CA2510130A1 - Method and device for reducing pressure fluctuations in an induction pipe of a water turbine or water pump or water-pump turbine - Google Patents
Method and device for reducing pressure fluctuations in an induction pipe of a water turbine or water pump or water-pump turbine Download PDFInfo
- Publication number
- CA2510130A1 CA2510130A1 CA002510130A CA2510130A CA2510130A1 CA 2510130 A1 CA2510130 A1 CA 2510130A1 CA 002510130 A CA002510130 A CA 002510130A CA 2510130 A CA2510130 A CA 2510130A CA 2510130 A1 CA2510130 A1 CA 2510130A1
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- Prior art keywords
- turbine
- pump
- displacement body
- water
- suction pipe
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03B—MACHINES OR ENGINES FOR LIQUIDS
- F03B11/00—Parts or details not provided for in, or of interest apart from, the preceding groups, e.g. wear-protection couplings, between turbine and generator
- F03B11/04—Parts or details not provided for in, or of interest apart from, the preceding groups, e.g. wear-protection couplings, between turbine and generator for diminishing cavitation or vibration, e.g. balancing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03B—MACHINES OR ENGINES FOR LIQUIDS
- F03B3/00—Machines or engines of reaction type; Parts or details peculiar thereto
- F03B3/02—Machines or engines of reaction type; Parts or details peculiar thereto with radial flow at high-pressure side and axial flow at low-pressure side of rotors, e.g. Francis turbines
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/20—Hydro energy
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Hydraulic Turbines (AREA)
Abstract
The invention relates to a turbine or pump or pump turbine, comprising a rotor which has a plurality of rotating blades and a hub, a housing which has a distributor for regulating the currents flowing into the rotor, and an induction pipe for guiding the water flowing out of the rotor, comprising an inlet diffusor. The inventive turbine or pump or pump turbine is characterised by the following characterisitics; an elongate displacement body is arranged in the induction pipe and the upstream end of the displacement body is arranged in the region of the hub of the rotor.
Description
PT 06062WOUS / Voith Siemens Hydro Power Generation GmbH & Co. KG
/DRW/RA/2005006587 / June 13, 2005 Method and Device for Reducing Pressure Fluctuations in a Suction Pipe of a Water Turbine or Water Pump or Water-Pump Turbine The invention relates to a turbine or pump or pump turbine, particularly to the suction pipe thereof which serves for guiding the water flowing out of the turbine to the downstream water. The invention primarily relates to Francis type machines, but also Kaplan type turbines may come into consideration.
Regarding water turbines such as Francis turbines there is an increasing demand for higher efficiencies as well as for an extended range of operation as well as for a higher flexibility regarding the rate of flow between partial load and overload. The efficiency should be high over the whole range of operational parameters, and at the same time the vibration of the turbine should be low.
The adjustment of Francis turbines to variable operational parameters is made by respective positioning of guide vanes. Nevertheless there are instable flow conditions, particularly at partial load, which result in heavy vibrations at the turbine. As a consequence, there may occur damages to specific components, particularly in case the characteristic frequencies of such components coincide with the said frequencies. Also, vibrations of the said kind may be particularly disadvantageous with large machines in that the said vibrations may affect the electric network. Rotational instabilities will be fed into the electric power supply via the generator, thereby resulting in voltage fluctuations. This necessitates disadvantageous limitations of the operational range of the turbine. Critical partial load ranges during start up of the turbine have to be run through rapidly.
When operated optimumly, the water flows from the inlet gates of a Francis turbine axially symmetrically into the runner, where it is deviated by the guide vanes such that it flows axially into the suction pipe and further to the downstream water. The flow in the suction pipe at optimum conditions will be irrotational. At operational conditions of the turbine outside of the optimum, however, there will be torsion of the flow downstreams of the runner. There is no firm knowledge of the PT 06062WOUS / voith Siemens Hydro Power Generation GmbH 8 Co. KG
/DRW/RA/2005006587 / June 13, 2005 dependence between the rotational component of the flow in the suction pipe and the vibrations of the machine. For stabilizing the flow in the suction pipe and for suppressing the torsion guide fins were used, arranged along the suction pipe.
