WO2010079309A1 - Pompe a dispositif d'equilibrage axial. - Google Patents
Pompe a dispositif d'equilibrage axial. Download PDFInfo
- Publication number
- WO2010079309A1 WO2010079309A1 PCT/FR2010/050027 FR2010050027W WO2010079309A1 WO 2010079309 A1 WO2010079309 A1 WO 2010079309A1 FR 2010050027 W FR2010050027 W FR 2010050027W WO 2010079309 A1 WO2010079309 A1 WO 2010079309A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- downstream
- nozzle
- stator
- passage
- upstream
- Prior art date
Links
- 239000012530 fluid Substances 0.000 claims abstract description 62
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 60
- 238000006073 displacement reaction Methods 0.000 claims description 8
- 210000003462 vein Anatomy 0.000 claims description 3
- 239000001257 hydrogen Substances 0.000 claims description 2
- 229910052739 hydrogen Inorganic materials 0.000 claims description 2
- 239000007788 liquid Substances 0.000 claims description 2
- 230000002093 peripheral effect Effects 0.000 claims description 2
- 238000005086 pumping Methods 0.000 claims description 2
- 238000011067 equilibration Methods 0.000 claims 1
- 125000004435 hydrogen atom Chemical class [H]* 0.000 claims 1
- 239000007789 gas Substances 0.000 description 2
- 238000003754 machining Methods 0.000 description 2
- 238000011084 recovery Methods 0.000 description 2
- UFHFLCQGNIYNRP-UHFFFAOYSA-N Hydrogen Chemical compound [H][H] UFHFLCQGNIYNRP-UHFFFAOYSA-N 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 230000006378 damage Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000009472 formulation Methods 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/042—Axially shiftable rotors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/041—Axial thrust balancing
- F04D29/0416—Axial thrust balancing balancing pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/2261—Rotors specially for centrifugal pumps with special measures
- F04D29/2266—Rotors specially for centrifugal pumps with special measures for sealing or thrust balance
Definitions
- the present invention relates to the axial balancing of a pump, in particular a turbopump, in particular a space engine. It is known that the rotors of these machines support often considerable axial thrusts due to the pressure differences that are established on either side of the wheels, to the variations in the amount of movement of the fluids conveyed and, in some cases, to the weight or at a fraction of the weight of the rotor itself. As a result, there are usually devices in the pumps for compensating the axial thrust exerted by the fluid on the rotor.
- FIGS. 1 and 2 show such a device for balancing known axial thrust, arranged between a wheel 11 and a stator 12.
- the turbopump of FIG. 1 essentially comprises a rotating assembly constituted around a central shaft 26, of reduced length, and comprising a single blade impeller 11 of a single stage centrifugal pump mounted on the shaft 26, in the middle portion thereof. ci, as well as two turbine wheels 22, mounted on the shaft 26 in the rear portion thereof.
- FIG. 1 shows, for the single-stage pump, an open-type impeller 11 with vanes 6 receiving the working fluid through a suction channel 2 and discharging the pressurized working fluid through a suction channel. repression 3.
- the working fluid is introduced axially through the inlet section 28 and passes directly into the suction channel 2 of the pump.
- This device for axial balancing or axial thrust balancing of the rotating assembly is integrated with the impeller 11 and comprises a single rear balancing chamber 18 interposed between the rear part of the wheel 11 and a portion of the stator 12, and a passage 20 connecting the rear balancing chamber to the fluid stream.
- a balancing chamber is a chamber in which there is a fluid pressure, the action of this pressure on a movable member (here, the rotor) for regulating and controlling the position of said movable member.
- the front face of this wheel 11 receives the pressure of the fluid stream 14 which tends to move the rotor 10 rearwardly.
- the fluid pressure in the rear balancing chamber 18 instead tends to move the rotor 10 forward. Equilibrium is achieved when these forces compensate axially, the force exerted by the fluid on the rotor 10 at the rear chamber 18 then compensating for the axial resultant forces exerted by the fluid on the other parts of the rotor, during the various phases of operation of the pump.
- the axial balancing device modulates the supply pressure of the rear chamber 18, via the axial displacement of the rotor, as follows:
- the fluid transfer passage 20 has a radial nozzle 40 extending between the rotating wall connected to the rotor 10, that is to say to the centrifugal wheel 11, and a wall facing the stator. 12, i.e. a fixed wall of the pump.
