthermore has, to the outside, in particular a flow-sealing manner, a second radial shaft sealing lip 51b, which rests against an outer circumferential mating surface 55 of the turbine runner 3. The first radial shaft sealing lip 51a and the second radial shaft sealing lip 5lb may be at the same axial height, as shown. be considered radially superimposed.

The seal 49a also has a third radial shaft sealing lip 51c which is inwardly, in particular flow-tight, and bears against the inner peripheral side mating surface 53 of the support means 17 or the housing. The seal 49a further has inwardly, in particular Strömungszuge wall sealingly a fourth radial shaft sealing lip 51d, which on the outer peripheral side Mating surface 55 of the turbine runner 3 is applied. The third radial shaft sealing lip 51c and the fourth radial shaft sealing lip 51d can, as shown, be at the same axial height, ie be arranged one above the other as viewed radially. Each of the seals 49a, 49b is in the embodiment according to the invention by means of at least three rollers 57, which are supported against both a first runway 59 on the support means 17 and the housing and supported against a second runway 61 on the turbine runner 3, rotatable between support means 17 and Housing and turbine runner 3 stored. In addition, as shown in FIG. 4, each of the seals 49a, 49b may additionally be axially supported axially by means of associated axial rollers 63, in particular against an axial roller track 65 on the support means 17 or on the housing.

LIST OF REFERENCE NUMBERS

1 turbine generator

3 turbine wheel

5 electric generator

7 shovels

9 central nodes

11 axis of rotation

13 turbine ring

15 inner wall

17 proppants

19 ring housing

21 inlet pipe piece

23 outlet pipe piece

25 gears

27 wave

29 output pinion

31 Drive sprocket

33 bearings

35 support ring

37 inner ring

39 outer ring

41 rolling elements

43 bearing seat

45 E ff ectives

47 ring flange

49a seal b seal

a first radial shaft sealing lip b second radial shaft sealing lip c third radial shaft sealing fourth radial shaft sealing lip

inner peripheral side mating surface outer peripheral side mating surface

castors

first runway

second runway

Axiallaufrollen

Claims

P atentansprUe turbine generator

A turbine generator, in particular a water turbine generator for generating electricity from a water flow, comprising a turbine runner (3), an electric generator (5) and a support means (17), by which a mutual position of turbine runner (3) and generator (5) is determined to each other and a transmission (25) for transmitting a torque from the turbine runner (3) to a shaft (27) of the generator (5), further comprising a bearing (33) having an outer ring (39) connected to the support means (17) ) and an inner ring (37) connected to the turbine runner (3), which surrounds a flow guided by the turbine runner (3), characterized in that the bearing (33) comprises a double-row tapered roller bearing.

2. turbine generator according to claim 1, wherein the double row tapered roller bearing in O arrangement and / or is formed with a pressure angle of 45 °.

3. turbine generator according to claim 1 or 2, comprising a turbine runner (3) with the inner ring (37) connecting the support ring (35).

4. turbine generator according to claim 3, wherein the inner ring (37) of the bearing (33) by means of a fit fit, in particular interference fit with the support ring (35) is connected and / or the support ring (35) by means of releasable fastening means (45), in particular screws with a flange, in particular annular flange (47) of the turbine runner (3) is connected.

5. turbine generator according to claims 3 or 4, comprising a with the support ring (35) connected to the drive sprocket (31).

6. turbine generator according to claim 5, wherein the transmission (25) with the drive sprocket (31) meshing pinion (29) which is connected by means of a shaft (27) with the generator (5).

7. turbine generator according to one of claims 1 to 6, wherein the support means (17) is a housing having at least one mating surface (53) for at least one seal (49 a, 49 b), in particular rotatably mounted with respect to housing and turbine runner (3) is, has.

8. turbine generator according to claim 7, wherein the seal (49 a, 49 b) by means of at least three rollers (57) which are supported against both a first runway (59) on the housing and a second runway (61) on the turbine runner (3) , is rotatably mounted between the housing and turbine runner (3).

9. turbine generator according to claim 7 or 8, wherein the seal (49 a, 49 b) at least one radial shaft seal, in particular with at least two radial shaft sealing lips (51 a, 51 b, 51 c, 51 d), and / or a cartridge seal.

10. turbine generator according to claim 9, wherein the seal (49 a, 49 b) at least one outwardly, in particular fluid-tight sealing Radialwel- lenseichtlippe (51 a), which rests against an inner peripheral side mating surface (53) of the housing.

11. A turbine generator according to claim 9 or 10, wherein the seal (49 a, 49 b) has at least one outwardly, in particular fluid-tight radialwave seal lip (51 b), which bears against an outer peripheral side mating surface (55) of the turbine runner (3).

12. A turbine generator according to any one of claims 9 to 11, wherein the seal (49 a, 49 b) has at least one inwardly, in particular fluidly facing sealing radial shaft sealing lip (51 c) which bears against an inner peripheral side mating surface (53) of the housing.

13. turbine generator according to one of claims 9 to 12, wherein the seal (49 a, 49 b) has at least one inwardly, in particular fluidly facing sealing radial shaft sealing lip (51 d), which abuts against an outer peripheral side mating surface (55) of the turbine runner (3).

14. Turbine generator according to one of claims 9 to 13, wherein the seal (49a, 49b) at least two outwardly, in particular flow-sealing sealing radial shaft sealing lips (51a, 51b) and at least two inwardly, in particular fluidly facing sealing radial shaft sealing lips (51c, 51d) ,