EP3721093B1 - Pumpe oder verdichter mit einem axialen ausgleichssystem - Google Patents

Pumpe oder verdichter mit einem axialen ausgleichssystem Download PDF

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Publication number
EP3721093B1
EP3721093B1 EP18836829.4A EP18836829A EP3721093B1 EP 3721093 B1 EP3721093 B1 EP 3721093B1 EP 18836829 A EP18836829 A EP 18836829A EP 3721093 B1 EP3721093 B1 EP 3721093B1
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EP
European Patent Office
Prior art keywords
balancing
pump
expansion
axial
centrifugal wheel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP18836829.4A
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English (en)
French (fr)
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EP3721093A1 (de
Inventor
Cyril LOISEAU
Sébastien BOUFFLERT
Thibaut LEMAIRE
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ArianeGroup SAS
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ArianeGroup SAS
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Publication of EP3721093A1 publication Critical patent/EP3721093A1/de
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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
    • F04D29/041—Axial thrust balancing
    • 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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/051—Axial thrust balancing
    • 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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/051—Axial thrust balancing
    • F04D29/0516—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
    • 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors

Definitions

  • the present invention relates to the field of axial balancing of pumps or compressors, such as for example pumps intended to suck liquefied gas, for aerospace turbomachines.
  • the pumps or compressors of the prior art comprise an axial balancing system making it possible to compensate all or part of the forces exerted on certain parts of the pump, when the latter is in operation.
  • the axial balancing system is generally defined by a restrictive fluid flow passage, formed between the housing and the rotor, for example a centrifugal impeller, of the pump. It is important to precisely calibrate the flow rate of the fluid in the restrictive flow passage in order to optimize axial balance of the pump.
  • US 4867633 discloses a centrifugal pump with hydraulic thrust balancing and tandem axial seals.
  • the main axis is the axis of rotation of the centrifugal wheel.
  • the axial direction corresponds to the direction of the main axis and a radial direction is a direction perpendicular to this main axis and intersecting this main axis.
  • an axial plane is a plane containing the main axis and a radial plane is a plane perpendicular to this main axis.
  • a circumference is understood as a circle belonging to a radial plane and whose center belongs to the main axis.
  • a tangential or circumferential direction is a direction tangent to a circumference; it is perpendicular to the main axis but does not pass through the main axis.
  • interior and exterior are used with reference to a radial direction so that the interior portion of an element is, in a radial direction, closer to the axis of the diffuser than the exterior portion of the same element.
  • the adjectives front and rear are used in reference to the axial direction with the understanding that the inlet of the centrifugal wheel is located on the front side of the centrifugal wheel, while its output is located on the rear side, in the direction normal fluid flow through the centrifugal wheel.
  • the second balancing portion is moved by the centrifugal force exerted on the centrifugal wheel when the latter is driven in rotation.
  • rest position is understood to mean the position occupied by the second balancing portion when the centrifugal wheel is not rotated. In this position, the first and second balancing portions are at a distance from each other.
  • operating position is understood to mean the position occupied by the second balancing portion when the centrifugal wheel is rotated, for example, at its nominal rotational speed.
  • the overall displacement of the second balancing portion can be the result of a radial displacement and an axial displacement, in particular.
  • the aerospace turbomachine is a cryogenic turbomachine, that is to say, configured to compress a fluid, for example, at a temperature less than or equal to 120 K (Kelvin).
  • a cryogenic turbomachine using liquid hydrogen as the fluid the turbomachine is configured to compress the fluid to a temperature less than or equal to 20 K.
  • the turbomachine using liquid oxygen as the fluid the turbomachine is configured to compress the fluid to a temperature less than or equal to 90 K.
  • the turbomachine is configured to compress the fluid to a temperature less than or equal to 110 K.