Such guide fins may be oriented in the axial direction. Thereby the flow torsion in the suction pipe will be suppressed, but at the same time the efficiency will be lowered.
To solve the said problem, variable guide fins are used, which according to the flow conditions may be moved in and out. Further, there are used guide fins oriented parallel to the wall surfaces of the suction pipe in order to stabilize the flow by avoiding the separation of the flow. However, also structures of the said type will reduce the efficiency of the turbine. Further, fixed as well as variable finns will increase the costs of manufacture and maintenance of the turbine.
A further approach for the reduction of a torsion of the flow and its detrimental effect under partial load conditions is to feed air or water into the non-stable flow.
There have become known structures whereby air is blown into the runner or into the suction pipe either from the wall of the suction pipe or from the axis of the runner.
Further, it has become known to arrange a chamber filled with water or with air around the suction pipe, which chamber communicates with the flow in the suction pipe by openings in the suction pipe wall. Thereby, air respectively water is introduced respectively removed depending on the pressure conditions in the suction pipe flow. Here again, the costs of manufacture are increased by the said pressure chamber as well as by a respective control unit for the pressure in the chamber.
It is the objective of the invention to provide a suction pipe for a Francis turbine which develops advantageous over the prior art. More in detail, the suction pipe should minimize the effect of pressure variations such as occur at partial load PT 06062WOUS / Voith Siemens Hydro Power Generation GmbH & Co. KG
/DRW/RA/2005006587 / June 13, 2005 conditions. The said objective will be achieved by a suction pipe according to claim 1.
The inventors have acknowledged that with a Francis turbine under partial load conditions there will be created a zone of recirculation downstreams of the runner.
Within the said zone of transition and the main flow there are heavy gradients of velocity. Hydrodynamic instabilities of the Kelvin-Helmholtz-type will result in the formation of vortexes which due to the overall rotation of the flow comprise a rotative component. A rotating vortex of the said type will result in a rotating pressure which in the region of the elbow of the suction pipe generates a force acting in the axial direction, and further results in pressure variations which also act in the axial direction and therefore in the direction of the turbine. It is further possible that such axial pressure variations in combination with the helically shaped vortex - called "rope" - will result in boundary layer burbling at the wall of the elbow, thereby increasing the effect of the axially acting pressure variations.
This explains the generation of pressure variations in the suction pipe depending on the rotational speed of the runner.
A further component of so-called stochastic pressure variations may be developed by the fact that due to the helical vortex rope local pressures below the vapour pressure will be created, thereby leading to cavitation. Additional pressure pulses will occur upon bursting of the cavitation blisters.
According to the invention there is arranged in the suction pipe an elongated displacement body. The upstream end thereof is in the vicinity of the hub of the runner.
The displacement body may be rotationally symmetrically, e. g. cylindrical.
Also, it may have the shape of a truncated cone which tapers in respectively against the direction of flow. It is arranged such that its outer surface is contacted by flowing water. In general, its length axis will coincide with the length axis of the suction pipe.
PT 06062WOUS / Voith Siemens Hydro Power Generation GmbH & Co. KG
/DRW/RA/2005006587 / June 13, 2005 Numerous embodiments may be possible. The displacement body may e. g. be a projection of the hub of the runner and therefore be part of the hub. Also, it may be located at a minimum distance from the hub. The said distance may be a few millimeters only, e. g. 1, 2, 3, 5 mm, but also 10 to 50 mm.
A further embodiment may consist in making the hub longer as usual, as seen in the direction of flow, e. g. twice or three times or five times as long as what could be deemed usual, so that the hub itself would form the displacement body. A
further part will follow, located in the direction of flow. The said further part is independent of the hub, so that the said further part will not rotate.
In such a case, the said further part independent from the hub has to be fixed inside the suction pipe. Such fixing may be done by means of rods arranged perpendicularly to the flow direction at the wall of the suction pipe. The said rods may be arranged radially.
A further particularly interesting approach may consist in journalling the upstream end of the displacement body at the hub of the runner such that the displacement body will be additionally stabilized.