- the section for the fluid passage of this radial nozzle depends on the relative axial position of the rotor and the stator; It increases when the rotor moves backwards (increase in thickness A of fluid film passing through passage 20, in FIG. 2, when wheel Ii moves to the right), which causes an increase in flow rate. entering the back bedroom, a climb from the pressure in the rear chamber, and therefore an increase in the restoring force exerted by the fluid on the rotor tending to push it forward. Conversely, if the rotor 10 tends to move forward (to the detriment of the thickness of fluid film), by a reverse mechanism the return force decreases which causes the rotor to return further back.
- the displacement of the rotor makes it possible to modulate the pressure in the rear balancing chamber 18, and thus to keep the rotor in a substantially constant axial position, and this advantageously with a minimum of friction.
- the system is self-regulating, and tends to keep the rotor in its equilibrium position.
- the fluid passage section is inherently variable, the only degree of freedom available to the designer to vary the effect of the device and therefore the pressure drop between upstream and downstream.
- the downstream of this passage is the radial distance B traversed by the fluid in the nozzle of the passage, which in this case corresponds to the distance between the inner and outer radii of the crown that forms this nozzle.
- this distance B may not be sufficient to obtain the pressure drop required to achieve axial thrust balancing, particularly in the case of a single-stage centrifugal pump open: In this case indeed , the only surface on which we can come to circulate fluid is the balancing piston located at the back of the wheel. In multi-stage pumps, each wheel can contribute to the axial balancing of the pump.
- the object of the invention is to overcome the aforementioned disadvantages by defining a pump comprising a stator, a rotor comprising at least one impeller, and an axial balancing device arranged on at least one impeller of the rotor in which ( or in particular, but not exclusively, having a wall, in particular a front wall, against which passes a stream of fluid, said device comprising for each wheel involved in this device, a balancing chamber extending between a wall of said involved wheel and the stator, and a passage arranged between said wheel involved and the stator, allowing a discharge of fluid from said vein of fluid to said balancing chamber, said rotor having a slight axial clearance allowing limited axial displacement, the fluid pressure in the balancing chamber (s) can thus compensate for the pressures exerted by the fluid on the other parts of the rotor to achieve r axial balancing of the rotor; pump whose axial thrust balancing device is achievable with the conventional machining means, and has an optimized radial and
- said passage comprising an upstream nozzle and a downstream nozzle, both axially variable, extending between two crown walls facing each other with a positive, zero or negative overlap, respectively of the wheel involved and of the stator, and an intermediate annular chamber arranged between walls of the involved wheel and the stator, opening downstream of the upstream nozzle and upstream of the downstream nozzle of said passage.
- the jet of fluid is passed through and circulate in the intermediate chamber, wherein it dissipates its kinetic energy by swirling, resulting in increased pressure loss on both sides of the passage.
- the term "chamber” here implies that the annular chamber is distinguished from the upstream and downstream nozzles by a large passage section relative to that of the nozzles, which can be in particular greater than triple their passage section.
- said upstream and downstream nozzles are annular parts of the passage presenting sections that are particularly small relative to the remainder of the passage, or at least smaller than the average section thereof.
- These nozzles are said to be axially variable, since their passage sections vary as a function of the axial displacements of the rotor relative to the stator.
- An example of an axially variable nozzle is a passage extending radially between two parallel plane circular rings, perpendicular to the axis of rotation of the pump. The approximation or the axial spacing of these rings causes a reduction or a proportional increase in the cross section between the crowns.
- the crown walls facing each other of the upstream and / or downstream nozzles may have a positive, zero or negative overlap. These walls may or may not have a radial overlap. There is radial overlap when the two facing surfaces which constitute the nozzle, have an effective overlap in the radial direction, that is to say are at least partly opposite to the axis of the pump (this means that a displacement along the axis of the rotor pump with respect to the stator could bring these surfaces into contact). Conversely, the absence of recovery corresponds to the situation in which these two surfaces have no vis-à-vis along the axis of the pump; that, although they face each other, that is to say, although their normals are of the same direction but of opposite directions. In all cases (with or without radial overlap), the surfaces of a nozzle are arranged in such a way that their relative axial displacement induces a variation of the passage section of the nozzle, that is to say of the passage section between them.
- the section of the annular chamber in a meridian plane is slightly elongated, i.e., has a larger dimension less than twice its smaller dimension. This arrangement promotes the dissipation of energy by vortex.