  • the pump or the compressor includes a shaft configured to drive the centrifugal wheel in rotation about the main axis.
  • the centrifugal impeller includes a mounting portion configured to be mounted to the shaft.
  • the pump or the compressor according to the present invention avoids the presence of an attached nozzle.
  • the first and second balancing portions overlap, that is to say that the first and second balancing portions are located at least in part opposite one of the 'other, over an overlap distance.
  • the overlap distance is the length the pieces overlap.
  • the first and second balancing portions overlap axially.
  • the axial overlap of the first and second balancing portions allows better calibration of the flow rate, also called the leak rate, in the restrictive flow passage. Indeed, as the centrifugal wheel is subjected to expansion when it is rotated in the radial direction, it is difficult to control the radial play.
  • the axial play is easily controlled, and can be calibrated.
  • a fluid passage of which the dimensions are controlled is formed, which makes it possible to calibrate the flow rate in the restrictive flow passage.
  • the axial clearance therefore makes it possible to calibrate the flow rate of the fluid in the restrictive flow passage.
  • the overlap distance of the first and second balancing portions in a radial direction, in the operating position is between 0.012% and 0.032% of the diameter of the centrifugal wheel.
  • the overlap distance of the first and second balancing portions in a radial direction, in the operating position may be between 0.03 mm and 0.08 mm, for example for a diameter of the wheel centrifugal of 250 mm, a speed of rotation of the centrifugal wheel of 40,000 rpm (revolutions per minute) and for a temperature of about 40 K.
  • the first and second balancing portions form a baffle, or a labyrinth making it possible to better restrict the entry of fluid into the restrictive flow passage, and therefore to better ensure the axial balancing of the pump. or compressor.
  • the second balancing portion is configured to move a distance between 0.024% and 0.06% of the diameter of the centrifugal wheel.
  • the second balancing portion is configured to move a distance between 0.06mm and 0.15mm, for example for a centrifugal wheel diameter of 250mm, a centrifugal wheel rotational speed of 40,000 rpm / min and for a temperature of about 40 K.
  • the second balancing portion is configured to be received in a balancing groove formed by the first balancing portion and a portion of the housing adjacent to the first balancing portion.
  • first and second balancing portions are configured to form the entrance to the restrictive flow passage by the cooperation between the second balancing portion and the balancing groove, in the operating position.
  • the first and second balancing portions are remote from one another.
  • the second balancing portion does not fit into the balancing groove.
  • the first and second balancing portions do not overlap axially.
  • the entrance to the restrictive flow passage is, for example, of the general shape of a labyrinth or of a baffle.
  • the centrifugal wheel includes an expansion portion configured to move the second balancing portion from the rest position to the operating position.
  • the mounting portion, the expansion portion and the second balancing portion are arranged in this order in the radial direction, starting from the main axis.
  • the expansion portion of the centrifugal wheel allows movement of the second balancing portion by virtue of the centrifugal force, which further simplifies the mounting of the balancing system while ensuring better axial balancing. pump or compressor.
  • the expansion portion is annular.
  • the expansion portion is configured to undergo greater expansion than other parts of the centrifugal wheel under the effect of centrifugal force.
  • the expansion portion allows the second balancing portion to pass more easily from the rest position to the operating position when the centrifugal wheel is in operation and also to return to the rest position when the centrifugal wheel. stopped working.
  • the expansion portion comprises at least a portion of reduced thickness in the axial direction with respect to adjacent parts of the centrifugal wheel.
  • the thickness of the centrifugal wheel is reduced at the expansion portion, which allows the expansion portion to expand more than the other parts of the centrifugal wheel.
  • the expansion portion includes an expansion member, which may be disposed along the restrictive flow passage.
  • expansion element is adjacent to the restrictive flow passage.
  • the expansion element is disposed on the back of the centrifugal wheel, that is to say on the side of the rear part of the centrifugal wheel.
  • the expansion element comprises a groove.
  • the groove is configured to thin at least part of the expansion portion in the axial direction.