The invention may be used for straight suction pipes as well as for suction pipes comprising an elbow. With suction pipes with an elbow there is an additional possibility of support by fixing the displacement body in the region of the elbow at the suction pipe respectively at the foundation thereof.
The invention as well as the prior art will be explained more in detail by the figures:
Figure 1 shows an axially cut Francis turbine.
Figure 2 is a numeric flow simulation of the formation of a vortex.
Figure 3 is a suction pipe with a first embodiment of a displacement body.
PT 06062WOUS / Voith Siemens Hydro Power Generation GmbH & Co. KG
/DRW/RA/2005006587 / June 13, 2005 Figure 4 is a suction pipe with an elbow comprising a second embodiment of a displacement body.
Figure 5 is a straight suction pipe comprising a further embodiment of a displacement body.
/DRW/RA/2005006587 / June 13, 2005 Method and Device for Reducing Pressure Fluctuations in a Suction Pipe of a Water Turbine or Water Pump or Water-Pump Turbine The invention relates to a turbine or pump or pump turbine, particularly to the suction pipe thereof which serves for guiding the water flowing out of the turbine to the downstream water. The invention primarily relates to Francis type machines, but also Kaplan type turbines may come into consideration.
Regarding water turbines such as Francis turbines there is an increasing demand for higher efficiencies as well as for an extended range of operation as well as for a higher flexibility regarding the rate of flow between partial load and overload. The efficiency should be high over the whole range of operational parameters, and at the same time the vibration of the turbine should be low.
The adjustment of Francis turbines to variable operational parameters is made by respective positioning of guide vanes. Nevertheless there are instable flow conditions, particularly at partial load, which result in heavy vibrations at the turbine. As a consequence, there may occur damages to specific components, particularly in case the characteristic frequencies of such components coincide with the said frequencies. Also, vibrations of the said kind may be particularly disadvantageous with large machines in that the said vibrations may affect the electric network. Rotational instabilities will be fed into the electric power supply via the generator, thereby resulting in voltage fluctuations. This necessitates disadvantageous limitations of the operational range of the turbine. Critical partial load ranges during start up of the turbine have to be run through rapidly.
When operated optimumly, the water flows from the inlet gates of a Francis turbine axially symmetrically into the runner, where it is deviated by the guide vanes such that it flows axially into the suction pipe and further to the downstream water. The flow in the suction pipe at optimum conditions will be irrotational. At operational conditions of the turbine outside of the optimum, however, there will be torsion of the flow downstreams of the runner. There is no firm knowledge of the PT 06062WOUS / voith Siemens Hydro Power Generation GmbH 8 Co. KG
/DRW/RA/2005006587 / June 13, 2005 dependence between the rotational component of the flow in the suction pipe and the vibrations of the machine. For stabilizing the flow in the suction pipe and for suppressing the torsion guide fins were used, arranged along the suction pipe.
Such guide fins may be oriented in the axial direction. Thereby the flow torsion in the suction pipe will be suppressed, but at the same time the efficiency will be lowered.
To solve the said problem, variable guide fins are used, which according to the flow conditions may be moved in and out. Further, there are used guide fins oriented parallel to the wall surfaces of the suction pipe in order to stabilize the flow by avoiding the separation of the flow. However, also structures of the said type will reduce the efficiency of the turbine. Further, fixed as well as variable finns will increase the costs of manufacture and maintenance of the turbine.
A further approach for the reduction of a torsion of the flow and its detrimental effect under partial load conditions is to feed air or water into the non-stable flow.
There have become known structures whereby air is blown into the runner or into the suction pipe either from the wall of the suction pipe or from the axis of the runner.
Further, it has become known to arrange a chamber filled with water or with air around the suction pipe, which chamber communicates with the flow in the suction pipe by openings in the suction pipe wall. Thereby, air respectively water is introduced respectively removed depending on the pressure conditions in the suction pipe flow. Here again, the costs of manufacture are increased by the said pressure chamber as well as by a respective control unit for the pressure in the chamber.