- the invention is particularly advantageous in the case of pumps arranged for pumping liquid hydrogen.
- Ia or the impellers can reach a peripheral speed greater than 400 m / s r or even 500 m / s, it is understood that under these conditions, any unwanted contact occurring at the periphery of the wheels between a paddle wheel and the stator can have considerable consequences.
- the shape of the fluid evacuation passage is therefore essential, since it concerns precisely this part of the pump.
- the invention allows the passage creates a significant pressure drop, while having a very small axial and radial dimensions, and without causing additional manufacturing cost unacceptable.
- the fluid discharge passage is substantially sealed, except for the fluid inlet via the upstream nozzle, and fluid discharge via the downstream nozzle.
- the intermediate annular chamber is substantially sealed except for the passage of fluid through the upstream and downstream nozzles, and no fluid exchange path other than the upstream and downstream nozzles is provided.
- the upstream nozzle and the downstream nozzle are radially stages. In other words, the upstream nozzle and the downstream nozzle are located at different distances from one another relative to the axis of rotation of the pump. With this arrangement, it is possible to achieve an axially compact axial balancing device, that is to say of short length along the axis of the pump.
- the annular chamber may in particular be arranged radially between a radius of the upstream nozzle and a radius of the downstream nozzle (a radius of a nozzle here designating the radius of a lesser passage section of the nozzle).
- the nozzles In general, various forms of revolution around the axis of the pump may be adopted for the nozzles, the nozzles necessarily necessarily extending radially, but may for example have a conical or other shape, and the respective facing surfaces wheel and stator to be geometrically matched.
- the expression "facing each other” indicates here that for each of the nozzles, the walls of the wheel and of the stator are substantially opposite one another, the two nozzles being moreover offset one by the other. relative to the other axially and / or radially.
- At least one of the upstream nozzle and the downstream nozzle extends in a plane perpendicular to the axis of the pump.
- the axial thrust balancing device can be arranged only in a single impeller. It can therefore be used when the rotor has only one impeller.
- the thrust balancer may be used in a rotor having a plurality of impellers.
- the only wheel involved is the last wheel behind the pump, that is to say the one located furthest downstream in the direction of advance of the fluid in the pump.
- the axial thrust balancing device involves at least two wheels, and in particular all the wheels.
- the forces are distributed more homogeneously within the rotor.
- the passage further comprises at least one other intermediate nozzle extending between two opposite crown walls, respectively of the rotor and the stator, and at least one other chamber.
- annular intermediate arranged between the rotor and the stator, opening downstream of the intermediate nozzle, or the intermediate nozzle (s) and intermediate annular chamber (s) being interposed alternately on the path of fluid downstream of the first intermediate annular chamber and upstream of the downstream nozzle.
- the invention applies more particularly to the realization of turbopumps for space engine, associating a pump as described previously coupled to a turbine.
- FIG. 1 already described is an axial sectional view of a centrifugal pump equipped with an axial thrust balancing device
- Ia Figure 2 already described is an axial sectional view of a fluid transfer passage of this device, in a known conformation
- FIG. 3 is an axial sectional view of a fluid transfer passage of an axial pump balancing device, in a first embodiment of FIG. embodiment of the invention
- FIG. 4 is a view in axial section of a fluid transfer passage of an axial pump balancing device, in a second embodiment of the invention
- FIG. an axial sectional view of a fluid transfer passage of an axial pump balancing device, in a third embodiment of the invention.
- FIGS. 3 to 5 show axial balancing devices that can be implemented in a pump such as that presented with reference to FIG. 1.
- the operation of an axial pump balancing device, in a first embodiment of the invention, will now be described with reference to FIG.
- Figure 3 is a partial section of a pump generally similar to that shown in Figure 1, namely a single stage pump having an open type wheel 111. However, the device of the pump of FIG. 3 is different from that of the pump of FIG.
- the pump shown in FIG. 3 comprises a rotor 114 and a stator 112, and a thrust balancing device comprising in particular a fluid passage 120 formed between the rotor 114 and the stator 112.
- the thrust device is arranged on the rear wall of the impeller. It will of course be understood that, in general, the thrust device may be arranged both on a rear wall of the wheel 111 and on a front wall thereof.
- the passage 120 Upstream of the side of the fluid stream, the passage 120 comprises an upstream axial portion 130 extending between two substantially cylindrical walls 131,132 of circular section facing each other, respectively of the wheel 111 (wheel involved) and the stator 112, located upstream of the upstream nozzle 140.