  • the expansion element can comprise several grooves.
  • the expansion element comprises a lattice structure, i.e. a mesh structure or a lattice structure.
  • the lattice structure having anisotropic and / or flexible behavior, it more easily allows the expansion portion of the centrifugal wheel to expand radially under the centrifugal effect to pass the second balancing portion of the rest position to the operating position.
  • the expansion element comprises an anisotropic material.
  • the anisotropic material makes it easier for the expansion portion of the centrifugal wheel to expand radially under the centrifugal effect to cause the second balancing portion to pass from the rest position to the operating position.
  • the anisotropic material is solid.
  • the figure 1 shows a part of a pump 11 of an aerospace turbomachine, configured to allow the flow of a fluid.
  • the pump may comprise one or more axial compression stage (s) and one or more centrifugal compression stage (s).
  • the pump 11 comprises a casing 13 and a centrifugal impeller 15.
  • the housing 13 externally surrounds the blades of the centrifugal wheel 15.
  • the blades of the centrifugal wheel 15 are arranged on the front side of the centrifugal wheel 15.
  • a diffuser 12 is located downstream of the centrifugal wheel 15.
  • the turbomachine has a fluid inlet (not shown), the fluid passing through this inlet to reach the pump 11.
  • the centrifugal wheel and the axial speed of the fluid which passes through the centrifugal wheel 15 is gradually transformed into radial speed, the fluid exiting at the outer periphery of the centrifugal wheel 15.
  • the fluid enters the centrifugal wheel 15, substantially in an axial direction DA , defined by the main axis, and leaves the centrifugal wheel 15 substantially in a radial direction DR, substantially perpendicular to the main axis.
  • the fluid leaving the centrifugal wheel 15 passes through the diffuser 12 before reaching the combustion chamber (not shown).
  • the centrifugal wheel 15 can be mounted on a shaft driven in rotation by the turbine.
  • the centrifugal wheel 15 is therefore configured to be driven in rotation with respect to the casing 13 about the main axis.
  • the pump 11 comprises a main fluid flow passage 17, defined between the housing 13 and the front of the centrifugal impeller 15, and a restrictive fluid flow passage 19 defining an axial balancing system, here arranged between the back of the centrifugal impeller 15, or the back of the centrifugal impeller 15, and the housing 13.
  • the restrictive flow passage 19 is a secondary fluid passage, configured to receive a circulation flow, or a leakage flow. which exerts an axial back pressure on the centrifugal impeller 15 with a view to the axial balancing of the pump 11.
  • the casing 13 comprises a body 21 and a first balancing portion 23.
  • the first balancing portion 23 is integral with the body 21.
  • the centrifugal wheel 15 comprises a mounting portion 25, an expansion portion 27 and a second balancing portion 29, arranged radially in this order.
  • the mounting portion 25 is mounted on the shaft.
  • the mounting portion 25, the expansion portion 27, and the second balancing portion 29 are integral.
  • the first and second balancing portions 23, 29 define the entrance to the restrictive flow passage 19.
  • the first balancing portion 23 includes an inwardly projecting portion and the second balancing portion 29 includes an outwardly projecting portion.
  • the first and second balancing portions 23, 29 are offset with respect to each other in the axial direction DA, and therefore have an axial clearance JA.
  • the axial clearance JA between the first and second balancing portions is between 0.02% and 0.4% of the radius of the centrifugal wheel, preferably between 0.08% and 0.2% of the radius of the centrifugal wheel and more preferably, the axial play JA between the first and second balancing portions 23, 29 is 0.12% of the radius of the centrifugal wheel 15.
  • the axial play JA between the first and second balancing portions 23, 29 is between 30 ⁇ m and 500 ⁇ m, preferably between 100 ⁇ m and 250 ⁇ m.
  • the axial clearance JA between the first and second balancing portions is 150 ⁇ m.
  • the axial play JA in the rest position is dimensioned so as to obtain a satisfactory play in the operating position.
  • the axial clearance JA thus makes it possible to calibrate the flow rate of the fluid in the restrictive flow passage 19.
  • the second balancing portion 29 is disposed opposite a balancing groove 31 formed by the first axial balancing portion 23 and an adjacent portion 32 of the housing 13.
  • the expansion portion 27 is configured to undergo an expansion greater than the mounting portion 25 and the second balancing portion 29 of the centrifugal wheel 15 under the effect of centrifugal force.
  • the expansion portion 27 includes, along the restrictive flow passage 19, an expansion member 35.