It is the objective of the invention to provide a suction pipe for a Francis turbine which develops advantageous over the prior art. More in detail, the suction pipe should minimize the effect of pressure variations such as occur at partial load PT 06062WOUS / Voith Siemens Hydro Power Generation GmbH & Co. KG
/DRW/RA/2005006587 / June 13, 2005 conditions. The said objective will be achieved by a suction pipe according to claim 1.
The inventors have acknowledged that with a Francis turbine under partial load conditions there will be created a zone of recirculation downstreams of the runner.
Within the said zone of transition and the main flow there are heavy gradients of velocity. Hydrodynamic instabilities of the Kelvin-Helmholtz-type will result in the formation of vortexes which due to the overall rotation of the flow comprise a rotative component. A rotating vortex of the said type will result in a rotating pressure which in the region of the elbow of the suction pipe generates a force acting in the axial direction, and further results in pressure variations which also act in the axial direction and therefore in the direction of the turbine. It is further possible that such axial pressure variations in combination with the helically shaped vortex - called "rope" - will result in boundary layer burbling at the wall of the elbow, thereby increasing the effect of the axially acting pressure variations.
This explains the generation of pressure variations in the suction pipe depending on the rotational speed of the runner.
A further component of so-called stochastic pressure variations may be developed by the fact that due to the helical vortex rope local pressures below the vapour pressure will be created, thereby leading to cavitation. Additional pressure pulses will occur upon bursting of the cavitation blisters.
According to the invention there is arranged in the suction pipe an elongated displacement body. The upstream end thereof is in the vicinity of the hub of the runner.
The displacement body may be rotationally symmetrically, e. g. cylindrical.
Also, it may have the shape of a truncated cone which tapers in respectively against the direction of flow. It is arranged such that its outer surface is contacted by flowing water. In general, its length axis will coincide with the length axis of the suction pipe.
PT 06062WOUS / Voith Siemens Hydro Power Generation GmbH & Co. KG
/DRW/RA/2005006587 / June 13, 2005 Numerous embodiments may be possible. The displacement body may e. g. be a projection of the hub of the runner and therefore be part of the hub. Also, it may be located at a minimum distance from the hub. The said distance may be a few millimeters only, e. g. 1, 2, 3, 5 mm, but also 10 to 50 mm.
A further embodiment may consist in making the hub longer as usual, as seen in the direction of flow, e. g. twice or three times or five times as long as what could be deemed usual, so that the hub itself would form the displacement body. A
further part will follow, located in the direction of flow. The said further part is independent of the hub, so that the said further part will not rotate.
In such a case, the said further part independent from the hub has to be fixed inside the suction pipe. Such fixing may be done by means of rods arranged perpendicularly to the flow direction at the wall of the suction pipe. The said rods may be arranged radially.
A further particularly interesting approach may consist in journalling the upstream end of the displacement body at the hub of the runner such that the displacement body will be additionally stabilized.
The invention may be used for straight suction pipes as well as for suction pipes comprising an elbow. With suction pipes with an elbow there is an additional possibility of support by fixing the displacement body in the region of the elbow at the suction pipe respectively at the foundation thereof.
The invention as well as the prior art will be explained more in detail by the figures:
Figure 1 shows an axially cut Francis turbine.
Figure 2 is a numeric flow simulation of the formation of a vortex.
Figure 3 is a suction pipe with a first embodiment of a displacement body.
PT 06062WOUS / Voith Siemens Hydro Power Generation GmbH & Co. KG
/DRW/RA/2005006587 / June 13, 2005 Figure 4 is a suction pipe with an elbow comprising a second embodiment of a displacement body.
Figure 5 is a straight suction pipe comprising a further embodiment of a displacement body.
5 Figure 6 is a suction pipe with an elbow comprising a displacement body similar to those according to Figures 3a and 3b.
Figure 7 is a suction pipe with an elbow comprising a displacement body similar to those according to Figures 4a and 4b.
Figure 8 is a suction pipe with an elbow comprising a displacement body which is solely fixed at the elbow.
The Francis turbine according to Figure 1 comprises a runner 1 with a plurality of runner vanes 1.1. The runner is rotatably journalled around runner axis 1.2.