- This upstream axial portion constitutes a cavity which advantageously allows a first dissipation of kinetic energy of the fluid passing through the passage 120.
- the upstream nozzle 140 Immediately downstream of the upstream axial portion extends the upstream nozzle 140. This is a passage extending radially over a distance B between the walls 141 and 142 respectively of the wheel and the stator. There is therefore, on the distance B, an effective radial overlap between the surfaces 141 and 142
- the chamber 150 This is of annular shape and extends between the walls 151 and 152 of the wheel 111 and the stator 112.
- the chamber can indifferently be arranged in the volume of the wheel and / or the stator. With the exception of the upstream and downstream nozzles, the chamber 150 is sealed.
- the annular chamber 150 is of short length in the radial direction, since it extends radially on less than one tenth, and more precisely less than one twentieth of the radius of the wheel 111 at the level of the upstream nozzle.
- this intermediate chamber 150 extends the downstream nozzle 160, between the walls 161 and 162 respectively of the wheel and the stator. It is also positive recovery.
- the upstream and downstream radial nozzles respectively define axial sets A1O1 and A1Q2, equal or otherwise, between the wheel 111 and the stator 112.
- the upstream and downstream nozzles are radially raised.
- the upstream nozzle 140 is at a smaller radial distance from the axis of rotation of the pump than the downstream nozzle 160.
- These two nozzles are separated by the distance radially separating the walls 151 and 152 respectively of the rotor and stator, which corresponds to the radial extension of the annular chamber 150.
- the passage 120 comprises a downstream axial portion 170 extending between two substantially cylindrical walls 171,172 of circular section facing each other, respectively of the wheel
- stator 112 located downstream of the downstream nozzle
- this downstream axial part also constitutes a cavity allowing the dissipation of kinetic energy of the fluid passing through the passage 120.
- these axial portions upstream and downstream of the passage 120 may adopt other forms of revolution around the axis of the pump, for example present a convergent (upstream) or a divergent (downstream) between frustoconical surfaces facing respectively the wheel 111 and the stator 112.
- the impeller 211 is a closed wheel, or flanged, that is to say closed by a lid 290 (or flange) on the front side of the blades.
- the axial balancing device is doubled, comprising first axial balancing means (including a first passage 220) very similar to those presented in FIG. FIG. 3 and second counterbalancing axial balancing means arranged on the cover side.
- the various elements of the first axial balancing means, and in particular the passage 220, are substantially the same as in the previous embodiment and will therefore not be described again in detail.
- the upstream and downstream radial nozzles extend substantially in the same plane perpendicular to the axis of rotation of the rotor, whereas on the contrary in the embodiment shown in FIG.
- the upstream radial nozzles 140 and downstream 160 are slightly offset along the axis of rotation of the pump.
- the machining of the surfaces 241, 261 of the wheel and 242, 262, of the stator is simplified.
- the axial size of the axial balancing device is thus not increased, compared to the axial balancing device shown in FIG.
- the intermediate chamber was arranged only in the stator. As this chamber can be subjected to rapid wear and / or vibration, these are advantageously concentrated in the stator and not in the rotating assembly of the pump.
- annular chamber 273 is arranged in the upstream portion of the downstream axial portion 270, in the vicinity of the outlet section of the downstream nozzle 260 of the passage 220. Forcing the fluid to flow also in this annular chamber 273, the pressure drop is further increased when passing through the passage 220.
- a similar cavity may symmetrically be provided in the downstream portion of the upstream axial portion 230, in the vicinity of the inlet section of the upstream nozzle. 240.
- the axial balancing device comprises second axial balancing means for the wheel 211, to prevent movement of the latter forward.
- the axial balancing device thus comprises another balancing chamber 288, called the front balancing chamber, extending between a front wall of the cover 290 and the stator 212, a second passage 292 arranged between the cover and the stator, allowing fluid to be discharged from the fluid channel 214 to the front balancing chamber 288, the second passage 292 comprising an upstream nozzle 294 and a nozzle 296, these nozzles extending between two crown walls facing each other, respectively the lid 290 on the front side and the stator 212 on the rear side, and an intermediate annular chamber 298 arranged between walls respectively of the lid 290 and the stator 212, the intermediate annular chamber 298 s opening downstream of the upstream nozzle 294 and upstream of the downstream nozzle 296 of the second passage 292.
