EP2679827B1 - Turbomachine - Google Patents

Turbomachine Download PDF

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Publication number
EP2679827B1
EP2679827B1 EP12749591.9A EP12749591A EP2679827B1 EP 2679827 B1 EP2679827 B1 EP 2679827B1 EP 12749591 A EP12749591 A EP 12749591A EP 2679827 B1 EP2679827 B1 EP 2679827B1
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EP
European Patent Office
Prior art keywords
impeller
shaft
way screw
turbomachine
rotation axis
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
EP12749591.9A
Other languages
German (de)
English (en)
Other versions
EP2679827A4 (fr
EP2679827A1 (fr
Inventor
Nozomu Asano
Shusaku Yamasaki
Toshimichi Taketomi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
IHI Rotating Machinery Engineering Co Ltd
Original Assignee
IHI Rotating Machinery Engineering Co Ltd
Priority date (The priority date 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 date listed.)
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Publication date
Application filed by IHI Rotating Machinery Engineering Co Ltd filed Critical IHI Rotating Machinery Engineering Co Ltd
Publication of EP2679827A1 publication Critical patent/EP2679827A1/fr
Publication of EP2679827A4 publication Critical patent/EP2679827A4/fr
Application granted granted Critical
Publication of EP2679827B1 publication Critical patent/EP2679827B1/fr
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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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/266—Rotors specially for elastic fluids mounting compressor rotors on shafts
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/025—Fixing blade carrying members on shafts
    • 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
    • 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
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/624—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for elastic fluid pumps

Definitions

  • the present invention relates to turbomachinery.
  • a turbomachine such as a turbocompressor or a supercharger is provided with an impeller that is rotatively driven by rotative power that is transmitted from a shaft.
  • a male screw and a female screw are formed on an impeller and a shaft as shown in Patent Document 1 and Patent Document 2.
  • the impeller and the shaft are then fastened by screwing together of the male screw and the female screw.
  • the present invention was achieved in view of the above circumstances, and has as its object to, in a turbomachinery that is provided with an impeller and a shaft that are to be fastened, eliminating the need for complicated and large equipment and reducing the amount of work during fastening when fastening the impeller to the shaft.
  • the invention is in the turbomachine of claim 1.
  • the impeller and the shaft are fastened by the two-way screw, in which the turning direction of the screw thread that is formed on the impeller side and the turning direction of the screw thread that is formed on the shaft side are opposite directions.
  • the impeller and the shaft by rotating the two-way screw, it is possible to cause the impeller and the shaft to move in a straight line along the rotation axis direction without the impeller undergoing rotative movement with respect to the shaft. That is to say, according to the present invention, compared to the case of fastening the impeller and the shaft while rotatively moving the impeller with respect to the shaft, it is possible to reduce the amount of movement of the impeller, and it is possible to cut down the amount of work during fastening.
  • the impeller when the impeller is pushed to the shaft side and made to undergo elastic deformation in order to ensure the frictional force with the shaft, it is possible to cause the impeller and the shaft to move in a straight line along the rotation axis direction without the impeller undergoing rotative movement with respect to the shaft. That is to say, according to the present invention, compared to the case of fastening the impeller and the shaft while rotatively moving the impeller with respect to the shaft, it is possible to reduce the friction resistance and possible to cut down the amount of work during fastening.
  • turbocompressor as one example of the turbomachinery of the present invention, but the turbomachinery of the present invention is not limited to a turbocompressor, and it can also be applied to general turbomachinerys provided with an impeller and a shaft such as a supercharger.
  • FIG. 1 is a cross-sectional view that shows the outline constitution of a turbocompressor S1 of the present embodiment.
  • the turbocompressor S1 is a machinery that compresses a gas such as air and emits it as compressed gas, and as shown in FIG. 1 , is provided with a compressor 1, a shaft 2, a two-way screw 3, and a drive unit 4.
  • the compressor is a member for compressing gas by being driven, and is equipped with a compressor impeller 1a (equivalent to the impeller of the present invention), and the compressor housing 1b.
  • the compressor impeller 1a is a member for imparting kinetic energy to gas to accelerate it, and is a radial impeller that accelerates gas that is taken in from a rotation axis L direction, and discharges it in a radial direction.
