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
  • F03B1/00—Engines of impulse type, i.e. turbines with jets of high-velocity liquid impinging on blades or like rotors, e.g. Pelton wheels; Parts or details peculiar thereto
  • F03B1/02—Buckets; Bucket-carrying rotors
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
  • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
  • F05B2260/00—Function
  • F05B2260/30—Retaining components in desired mutual position
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
  • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
  • F05B2260/00—Function
  • F05B2260/30—Retaining components in desired mutual position
  • F05B2260/301—Retaining bolts or nuts
• • 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
• • 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
  • Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
  • Y02P70/00—Climate change mitigation technologies in the production process for final industrial or consumer products
  • Y02P70/50—Manufacturing or production processes characterised by the final manufactured product
• • 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
  • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
  • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
  • Y10T29/00—Metal working
  • Y10T29/49—Method of mechanical manufacture
  • Y10T29/49316—Impeller making
  • Y10T29/4932—Turbomachine making
  • Y10T29/49321—Assembling individual fluid flow interacting members, e.g., blades, vanes, buckets, on rotary support member

Definitions

• the invention relates to a wheel intended to equip a Pelton-type turbine used in a hydraulic energy conversion installation into mechanical or electrical energy.
• the invention also relates to a turbine equipped with such a wheel and a method of manufacturing such a wheel.
• a Pelton turbine In the case of a hydro-electric installation, a Pelton turbine is associated with a generator to produce electric power.
• a one-piece Pelton turbine wheel is a bulky object that is difficult to machine and transport. It is known, for example from WO-A-99/49213, to manufacture a Pelton turbine wheel from a rim on which individual buckets are mounted, by means of bolts, whereas force recovery flanges. are arranged around the buckets. This type of material is satisfactory in many cases of use.
• the aim of the invention is to propose an alternative solution in which independent buckets are used in a Pelton turbine wheel, without it being necessary to use an external flange for taking up the force or to perform precise machining of the flanges. foot anchors buckets and while the assembly of the turbine wheel is durable.
• the invention relates to a Pelton turbine wheel which comprises several subassemblies distributed around an axis of rotation of the wheel and which each comprise a bucket and an anchor foot.
• This wheel is characterized in that a circular section cylindrical locking pin is arranged, in a direction parallel to the axis of rotation of the wheel, between each pair of two adjacent anchoring legs, this pin being engaged both in two housings respectively formed in the two aforementioned anchor feet and in that the pins are arranged in the housing with the possibility of relative displacement of the subsets under load and movement of the pins engaged in the housing, until the pins block the different anchor feet relative to each other.
• the manufacture of the turbine wheel according to the invention is easy insofar as the subassemblies can be manufactured independently of each other before being assembled to form the turbine wheel.
• These different sub-assemblies are relatively easy to machine, with relatively wide manufacturing tolerances and their dimensions make it possible to manufacture them on conventional machining centers, and not on machining centers dedicated to large parts. Maintenance operations are also facilitated to the extent that the subassemblies can be mounted and disassembled individually with respect to the turbine wheel.
• the locking pins disposed at the interface between two adjacent anchoring feet make it possible to lock these feet relative to each other during a rotation under load of the wheel, which limits the relative sliding of the subassemblies with each other.
• the pins are arranged in the slots with clearance, which allows the relative sliding of the anchoring feet for their wedging by the pins.
• a Pelton turbine wheel may incorporate one or more of the following characteristics, taken in technically permissible combination:
• the inner diameter of a circular section cylindrical volume formed by a pair of housings in two adjacent anchoring feet is strictly greater than the diameter of the portion of the pin engaged in this volume.
• Each anchor foot is provided on each of its two sides facing respectively to the two adjacent anchoring feet, a housing partially receiving a locking pin.
• Each housing of an anchoring foot is in the form of a cylinder, with a section corresponding to half of the section of the locking pin that it receives.