  • the expansion member 35 includes a groove 33.
  • the expansion member 35 only comprises the groove 33.
  • the reduced thickness of the centrifugal wheel 15 at this location allows it to expand more strongly at this expansion portion 27.
  • the expansion element 35 is annular.
  • the groove 33 extends over a length of approximately 40% of the diameter of the centrifugal wheel in the radial direction.
  • the groove 33 has a depth of approximately 20% of the thickness of the centrifugal wheel, in the axial direction, considered at mid-height of the centrifugal wheel 15 in the radial direction, that is to say say about 50% of the outer radius of the centrifugal wheel 15.
  • the groove 33 extends over a length of approximately 50 mm in the radial direction. In this example, the groove 33 has a depth of about 5 mm in the axial direction.
  • the centrifugal wheel 15 can be made of a material conventionally used for cryogenic turbomachines.
  • a material has a Young's modulus of 200,000 MPa, a Poisson's ratio of 0.3 and a density of 8.26.10 -6 kg / mm 3 .
  • the centrifugal wheel 15 is made of titanium, aluminum or a nickel-based material, such as a nickel-based superalloy, for example Inconel (registered trademark).
  • the second balancing portion 29 of the centrifugal wheel 15 is configured to pass from a visible rest position in figure 1 , in an operating position, visible in figure 2 .
  • the first and second balancing portions 23, 29 are at a distance from each other and the centrifugal wheel 15 is not rotated.
  • an inner edge 23a of the first balancing portion 23 and an outer edge of the second balancing portion 29 are spaced apart by a radial rest play in a radial direction DR.
  • the radial rest play JRR is between 0.03 mm and 0.08 mm, preferably between 0.04 mm and 0.07 mm, and more preferably, the play is 0.05 mm.
  • the second balancing portion 29 does not fit into the balancing groove 31. Thus, the mounting of the centrifugal wheel 15 on the housing 13 is carried out easily.
  • the centrifugal impeller 15 When the pump is put into operation, the centrifugal impeller 15 starts to rotate and is subjected to the centrifugal force. Under this force, the centrifugal wheel 15 expands outwardly, thanks to the expansion of the expansion portion 27, in particular.
  • the first and second balancing portions 23, 29 overlap in the axial direction DA under the effect of the centrifugal force exerted on the centrifugal wheel 15 when the centrifugal wheel 15 is rotated.
  • the nominal speed of the pump is between 1000 rpm and 120,000 rpm, preferably between 10,000 rpm and 100,000 rpm and more preferably 40,000 rpm.
  • the second balancing portion 29 fits into the balancing groove 31, which forms a labyrinthine passage at the entrance to the restrictive flow passage 19.
  • the calibration of the circulation flow rate is easy.
  • the first and second balancing portions 23, 29 overlap over an overlap distance DC of between 0.03 mm and 0.08 mm, preferably between 0.04 mm and 0.07 mm, and more preferably over a distance 0.05 mm in the radial direction DR.
  • the second balancing portion 23 moves over a displacement distance DD, in the radial direction DR, between 0.06 mm and 0.15 mm, preferably between 0.08 mm and 0.13 mm, more preferably, over a displacement distance DD of 0.1 mm.
  • the figure 4 shows a second embodiment of the expansion portion 27.
  • This second example differs from the first embodiment in that the expansion element 135 comprises a lattice structure 137, that is to say a mesh structure or else reticular.
  • the lattice structure 137 is attached to the centrifugal wheel 15, after having been manufactured by an additive manufacturing process, for example by laser fusion on a powder bed.
  • the lattice structure 137 is arranged in place of the groove 33 of the first embodiment.
  • the expansion element 135 includes only the truss structure 137.
  • the figure 5 shows a third exemplary embodiment of the expansion portion 27.
  • This third exemplary embodiment differs from the first and second exemplary embodiments in that the expansion element 235 comprises an anisotropic material 237.
  • the anisotropic material 237 is solid. .
  • the anisotropic material 237 is arranged in place of the groove 33 of the first embodiment.
  • the expansion element 235 comprises only the anisotropic material 237.
  • the anisotropic material 237 is configured to undergo preferential expansion in the radial direction DR.
  • the anisotropic material 237 is a composite material comprising oriented fibers.
  • the fibers can be generally oriented in the radial direction DR, which makes it possible to give more flexibility to the expansion element 235 in the radial direction DR.
  • the expansion portion 27 is entirely made of the anisotropic material 237.
  • the centrifugal wheel 15 is entirely made of the anisotropic material 237.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (10)