  • the compressor impeller 1a is provided with a base portion 1c that is fastened to the shaft 2, and a plurality of wings 1d that are arranged at equal intervals in the rotation direction on the surface of the base portion 1c.
  • a fitting hole 1e that is opened facing the drive unit 4 and in which a fitting projection 2a that the shaft 2 is provided with is fitted.
  • a housing space of the two-way screw 3 is provided in communication with the fitting hole 1e.
  • a screw thread is formed in the inner wall surface of this housing space and constituted so as to be a female thread that a first end side of the two-way screw 3 can be screwed together with.
  • an exposure hole If that exposes a first end face of the two-way screw 3 is formed from a distal end of the compressor impeller 1a.
  • the exposure hole If has a diameter that allows the passing through of a tool 10 that rotates the two-way screw 3 described later (refer to FIG. 2 ), and is provided along the rotation axis L of the compressor impeller 1a.
  • the fitting hole 1e and the exposure hole If sandwich the housing space of the two-way screw 3, and are arranged so as to be concentric with the rotation axis L of the compressor impeller 1a.
  • the compressor impeller 1a is formed for example with a titanium alloy, an aluminum alloy, or stainless steel, depending on the gas to be compressed.
  • the compressor housing 1b forms the outer shape of the compressor 1, has a gas flow passage in the interior, and houses the compressor impeller 1a in the interior.
  • an intake opening 1g that intakes gas
  • a diffuser 1h that decelerates and compresses the gas that has been accelerated by the compressor impeller 1a
  • a scroll flow passage 1i that serves as the flow passage of the compressed gas
  • a discharge opening that is not illustrated from which the compressed gas is discharged.
  • the shaft 2 is a member for transmitting power generated by the drive unit 4 as rotative power to the compressor impeller 1a, and is connected with the drive unit 4.
  • a fitting projection 2a is provided for fitting in the fitting hole le provided in the base portion 1c of the compressor impeller 1a, and by the fitting projection 2a being fitted in the fitting hole 1e, the compressor impeller 1a and the shaft 2 are positioned so as to be coaxial.
  • a female screw that a second end side of the two-way screw 3 is capable of screwing together with is provided in the fitting projection 2a.
  • the shaft 2 is formed for example with a steel material (for example, a steel material including chrome and molybdenum).
  • a steel material for example, a steel material including chrome and molybdenum.
  • the two-way screw 3 is a member for fastening the compressor impeller 1a and the shaft 2.
  • the first end side of this two-way screw 3 serves as an impeller screwing region 3a that is screwed together with the compressor impeller 1a, while the second end side serves as a shaft screwing region 3b that is screwed together with the shaft 2.
  • the turning direction of the screw thread that is formed on the impeller screwing region 3a and the turning direction of the screw thread that is formed on the impeller screwing region 3b are opposite directions.
  • the turning direction of the screw thread that is formed on the impeller screwing region 3a is set to a direction in which the fastening power between the two-way screw 3 and the compressor impeller 1a increases due to a reactive force when the compressor impeller 1a is rotatively driven.
  • a fitting hole 3c for fitting a tool 10 for rotating the two-way screw 3 is provided in the first end face of the two-way screw 3 (a face on the compressor impeller 1a side).
  • the shape of this fitting hole 3a is set to a shape, viewed from the rotation axis L direction, whose center of gravity is on the rotation axis L (for example, a hexagonal shape).
  • the shape of the fitting hole 3c have a shape whose center of gravity is on the rotation axis L, when the compressor impeller 1a is rotated, it is possible to keep the weight distribution of the compressor impeller 1a that is centered on the rotation axis L uniform, and it is possible to rotate the compressor impeller 1a in a stable manner.
  • the first end face of the two-way screw 3 is exposed by the exposure hole If that is provided in the base portion 1c of the compressor impeller 1a as described above. For this reason, the fitting hole 3c that is formed in the first end face of the two-way screw 3 is exposed from a first end of the compressor impeller 1a via the exposure hole If.
  • the two-way screw 3 is formed with a material having a higher thermal conductivity than the compressor impeller 1a.