• Each anchor foot is provided with at least one heel adapted to come into contact with an annular ring, which surrounds the anchoring feet, under the effect of the centrifugal force resulting from the rotation of the wheel.
• the subassemblies are mounted directly on the end of the turbine shaft, without the use of a force recovery flange.
• the subassemblies are mounted on the end of the turbine wheel by means of at least one annular coupling flange.
• This flange can be supported against a counter-flange on which are mounted anchor feet.
• the flange or the counter-flange advantageously form a hoop capable of receiving bearing the heels of the anchoring feet under the effect of the centrifugal force.
• at least one hoop is arranged around the anchoring feet, independently of the coupling flange.
• the invention also relates to a Pelton turbine which is equipped with a wheel as mentioned above.
• a Pelton turbine which is equipped with a wheel as mentioned above.
• Such a turbine can be manufactured more economically than those of the state of the art and its maintenance is facilitated.
• the invention also relates to a method of manufacturing a Pelton turbine wheel as mentioned above and, more specifically, to a method which comprises the steps of: a) mounting the sub-assemblies on a circular structure b) arranging, in a direction parallel to the axis of rotation of the wheel, a cylindrical and circular section locking pin in two housings respectively formed in each pair of two adjacent anchoring legs and c) subjecting the wheel to load rotation during which the subassemblies move relative to each other and move the engaged pins into their housings, up to that the pins block the different anchoring feet relative to each other.
• an anchor foot tends to slide radially towards the axis of rotation, a portion of the surface defining a housing in this foot abuts against the pin inserted in this housing and the pin bears against a portion of a surface defining a housing in an adjacent anchor foot.
• FIG. 1 is a front view of a turbine wheel according to the invention mounted on the shaft of a turbine also according to the invention;
• FIG. 2 is a section along the line N-II in Figure 1;
• FIG. 3 is a perspective view of a trough subassembly used in the wheel of FIGS. 1 and 2;
• FIG. 4 is a schematic representation of two anchoring feet belonging to subassemblies such as that represented in FIG. 3, in a first configuration;
• - Figure 5 is a view similar to Figure 4 when the anchoring feet are in a second configuration;
• FIG. 6 is a view similar to Figure 1 for a turbine wheel according to a second embodiment;
• - Figure 7 is a section along the line VII-VII in Figure 6;
• Figure 8 is a section similar to Figure 7 for a turbine wheel according to a third embodiment of the invention.
• Figure 9 is a section similar to Figure 7 for a turbine wheel according to a fourth embodiment of the invention.
• the wheel 1 shown in FIGS. 1 and 2 belongs to a Pelton-type turbine T and is mounted on the end 21 of the shaft 2 of this turbine.
• the wheel 1 is formed by the assembly of independent sub-assemblies 11, one of which is visible in perspective in FIG. 3 and which is formed of a molded stainless steel one-piece part.
• the subsets 11 may be made of forged stainless steel or composite material, which allows to reduce their mass and the inertial forces resulting from the rotation of the shaft.
• Each subassembly 11 defines a trough 111 delimiting two bowls 1111 and 1112 separated by a ridge 1113.
• the trough 111 of a subassembly 11 is in one piece with an anchor foot 112 which generally has a right prism shape of which the base has the shape visible in Figure 1.
• the anchoring foot 112 of a subassembly 11 is provided with two holes 1121 and 1122 receiving studs 12 for mounting the subassembly 11 on the end 21 of the shaft 2.
• the two holes 1121 and 122 are aligned along a radius Rn extending radially relative to the axis of rotation X 2 of the shaft 2, which coincides with the central axis Xi of rotation of the wheel 1 in the mounted configuration thereof.
• the anchoring feet 112 are arranged side by side on the end 21 of the shaft 2. Note 1123 the side of a foot 112 facing the axis X in mounted configuration of the wheel. 1124 and 1125 respectively denote the sides of a foot 112 facing the adjacent feet in the mounted configuration of the wheel 1.