- the front balancing chamber extending between a front wall of the cover 290 and the stator 212
- a second passage 292 arranged between the cover and the stator, allowing fluid to be discharged from the fluid channel 214 to
- the structure of the second balancing means is functionally equivalent to that of the first means, but the second means are arranged in a direction opposite with respect to the pump fee. Due to this conformation of the axial balancing device with counterbalancing means in opposite directions disposed on both sides of the wheel, the axial displacements of the rotor are compensated in both directions. Note finally that according to the invention, the balancing device can be disposed on one or more flasks, each provided with balancing means in both directions.
- the various elements of the axial balancing means, and in particular the passage 320, are substantially the same as in the first embodiment and will therefore not be described again in detail.
- This third embodiment lies in the absence of radial overlap between the surfaces of the upstream and downstream nozzles 360 and 360.
- the nozzles 340 and 360 do indeed have no radial overlap. Indeed, for each of these nozzles, the surfaces of the nozzles 341, 361; 342,362 respectively of the rotor and the stator, do not comprise any portion vis-à-vis along the axis of the pump. More specifically, concerning the upstream nozzle 340, the surfaces 341 and 342 constituting this nozzle are separated by a radial gap C; concerning the downstream nozzle 360, a radial gap D separates the surfaces 361 and 362 constituting this nozzle.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201080004084.6A CN102272457B (zh) | 2009-01-09 | 2010-01-08 | 具有轴向平衡装置的泵 |
RU2011130704/06A RU2539954C2 (ru) | 2009-01-09 | 2010-01-08 | Насос с осевым балансировочным устройством |
EP10706014.7A EP2376789B1 (fr) | 2009-01-09 | 2010-01-08 | Pompe a dispositif d'equilibrage axial. |
JP2011544909A JP5492222B2 (ja) | 2009-01-09 | 2010-01-08 | 軸線方向平衡装置を備えたポンプ |
US13/143,616 US9109606B2 (en) | 2009-01-09 | 2010-01-08 | Pump having an axial balancing device |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR0950107 | 2009-01-09 | ||
FR0950107A FR2941019A1 (fr) | 2009-01-09 | 2009-01-09 | Pompe a dispositif d'equilibrage axial |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2010079309A1 true WO2010079309A1 (fr) | 2010-07-15 |
Family
ID=40845920
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/FR2010/050027 WO2010079309A1 (fr) | 2009-01-09 | 2010-01-08 | Pompe a dispositif d'equilibrage axial. |
Country Status (7)
Country | Link |
---|---|
US (1) | US9109606B2 (fr) |
EP (1) | EP2376789B1 (fr) |
JP (1) | JP5492222B2 (fr) |
CN (1) | CN102272457B (fr) |
FR (1) | FR2941019A1 (fr) |
RU (1) | RU2539954C2 (fr) |
WO (1) | WO2010079309A1 (fr) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2019110909A1 (fr) * | 2017-12-08 | 2019-06-13 | Arianegroup Sas | Pompe comprenant un systeme d'equilibrage axial |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010016563A1 (de) | 2010-04-21 | 2011-10-27 | Miklos Gäbler | Vorrichtung zum Umwandeln von Energie aus einer oszillatorischen Bewegung in elektrische Energie sowie Anordnung |
WO2016160016A1 (fr) * | 2015-04-02 | 2016-10-06 | Schlumberger Canada Limited | Chambres d'équilibrage dans des pompes électriques submersibles |
US10513928B2 (en) * | 2017-08-31 | 2019-12-24 | Flowserve Management Company | Axial thrust balancing device |
CN109973401B (zh) * | 2018-10-24 | 2020-06-26 | 浙江朗庆智能科技有限公司 | 基于离心式的尿素泵 |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR405266A (fr) * | 1908-07-24 | 1909-12-24 | Henri Legros | Dispositif pour équilibrer la poussée axiale dans les pompes centrifuges |