Runner 1 is surrounded by a spiral housing 2. In front of runner 1 there are provided guide vanes 3.
The turbine is provided with a suction pipe 4. Suction pipe 4 comprises a frustroconical inlet portion 4.1 having an axis 4.1.1, followed by an elbow 4.2, which again is followed by a frustroconical outlet portion 4.3.
Inlet portion 4.1 may be shaped asymmetrical with regard to runner axis 1.2.
Many variations may be possible. Axis 4.1.1 of inlet portion 4.1 may be offset against runner axis 1.1. Axis 4.1.1 of the inlet portion may be bowed. The wall of inlet portion 4.1 may comprise a bulb at one side thereof, related to the runner axis 1.2.
The cross section of inlet portion 4.1 may be different from a circle, e. g.
elliptical.
The displacement body 5 according to the invention and the hub of runner 1 may be one single piece, so that displacement body 5 is a projection of the hub in the direction of flow. Therefore, displacement body 5 rotates together with runner 1.
PT 06062WOUS l Voith Siemens Hydro Power Generation GmbH & Co. KG
/DRW/RA/2005006587 / June 13, 2005 Figure 2 shows a numerical flow simulation of a conventional Francis turbine at partial load operation, thereby demonstrating the velocity distribution of the flow in the suction pipe due to the formation of a helical vortex rope. The vortex rope is disentangled at the elbow, thereby dissipating energy. With the said process due to the rotating pressure field of the vortex rope there will occur pressure variations which will propagate in the axial direction to the turbine. The said instable flow condition causes vibrations, depending on the speed of the runner.
Figure 3a and 3b show the inlet portion of a conventional suction pipe. The said inlet portion is of circular cross section as may be clearly seen from Figure 3b. The axis of inlet portion is straight and coincides with the runner axis.
The hub 1.3 of runner 1 (not shown) is followed by a separate displacement body 5. There is a small distance between hub 1.3 and upper end face 5.1 of displacement body 5. Displacement body 5 is supported by rods 6.1, 6.2, 6.3.
The said rods are fixedly connected to the suction pipe 4.1.
Displacement body 5 does not rotate together with the runner 1. As may be seen, its cross section is increasing in the direction of flow, In contrast to what is shown in Figures 3a and 3b, the displacement body could be located such that there would be no gap between hub 1.3 and displacement body 5, so that the upper face 5.1 of displacement body 5 could act as a support for hub 1.3. This would contribute to the stability and to the secure positioning of displacement body 5.
With the embodiment according to Figures 4a and 4b the suction pipe again comprises an elbow. Thereby, the displacement body 5 is of great axial length.
Its upper end is located at the hub of the runner (not shown) of a turbine, e. g.
of a turbine of the Kaplan type, and extends to the wall of elbow 4.2, where displacement body 5 is fixed. A further fixation may be necessary, either by means PT 06062WOUS / Voith Siemens Hydro Power Generation GmbH & Co. KG
/DRW/RA/2005006587 / June 13, 2005 of rods such as rods 6.1, 6.2 and 6.3, or by journalling the displacement body at the hub of the runner.
In case displacement body 5 is made of one single piece with hub 1.3 of runner 1, so that both parts will rotate together at the same speed, displacement body 5 may be additionally supported at suction pipe 4. The said rods 6.1, 6.2, 6.3 could journal displacement body 5 rotatably. The same applies to the embodiment according to Figures 4a and 4b at elbow 4.2.
The lowermost end of displacement body 5 may have the shape of a shell.
Alternatively, it may be rounded.
Figure 7 is a suction pipe with an elbow comprising a displacement body similar to those according to Figures 4a and 4b.
Figure 8 is a suction pipe with an elbow comprising a displacement body which is solely fixed at the elbow.
The Francis turbine according to Figure 1 comprises a runner 1 with a plurality of runner vanes 1.1. The runner is rotatably journalled around runner axis 1.2.
Runner 1 is surrounded by a spiral housing 2. In front of runner 1 there are provided guide vanes 3.