  • the compressor impeller 1a being formed with a titanium alloy
  • the two-way screw 3 it is conceivable for the two-way screw 3 to be formed with a steel material.
  • the two-way screw 3 by forming the two-way screw 3 with a material having a higher thermal conductivity than the compressor impeller 1a, it is possible to promote heat transfer from the compressor impeller 1a, which has risen in temperature due to the compression of gas, to the shaft 2, and it is possible to promptly transfer the heat to lubricating oil that is to be cooled by a cooling mechanism not shown.
  • the thermal expansion of the two-way screw 3 becomes greater than the compressor impeller 1a.
  • the compressor impeller 1a and the shaft 2 separating when the fastening portion becomes a high temperature
  • the two-way screw 3 and the compressor impeller 1a are screwed together, and the two-way screw 3 and the shaft 2 are screwed together. For this reason, the contact surface between the two-way screw 3 and the compressor impeller and the contact surface area between the two-way screw 3 and the shaft 2 broaden, the heat transmission area increases, and it is possible to further promote the aforementioned heat transfer.
  • the drive unit 4 is a member for generating power for rotatively driving the compressor impeller 1a and transmitting it to the shaft 2, and for example, is constituted to include a motor and gears and the like.
  • the impeller screwing region 3a of the two-way screw 3 is slightly screwed together with the female screw that is provided in the compressor impeller 1a
  • the shaft screwing region 3b is slightly screwed together with the female screw that is provided in the shaft 2.
  • the shaft screwing region 3b is slightly screwed together with the female screw that is provided in the shaft 2
  • the impeller screwing region 3a is slightly screwed together with the female screw that is provided in the compressor impeller 1a.
  • the tool 10 (hex wrench) is inserted in the exposure hole 1f that is provided in the base portion 1c of the compressor impeller 1a, and a distal end of the tool 10 is fitted in the fitting hole 3c that is exposed from the first end of the compressor impeller 1a via the exposure hole If. Then, by rotating the tool 10, the two-way screw 3 is rotated.
  • the compressor impeller 1a moves in a straight line along the rotation axis L without undergoing rotative movement with respect to the shaft 2.
  • the compressor impeller 1a and the shaft 2 are fastened.
  • the compressor impeller 1a and the shaft 2 are fastened by the two-way screw 3, in which the turning direction of the screw thread that is formed on the compressor impeller 1a side and the turning direction of the screw thread that is formed on the shaft 2 side are opposite directions.
  • turbocompressor S1 of the present embodiment since it is possible to fasten the compressor impeller 1a and the shaft 2 without applying great tension to the two-way screw 3, there is no need for an additional complicated and large equipment such as a hydraulic tensioner.
  • turbocompressor S1 of the present embodiment it is possible to cut down the work amount when fastening the compressor impeller 1a to the shaft 2 without additionally requiring a complicated and large device.
  • the turning direction of the screw thread that is formed on the impeller screwing region 3a is set to a direction in which the fastening power between the two-way screw 3 and the compressor impeller 1a increases due to a reactive force when the compressor impeller 1a is rotatively driven.
  • turbocompressor S1 of the present embodiment it is possible to inhibit loosening of the fastening power between the compressor impeller 1a and the two-way screw 3 during operation.
  • the fitting hole 3c that is capable of fitting the tool 10 that rotates the two-way screw 3 is provided in the end face of the two-way screw 3 on the compressor impeller 1a side, and the exposure hole If that exposes the fitting hole 3c is provided in the compressor impeller 1a.
  • turbocompressor S1 of the present embodiment in order to fasten the compressor impeller 1a and the shaft 2 by the two-way screw 3, there is no need to extend the shaft 2 until the distal end of the compressor impeller 1a in the manner of a conventional turbocompressor in order to fix the compressor impeller 1a. As a result, the shaft 2 becomes short, and so it is possible to improve the rigidity of the shaft 2.
  • FIG. 3A and FIG. 3B are drawings that show the outline constitution of the turbocompressor S2 of the present embodiment.
  • FIG. 3A is a cross-sectional view
  • FIG. 3B is a view on arrow of the shaft 2 seen from the rotation axis L direction.