DE922807C (de) * | 1945-03-06 | 1955-01-24 | Aeg | Einrichtung zum Ausgleich des Axialschubes mehrstufiger Kreiselpumpen |
CH330272A (fr) * | 1955-07-19 | 1958-05-31 | Harland Engineering Company Li | Pompe à rotor en porte à faux |
DE1528717A1 (de) * | 1965-06-30 | 1969-10-30 | Halbergerhuette Gmbh | Vorrichtung zum Ausgleich des Axialschubes bei mehrstufigen Kreiselpumpen |
US4867633A (en) * | 1988-02-18 | 1989-09-19 | Sundstrand Corporation | Centrifugal pump with hydraulic thrust balance and tandem axial seals |
DE19631824A1 (de) * | 1996-08-07 | 1998-02-12 | Klein Schanzlin & Becker Ag | Kreiselpumpenlagerung mit Axialschubausgleich |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1020699A (en) * | 1912-03-19 | Gen Electric | Centrifugal pump. | |
US1488931A (en) * | 1921-10-26 | 1924-04-01 | Marechal Paul Joseph Charles | Turbo engine |
JPS56109689U (fr) * | 1980-01-25 | 1981-08-25 | ||
JPS56109689A (en) | 1980-02-02 | 1981-08-31 | Bunsaku Taketomi | Overrlocking sewing machine particularly for sewing machine for both use |
FR2698667B1 (fr) * | 1992-11-30 | 1995-02-17 | Europ Propulsion | Pompe centrifuge à rouet ouvert. |
JP3646740B2 (ja) * | 1995-06-27 | 2005-05-11 | 石川島播磨重工業株式会社 | バランスピストン機構を備えたターボポンプ |
RU2095607C1 (ru) | 1995-07-19 | 1997-11-10 | Ракетно-космическая корпорация "Энергия" им.С.П.Королева | Жидкостный ракетный двигатель на криогенном топливе |
KR100610012B1 (ko) | 2004-08-16 | 2006-08-09 | 삼성전자주식회사 | 터보 펌프 |
US7445213B1 (en) * | 2006-06-14 | 2008-11-04 | Florida Turbine Technologies, Inc. | Stepped labyrinth seal |
-
2009
- 2009-01-09 FR FR0950107A patent/FR2941019A1/fr not_active Withdrawn
-
2010
- 2010-01-08 RU RU2011130704/06A patent/RU2539954C2/ru not_active IP Right Cessation
- 2010-01-08 CN CN201080004084.6A patent/CN102272457B/zh not_active Expired - Fee Related
- 2010-01-08 WO PCT/FR2010/050027 patent/WO2010079309A1/fr active Application Filing
- 2010-01-08 EP EP10706014.7A patent/EP2376789B1/fr active Active
- 2010-01-08 JP JP2011544909A patent/JP5492222B2/ja active Active
- 2010-01-08 US US13/143,616 patent/US9109606B2/en active Active
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR405266A (fr) * | 1908-07-24 | 1909-12-24 | Henri Legros | Dispositif pour équilibrer la poussée axiale dans les pompes centrifuges |
DE922807C (de) * | 1945-03-06 | 1955-01-24 | Aeg | Einrichtung zum Ausgleich des Axialschubes mehrstufiger Kreiselpumpen |
CH330272A (fr) * | 1955-07-19 | 1958-05-31 | Harland Engineering Company Li | Pompe à rotor en porte à faux |
DE1528717A1 (de) * | 1965-06-30 | 1969-10-30 | Halbergerhuette Gmbh | Vorrichtung zum Ausgleich des Axialschubes bei mehrstufigen Kreiselpumpen |
US4867633A (en) * | 1988-02-18 | 1989-09-19 | Sundstrand Corporation | Centrifugal pump with hydraulic thrust balance and tandem axial seals |
DE19631824A1 (de) * | 1996-08-07 | 1998-02-12 | Klein Schanzlin & Becker Ag | Kreiselpumpenlagerung mit Axialschubausgleich |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2019110909A1 (fr) * | 2017-12-08 | 2019-06-13 | Arianegroup Sas | Pompe comprenant un systeme d'equilibrage axial |
FR3074859A1 (fr) * | 2017-12-08 | 2019-06-14 | Arianegroup Sas | Pompe comprenant un systeme d'equilibrage axial |
Also Published As
Publication number | Publication date |
---|---|
CN102272457A (zh) | 2011-12-07 |
EP2376789A1 (fr) | 2011-10-19 |
CN102272457B (zh) | 2015-06-10 |
JP2012514713A (ja) | 2012-06-28 |
RU2539954C2 (ru) | 2015-01-27 |
RU2011130704A (ru) | 2013-02-20 |
US20120148384A1 (en) | 2012-06-14 |
JP5492222B2 (ja) | 2014-05-14 |
EP2376789B1 (fr) | 2018-09-12 |
FR2941019A1 (fr) | 2010-07-16 |
US9109606B2 (en) | 2015-08-18 |
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