• the side 1124 is disposed, relative to the holes 1121 and 1122, on the concave side of the trough 111, then that the side 1125 is located, relative to these holes, the convex side of the bucket.
• a cylindrical housing 1126 with a semicircular section is formed on the side 1124 and opens on this side, while a cylindrical housing 1127 with a semicircular section is formed on the side 1125 and opens on this side.
• All the anchoring feet 112 are provided with housings 1126 and 1127 on their respective sides 1124 and 1125, so that when two anchoring feet are arranged side by side, in the configuration shown in FIG. 1, a housing 1126 or 1127 of each foot 112 is arranged facing a corresponding housing 1127 or 1126 of an adjacent foot. It is thus formed pairs of housings 1126-1127 which together constitute a cylindrical volume of substantially circular section in which can be engaged a locking pin 13 which is cylindrical, monobloc and circular section.
• the internal diameter Dj of a cylindrical volume defined by a pair of housings 1126-1127 is slightly greater than the diameter Di 3 of the portion of a pin 13 which enters this volume.
• the trace of the anchor foot 112 'of a subset adjacent to that shown in the mounted configuration of the wheel 1 is shown in dashed lines.
• the housing 1126 'of this second anchor foot 112' defines with the housing 1127 a volume V 13 for receiving a pin 13, which can be introduced in this volume in the direction of the arrow Fi 3 in this figure, c that is to say in a direction parallel to the axes X 1 and X 2 .
• the anchoring feet 112 and the end 21 are dimensioned such that, when the wheel 1 is mounted on the shaft 2, the facing faces 1124 and 1125 of the different feet 112 are not in contact.
• the anchor foot 112 of a subassembly 11 comprises a surface 1128 opposite to the surface 1123 and which delimits a heel 1128A projecting from the surface 1129 in which the hole 1122 opens, in the vicinity of the surface 1128.
• the end 21 of the shaft 2 is, in turn, provided with an end flange 211 which delimits, with the front face 212 of the end 21, a shoulder 213 for receiving the heel 1128A in a mounted configuration of a subassembly 11 on the shaft 2.
• Each peg 13 is equipped at one of its ends with a head 131 which is engaged in a countersink 1126A or 1127A which borders each housing 1126 or 1127 in the vicinity of the surface 1129.
• the pegs can enter the housing 1126. and 1127 by the side of the surface 1129, engaging their end opposite their head 131 in these housings, in the direction of the arrows Fi 3 in Figure 3.
• the pins 13 may be inserted into the volumes V13 by the side of the feet 112 opposite the surface 1129. In this case, the countersinks 1126A and 1127A are removed in the vicinity of the surface 1129.
• the assembly of the wheel 1 on the shaft 2 takes place by positioning each anchoring foot 112 on the end 21 of the shaft 2 so that its holes 1121 and 1122 come opposite corresponding holes 214 and 215 formed in the end 21 and allowing the passage of studs 12.
• the pins 13 are interposed between the feet 112, as the subassemblies 11 are installed on the shaft 2, being installed with their axes X 13 respectively parallel to the axes Xi and X 2 then merged.
• the studs 12 are then tensioned, respectively in the holes 1121 and 214, on the one hand, 1122 and 215, on the other hand, for each subassembly 11.
• the subassemblies 11 are pre-positioned on a support jig, then the pins 13 are placed in the volumes V13 through the surface 1129 and the wheel thus formed is mounted on the plate of the shaft 2. Then, the studs 12 are put in tension.
• 1127 define, in pairs, volumes V 13 for receiving the locking pins 13. It can be seen in FIG. 2 that the pins 13 do not penetrate into the end
• the pins 13 ensure the stability of the wheel 1 thus formed.
• the subassemblies 11 are pressed against an internal shoulder 213 of the end 21 of the shaft 2, under the effect of the centrifugal force. These subassemblies tend to pivot relative to the shaft 2, which induces that each anchor foot is strongly pressed against a pin 13 engaged in its housing 1127 and that this phenomenon is repeated for all subassemblies 11 of the wheel 1.