The turbine is provided with a suction pipe 4. Suction pipe 4 comprises a frustroconical inlet portion 4.1 having an axis 4.1.1, followed by an elbow 4.2, which again is followed by a frustroconical outlet portion 4.3.
Inlet portion 4.1 may be shaped asymmetrical with regard to runner axis 1.2.
Many variations may be possible. Axis 4.1.1 of inlet portion 4.1 may be offset against runner axis 1.1. Axis 4.1.1 of the inlet portion may be bowed. The wall of inlet portion 4.1 may comprise a bulb at one side thereof, related to the runner axis 1.2.
The cross section of inlet portion 4.1 may be different from a circle, e. g.
elliptical.
The displacement body 5 according to the invention and the hub of runner 1 may be one single piece, so that displacement body 5 is a projection of the hub in the direction of flow. Therefore, displacement body 5 rotates together with runner 1.
PT 06062WOUS l Voith Siemens Hydro Power Generation GmbH & Co. KG
/DRW/RA/2005006587 / June 13, 2005 Figure 2 shows a numerical flow simulation of a conventional Francis turbine at partial load operation, thereby demonstrating the velocity distribution of the flow in the suction pipe due to the formation of a helical vortex rope. The vortex rope is disentangled at the elbow, thereby dissipating energy. With the said process due to the rotating pressure field of the vortex rope there will occur pressure variations which will propagate in the axial direction to the turbine. The said instable flow condition causes vibrations, depending on the speed of the runner.
Figure 3a and 3b show the inlet portion of a conventional suction pipe. The said inlet portion is of circular cross section as may be clearly seen from Figure 3b. The axis of inlet portion is straight and coincides with the runner axis.
The hub 1.3 of runner 1 (not shown) is followed by a separate displacement body 5. There is a small distance between hub 1.3 and upper end face 5.1 of displacement body 5. Displacement body 5 is supported by rods 6.1, 6.2, 6.3.
The said rods are fixedly connected to the suction pipe 4.1.
Displacement body 5 does not rotate together with the runner 1. As may be seen, its cross section is increasing in the direction of flow, In contrast to what is shown in Figures 3a and 3b, the displacement body could be located such that there would be no gap between hub 1.3 and displacement body 5, so that the upper face 5.1 of displacement body 5 could act as a support for hub 1.3. This would contribute to the stability and to the secure positioning of displacement body 5.
With the embodiment according to Figures 4a and 4b the suction pipe again comprises an elbow. Thereby, the displacement body 5 is of great axial length.
Its upper end is located at the hub of the runner (not shown) of a turbine, e. g.
of a turbine of the Kaplan type, and extends to the wall of elbow 4.2, where displacement body 5 is fixed. A further fixation may be necessary, either by means PT 06062WOUS / Voith Siemens Hydro Power Generation GmbH & Co. KG
/DRW/RA/2005006587 / June 13, 2005 of rods such as rods 6.1, 6.2 and 6.3, or by journalling the displacement body at the hub of the runner.
In case displacement body 5 is made of one single piece with hub 1.3 of runner 1, so that both parts will rotate together at the same speed, displacement body 5 may be additionally supported at suction pipe 4. The said rods 6.1, 6.2, 6.3 could journal displacement body 5 rotatably. The same applies to the embodiment according to Figures 4a and 4b at elbow 4.2.
The lowermost end of displacement body 5 may have the shape of a shell.
Alternatively, it may be rounded.
Claims (9)
1. Water - turbine or - pump or - pump turbine comprising a runner (1.1 ) with a plurality of runner vanes as well as with a hub (1.3);
1.2 with a housing, comprising a guide device for adjusting the flow of water into the runner (1.1);
1.3 with a suction pipe (4) for guiding the water flowing out of the runner, the suction pipe (4) comprising an inlet portion;
characterized by the following features:
1.4 in the suction pipe (4) there is provided an elongated displacement body (5);
1.5 the upstream end of the displacement body (5) is located in the vicinity of the hub (1.3) of runner (1)
1.2 with a housing, comprising a guide device for adjusting the flow of water into the runner (1.1);
1.3 with a suction pipe (4) for guiding the water flowing out of the runner, the suction pipe (4) comprising an inlet portion;
characterized by the following features:
1.4 in the suction pipe (4) there is provided an elongated displacement body (5);
1.5 the upstream end of the displacement body (5) is located in the vicinity of the hub (1.3) of runner (1)
2. Turbine or pump according to claim 1, characterized in that the distance between hub 1.3 of runner (1) and the upstream end (5.1) of displacement body 5 is between 0.5 and 50 mm.