  1. Pumpe (11) oder Kompressor für den Durchfluss eines Fluids, umfassend:
    - ein Gehäuse (13) und
    - ein Zentrifugalrad (15), das dazu ausgelegt ist, gegenüber dem Gehäuse (13) um eine Hauptachse, welche eine axiale Richtung (DA) definiert, drehangetrieben zu werden,
    - einen den Fluiddurchfluss einschränkenden Durchgang, der zwischen dem Gehäuse (13) und dem Zentrifugalrad (15) ausgebildet ist und ein axiales Ausgleichssystem (19) definiert,
    wobei das Gehäuse (13) einen ersten Ausgleichsabschnitt (23) umfasst und das Zentrifugalrad (15) einen zweiten Ausgleichsabschnitt (29) umfasst, wobei der erste und der zweite Ausgleichsabschnitt (23, 29) den Einlass des den Durchfluss einschränkenden Durchgangs definieren,
    dadurch gekennzeichnet, dass der zweite Ausgleichsabschnitt (29) des Zentrifugalrades (15) dazu ausgelegt ist, aus einer Ruheposition, in welcher der Außendurchmesser des zweiten Ausgleichsabschnittes (29) kleiner als der Innendurchmesser des ersten Ausgleichsabschnittes (23) ist, in eine Betriebsposition überzugehen, in welcher sich der erste und der zweite Ausgleichsabschnitt (23, 29) unter der Wirkung der auf das umlaufende Zentrifugalrad (15) ausgeübten Zentrifugalkraft in axialer Richtung (DA) überlappen.
  2. Pumpe oder Kompressor nach Anspruch 1, wobei der zweite Ausgleichsabschnitt (29) dazu ausgelegt ist, sich über eine Bewegungsstrecke (DD) im Bereich zwischen 0,024 % und 0,06 % des Durchmessers des Zentrifugalrades (15) zu bewegen.
  3. Pumpe oder Kompressor nach einem der Ansprüche 1 oder 2, wobei der zweite Ausgleichsabschnitt (29) dazu ausgelegt ist, in einer Ausgleichsnut (31) aufgenommen zu werden, die durch den ersten Ausgleichsabschnitt (23) und einen Teil des Gehäuses (13), welcher zu dem ersten Ausgleichsabschnitt (23) benachbart ist, gebildet ist.
  4. Pumpe oder Kompressor nach einem der vorhergehenden Ansprüche, wobei das Zentrifugalrad (15) einen Ausdehnungsabschnitt (27) umfasst, der dazu ausgelegt ist, den zweiten Ausgleichsabschnitt (29) von der Ruheposition in die Betriebsposition zu überführen.
  5. Pumpe oder Kompressor nach Anspruch 4, wobei der Ausdehnungsabschnitt (27) dazu ausgelegt ist, unter der Wirkung der Zentrifugalkraft eine größere Ausdehnung als die anderen Teile des Zentrifugalrades (15) zu erfahren.
  6. Pumpe oder Kompressor nach einem der Ansprüche 4 oder 5, wobei der Ausdehnungsabschnitt (27) ein Ausdehnungselement (35, 135, 235) umfasst, das entlang des den Durchfluss einschränkenden Durchgangs (19) angeordnet ist.
  7. Pumpe oder Kompressor nach einem der Ansprüche 4 bis 6, wobei der Ausdehnungsabschnitt (27) wenigstens einen Abschnitt mit einer in der axialen Richtung (DA) gegenüber den benachbarten Teilen des Zentrifugalrades (15) verringerten Dicke umfasst.
  8. Pumpe oder Kompressor nach einem der Ansprüche 4 bis 7, wobei das Ausdehnungselement (35) eine Auskehlung (33) umfasst.
  9. Pumpe oder Kompressor nach einem der Ansprüche 4 oder 5, wobei das Ausdehnungselement (135) eine Gitterstruktur (137) umfasst.
  10. Pumpe oder Kompressor nach einem der Ansprüche 4 oder 5, wobei das Ausdehnungselement (235) ein anisotropes Material (237) umfasst.
EP18836829.4A 2017-12-08 2018-12-03 Pumpe oder verdichter mit einem axialen ausgleichssystem Active EP3721093B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR1761863A FR3074859B1 (fr) 2017-12-08 2017-12-08 Pompe comprenant un systeme d'equilibrage axial
PCT/FR2018/053093 WO2019110909A1 (fr) 2017-12-08 2018-12-03 Pompe comprenant un systeme d'equilibrage axial