• the different subassemblies slightly move the pins 13 relative to the shaft 2, under the effect of their pivoting, which is possible since the pins 13 are not integral with the shaft 2.
• L effort made by each trough 111 of the makes the jet causes a relative sliding of the subassemblies 11 relative to the shaft 2 and wedges these subsets with respect to each other through the action of the pins 13.
• the pins 13 ensure a perennial mounting different subassemblies 11 on the shaft 2, by blocking the different anchoring feet 112 relative to each other.
• Figures 4 and 5 on which the heads 131 have been omitted for clarity of the drawing, schematize this phenomenon and represent two anchoring feet 112 and a pin 13 respectively before and after the first start of the wheel 1.
• the pin 13 Before the first starting, the pin 13 is mounted in the volume V 13 defined jointly by the housing 1126 and 1127 of the feet 112.
• the feet 112 slide the relative to each other, as represented by the arrow F 2 in Figure 5.
• the foot 112 shown in the upper part of this figure tends to slide radially inward relative to the foot 112 shown in the lower part, which has the effect of bringing a portion 1126B of the surface defining the housing 1126 in abutment against the pin 13 and to bring the pin 13 in abutment against a portion 1127B of the surface defining the housing 1127 of the foot 112 shown in the upper part pool.
• the portions 1126B and 1127B of the surfaces of the housings 1126 and 1127 thus form zones of contact between the pin 13 and the anchoring feet 112, the zone 1126B being radially closer to the axis Xi than the central axis X13 of the pin 13, which is closer to the axis Xi than the zone 1127B.
• the pins 13 are mounted in the housings 126 and 127 with play, thanks to the difference between the diameters Dj and D13, and the first rotation of the wheel 1 under load has the effect of making up the game, thanks relative sliding F 2 of the anchoring feet 112 relative to each other.
• the relative position of the various anchoring feet which was obtained after sliding during the first start, is maintained because of the frictional forces between the parts 112 and 13 assembled .
• the powders increasing the coefficient of friction between their respective surfaces in contact. This ensures that the friction between the surfaces is able to prevent slippage between the anchoring feet 112 and the pins 13 during the starting and stop, or during normal operation, after the first rotation of the wheel.
• the radial expansion movement of the wheel 1, under the effect of the centrifugal force due to its rotation, is limited by the fact that the heels 1128A of the anchoring feet 112 are arranged at the level of the shoulder 213 of the end 21.
• the radial expansion of the wheel 1 is limited by the support of the surface 1128 of each anchoring foot 112 against the flange 211 which constitutes a radial stop for the feet 111 of the subwoofers. sets 11.
• the first embodiment of the invention described with reference to Figures 1 to 5 is more particularly applicable to the manufacture of a new turbine whose shaft 2 can be configured, forming the flange 211 and the holes 214 and 215, to directly receive the subassemblies 11, without the use of a force recovery flange as explained above.
• the invention can also be used with a turbine T whose shaft 2 has a flat end, as shown in FIGS. 6 to 9. This is particularly useful when rehabilitating an existing turbine whose shaft does not have to be exchange.
• the pins 13 are mounted with play in the cylindrical volumes formed by housing of the housing type.
• the wheel 1 of the Pelton turbine T is formed by subassemblies 11 which comprise, as in the first embodiment, buckets 111 and
• the end 21 of the shaft 2 has a flat front face 212.
• the attachment of the wheel 1 with the shaft 2 is obtained by means of coupling studs 12 which pass through a flange 14 provided with a collar 141 of axial support of the inner radial portion of the anchoring feet 112 against the front face 212.
• the studs 12 pass through bores 214 formed in the end 21, these bores may pre-exist in case of rehabilitation of the turbine T.
• the distribution of the drill holes 142 of the studs 12 in the flange 14 is then adapted to that of the holes 214.