3. Turbine or pump according to claims 1 or 2, characterized in that the displacement body (5) is supported at the suction pipe 4 by rods 6.1, 6.2, 6.3.
4. Pump or turbine according to either one of claims 1 to 3, characterized in that the displacement body (5) is supported at the hub (3) of runner (1).
5. Pump or turbine according to either one of claims 1 to 4, characterized in that the displacement body (5) and the hub (1.3) of runner (1) are made of one single piece and are rotating together.
6. Turbine or pump according to either one of claims 1 to 3, characterized in that the suction pipe (4) is straight.
7. Pump or turbine according to either one of claims 1 to 5, characterized in that the suction pipe (4) is bowed.
8. Pump or turbine according to either one of claims 1 to 7, characterized in that the displacement body (5) tapers in the direction of flow.
9. Pump or turbine according to either one of claims 1 to 7, characterized in that the displacement body (5) tapers against the direction of flow.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE10258557.1 | 2002-12-14 | ||
| DE10258557A DE10258557A1 (en) | 2002-12-14 | 2002-12-14 | Method and device for reducing pressure fluctuations in the intake manifold of a water turbine or pump or pump turbine |
| PCT/EP2003/013664 WO2004055362A1 (en) | 2002-12-14 | 2003-12-04 | Method and device for reducing pressure fluctuations in an induction pipe of a water turbine or water pump or water-pump turbine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2510130A1 true CA2510130A1 (en) | 2004-07-01 |
Family
ID=32477653
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002510130A Abandoned CA2510130A1 (en) | 2002-12-14 | 2003-12-04 | Method and device for reducing pressure fluctuations in an induction pipe of a water turbine or water pump or water-pump turbine |
Country Status (9)
| Country | Link |
|---|---|
| US (1) | US20070009352A1 (en) |
| EP (1) | EP1570175B1 (en) |
| KR (1) | KR20050091721A (en) |
| CN (1) | CN100408847C (en) |
| AU (1) | AU2003296608A1 (en) |
| BR (1) | BR0317307A (en) |
| CA (1) | CA2510130A1 (en) |
| DE (2) | DE10258557A1 (en) |
| WO (1) | WO2004055362A1 (en) |
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| CN101158328B (en) * | 2007-10-12 | 2010-04-21 | 杭州电子科技大学 | Novel draft-tube and preparation method thereof |
| ATE511606T1 (en) * | 2008-10-01 | 2011-06-15 | Grundfos Management As | CENTRIFUGAL PUMP UNIT |
| FR2942274B1 (en) | 2009-02-18 | 2014-04-18 | Alstom Hydro France | HYDRAULIC ENERGY CONVERSION INSTALLATION AND METHOD OF CONTROLLING SUCH INSTALLATION |
| DE102011015336A1 (en) | 2011-03-28 | 2012-01-12 | Voith Patent Gmbh | Hydraulic machine has impeller, housing provided upstream to impeller and suction pipe provided downstream to impeller, where compressed air line is provided for introduction of compressed air in working space |
| CN102322382B (en) * | 2011-06-02 | 2013-03-27 | 杭州电子科技大学 | Draft tube based on vibrating vortex generators |
| JP5956885B2 (en) * | 2012-09-19 | 2016-07-27 | 株式会社東芝 | Hydraulic machine and operation method thereof |
| CN103114956B (en) * | 2012-12-07 | 2015-08-05 | 哈尔滨电机厂有限责任公司 | Current stabilization making-up air device reduces the method for draft tube pressure pulsation amplitude |