Publications (2)

Publication Number Publication Date
EP3721093A1 EP3721093A1 (de) 2020-10-14
EP3721093B1 true EP3721093B1 (de) 2021-08-25

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EP18836829.4A Active EP3721093B1 (de) 2017-12-08 2018-12-03 Pumpe oder verdichter mit einem axialen ausgleichssystem

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EP (1) EP3721093B1 (de)
FR (1) FR3074859B1 (de)
WO (1) WO2019110909A1 (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4148283A1 (de) * 2021-09-10 2023-03-15 Hamilton Sundstrand Corporation Turbomaschinenrotor mit variablen gitterdichten
US11773746B2 (en) 2021-09-10 2023-10-03 Hamilton Sundstrand Corporation Turbomachinery rotor shroud with variable lattice densities
US11802488B2 (en) 2021-09-10 2023-10-31 Hamilton Sundstrand Corporation Turbomachinery seal plate with variable lattice densities
US11994141B2 (en) 2021-09-10 2024-05-28 Hamilton Sundstrand Corporation Turbomachinery shaft with variable lattice densities

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH330272A (fr) * 1955-07-19 1958-05-31 Harland Engineering Company Li Pompe à rotor en porte à faux
SU1071805A1 (ru) * 1982-10-01 1984-02-07 Предприятие П/Я М-5841 Центробежный насос
US4867633A (en) * 1988-02-18 1989-09-19 Sundstrand Corporation Centrifugal pump with hydraulic thrust balance and tandem axial seals
FR2941019A1 (fr) * 2009-01-09 2010-07-16 Snecma Pompe a dispositif d'equilibrage axial

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4148283A1 (de) * 2021-09-10 2023-03-15 Hamilton Sundstrand Corporation Turbomaschinenrotor mit variablen gitterdichten
US11773746B2 (en) 2021-09-10 2023-10-03 Hamilton Sundstrand Corporation Turbomachinery rotor shroud with variable lattice densities
US11802488B2 (en) 2021-09-10 2023-10-31 Hamilton Sundstrand Corporation Turbomachinery seal plate with variable lattice densities
US11994141B2 (en) 2021-09-10 2024-05-28 Hamilton Sundstrand Corporation Turbomachinery shaft with variable lattice densities

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Publication number Publication date
EP3721093A1 (de) 2020-10-14
FR3074859B1 (fr) 2019-12-27
FR3074859A1 (fr) 2019-06-14
WO2019110909A1 (fr) 2019-06-13

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