• Two frets 15A and 15B are arranged on either side of the anchoring feet 112 and make it possible to resist the radial expansion of the wheel 1 under the effect of the centrifugal force during the rotation of the turbine T, in particular in case of runaway. Heels 1128A and 1128B are formed in the feet 112 to respectively abut against the bands 15A and 15B under the effect of the centrifugal force. As previously, blocking pins 13 are introduced into housings, of the type of housings 1126 and 1127 of the first embodiment, at the interface between two adjacent anchoring feet 112.
• a flange 14 is also used to press the anchoring feet 112 of the subassemblies 11 of a wheel 1 against the flat front face 212 of the shaft 2 of a Pelton turbine T.
• blocking pins 13 are used to limit the relative sliding of the anchoring feet 112.
• a counter-flange 16 receives the support flange 14 and is provided with holes 161 and 162 for the passage of locking studs. 12 similar to those of the first embodiment.
• the counter-flange 16 forms a flange 163 which functions as a hoop for a heel 1128A of the anchor foot 112 of each subassembly 11.
• main pins 17 are used to axially press the flange 14 and the feet 112 towards the shaft 2, as in the second embodiment.
• wheel 1 includes sub-components assemblies 11 each comprising a trough 111 and a foot 112 and locking pins 13, which limit the relative sliding between the anchoring feet 112.
• the flange 14 forms a hoop 145 against which is supported a heel 1128A of each 112.
• the number of subassemblies 11, studs 12 and blocking pins 13 results from a design choice of those skilled in the art.
• the pins 13 are not necessarily circular section. In this case, the geometry of the housings 1126 and 1127 is adapted to that of the pins.
• a coating increasing the coefficient of friction between the parts 11 and 2, and possibly between these parts and the parts 14 and 145, can be used at the interface between these parts, this to ensure the maintenance position in friction by subassemblies 11 in operation.
• an advantage of a Pelton turbine wheel according to the invention lies in the fact that the buckets which constitute it are "self-locking" under the effect of the centrifugal force and the load on the buckets during a first rotation.
• the relatively large play between the anchoring feet of the buckets induce that they are in contact only through the locking pins and not by direct support against each other, which facilitates the disassembly and change of one or more buckets when needed.
• the relative positioning of the anchoring feet of the buckets by relative sliding during the first rotation is quite advantageous compared to the devices of the prior art in which such a sliding phenomenon can not be implemented. .

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• Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Turbine Rotor Nozzle Sealing (AREA)
• Hydraulic Turbines (AREA)
• Structures Of Non-Positive Displacement Pumps (AREA)

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• 2007
  • 2007-10-30 FR FR0758676A patent/FR2922967B1/fr active Active
• 2008
  • 2008-10-29 MX MX2010004858A patent/MX2010004858A/es active IP Right Grant
  • 2008-10-29 CA CA2703984A patent/CA2703984C/fr not_active Expired - Fee Related
  • 2008-10-29 KR KR1020107011647A patent/KR101501911B1/ko not_active Expired - Fee Related
  • 2008-10-29 AU AU2008320687A patent/AU2008320687B2/en not_active Ceased
  • 2008-10-29 JP JP2010531563A patent/JP5409643B2/ja not_active Expired - Fee Related
  • 2008-10-29 US US12/739,797 patent/US8540489B2/en not_active Expired - Fee Related
  • 2008-10-29 CN CN2008801216557A patent/CN101903644B/zh not_active Expired - Fee Related
  • 2008-10-29 BR BRPI0818792 patent/BRPI0818792A2/pt not_active Application Discontinuation
  • 2008-10-29 MY MYPI2010001908A patent/MY154854A/en unknown
  • 2008-10-29 WO PCT/FR2008/051945 patent/WO2009056761A2/fr not_active Ceased
  • 2008-10-29 EP EP08844444A patent/EP2207956A2/fr not_active Withdrawn

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