| CA2908772A1 (en) * | 2013-04-08 | 2014-10-16 | Voith Patent Gmbh | Device and method for reducing pressure fluctuations in the suction pipe of a water turbine or water pump or water pump turbine |
| KR20170001332A (en) | 2015-06-26 | 2017-01-04 | 현대중공업 주식회사 | Apparatus for reducing pressure fluctuation of pump |
| CN105275711A (en) * | 2015-10-16 | 2016-01-27 | 江苏大学 | Hydraulic design method for bent tail water pipe of hydraulic turbine device |
| CN105240186A (en) * | 2015-10-16 | 2016-01-13 | 江苏大学 | Hydraulic design method for tail water pipe of small hydraulic turbine device |
| CN106825657B (en) * | 2017-02-28 | 2019-04-02 | 哈尔滨善思科技有限责任公司 | A method of 4 holes are made a call to based on the inclined operating condition hydraulic turbine draft cone of big flow |
| US11834952B2 (en) | 2022-03-02 | 2023-12-05 | General Electric Company | Exhaust frequency mitigation apparatus |
Family Cites Families (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1897501A (en) * | 1922-01-14 | 1933-02-14 | Taylor Harvey Birchard | Draft tube structure |
| US1690237A (en) * | 1923-10-31 | 1928-11-06 | Moody Lewis Ferry | Hydraulic turbine |
| US1919376A (en) * | 1929-01-11 | 1933-07-25 | Moody Lewis Ferry | Reversible pump turbine |
| US2010555A (en) * | 1931-05-26 | 1935-08-06 | Moody Lewis Ferry | Hydraulically reversible pumpturbine |
| US2079258A (en) * | 1933-08-15 | 1937-05-04 | Baldwin Southwark Corp | Cavitation control of hydraulic machines |
| US2262191A (en) * | 1940-06-26 | 1941-11-11 | Lewis F Moody | Pump |
| CH328203A (en) * | 1953-04-17 | 1958-02-28 | Neyrpic Ets | Reaction water turbine |
| GB799013A (en) * | 1955-05-06 | 1958-07-30 | English Electric Co Ltd | Improvements in and relating to hydraulic reaction turbines |
| FR1162872A (en) * | 1955-12-19 | 1958-09-18 | Karlstad Mekaniska Ab | Device for francis turbine wheel |
| US3292901A (en) * | 1965-03-04 | 1966-12-20 | Newport News S & D Co | Turbine apparatus |
| CN2081436U (en) * | 1990-12-01 | 1991-07-24 | 黄国宏 | Mixed flow hydraulic turbine drainage awl stretching taper sleeve (conical pipe) |
-
2002
- 2002-12-14 DE DE10258557A patent/DE10258557A1/en not_active Withdrawn
-
2003
- 2003-12-04 BR BR0317307-0A patent/BR0317307A/en not_active Application Discontinuation
- 2003-12-04 CA CA002510130A patent/CA2510130A1/en not_active Abandoned
- 2003-12-04 WO PCT/EP2003/013664 patent/WO2004055362A1/en not_active Application Discontinuation
- 2003-12-04 CN CNB2003801037944A patent/CN100408847C/en not_active Expired - Lifetime
- 2003-12-04 US US10/538,957 patent/US20070009352A1/en not_active Abandoned
- 2003-12-04 AU AU2003296608A patent/AU2003296608A1/en not_active Abandoned
- 2003-12-04 KR KR1020057010819A patent/KR20050091721A/en not_active Application Discontinuation
- 2003-12-04 DE DE50304308T patent/DE50304308D1/en not_active Expired - Lifetime
- 2003-12-04 EP EP03813105A patent/EP1570175B1/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| CN1714237A (en) | 2005-12-28 |
| KR20050091721A (en) | 2005-09-15 |
| WO2004055362A1 (en) | 2004-07-01 |
| DE10258557A1 (en) | 2004-07-08 |
| CN100408847C (en) | 2008-08-06 |
| DE50304308D1 (en) | 2006-08-31 |
| AU2003296608A1 (en) | 2004-07-09 |
| US20070009352A1 (en) | 2007-01-11 |
| EP1570175B1 (en) | 2006-07-19 |
| EP1570175A1 (en) | 2005-09-07 |
| BR0317307A (en) | 2005-11-08 |
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