  • the turbocompressor S2 of the present embodiment is, with the rotation axis L direction serving as the lengthwise direction, equipped with a fitting hole that is provided at a position offset from the rotation axis L of the compressor impeller 1a, and a pin member 5 to be fitted in the fitting hole that is provided at a position offset from the rotation axis L of the shaft 2.
  • the pin member 5 is a member for inhibiting rotational movement of the compressor impeller 1a with respect to the shaft 2, and functions as a rotation inhibiting member of the present invention.
  • a plurality of the pin members 5 are arranged at equally spaced intervals centered on the rotation axis L of the compressor impeller 1a.
  • turbocompressor S2 of the present embodiment having this kind of constitution, when attaching the compressor impeller 1a to the shaft 2 by the pin members 5, it is possible to inhibit rotational movement of the compressor impeller 1a, and it is possible to fasten the compressor impeller 1a and the shaft 2 in a stable manner.
  • the pin members 5 function as reinforcing members at the joining location of the compressor impeller 1a and the shaft 2. For this reason, it is possible to increase the strength of the joining location of the compressor impeller 1a and the shaft 2.
  • the turbocompressor S2 of the present embodiment realizes an improvement in strength at the joining location of the compressor impeller 1a and the shaft 2 that cannot be realized in a turbocompressor that uses the conventional fastening method of rotatively moving the compressor impeller 1a with respect to the shaft 2.
  • a plurality of the pin members 5 are provided at equally spaced intervals centered on the rotation axis L of the compressor impeller 1a.
  • FIG. 4A and FIG. 4B are drawings that show the outline constitution of the turbocompressor S3 of the present embodiment.
  • FIG. 4A is a cross-sectional view
  • FIG. 4B is a view on arrow of the shaft 2 seen from the direction of the rotation axis L.
  • the turbocompressor S3 of the present embodiment is equipped with a fitting projection 7 of which the shape seen from the rotation axis L direction of the compressor impeller 1a is an approximately triangular shape having rounded apices (a shape deviating from the rotation body shape) whose center of gravity is on the rotation axis L, and a fitting hole 6 that the fitting projection 7 is fitted into.
  • this kind of fitting projection 7 and fitting hole 6 function as a rotation inhibiting member of the present invention, by inhibiting rotational movement of the compressor impeller 1a with respect to the shaft 2.
  • the fitting projection 7 is provided at the shaft 2, while the fitting hole 6 is provided in the compressor impeller 1a.
  • turbocompressor S3 of the present embodiment having this kind of constitution, when attaching the compressor impeller 1a to the shaft 2 by the fitting projection 7 and the fitting hole 6, it is possible to inhibit rotational movement of the compressor impeller 1a, and so it is possible to fasten the compressor impeller 1a and the shaft 2 in a stable manner.
  • the fitting projection 7 has a shape whose center of gravity is on the rotation axis L.
  • FIG. 5 is a cross-sectional view that shows the outline constitution of the turbocompressor S4 of the present embodiment.
  • the turbocompressor S4 of the present embodiment is provided with a lock bolt 8 that abuts the two-way screw 3 from the rotation axis L direction of the compressor impeller 1a (left side of the page). Note that the turning direction of the screw thread that is formed on the impeller screwing region 3a of the two-way screw 3 and the turning direction of the screw thread that the lock bolt 8 is provided with are the same directions.
  • a tool hole (for example with a hexagonal shape) that penetrates in the rotation axis L direction and that is used when fastening or loosening the lock bolt 8.
  • the inscribed circle of this tool hole is set to be larger than the circumscribed circle of the tool 10 that fits in the fitting hole 3c of the two-way screw 3. For this reason, the tool 10 can fit in the two-way screw 3 by passing through the lock bolt 8.
  • turbocompressor S4 of the present embodiment having this constitution, even in the case of the compressor impeller 1a attempting to undergo rotational movement in the direction of loosening of the fastening power, it is possible to inhibit displacement of the two-way screw 3 in the rotation axis L direction by the lock bolt 8. As a result, it is possible to prevent rotational movement of the compressor impeller 1a in the direction of loosening of the fastening power.
  • the amount of movement of the compressor impeller 1a and the amount of movement of the shaft 2 per unit rotation of the two-way screw 3 change.
  • the rotation amount of the two-way screw 3 with respect to the unit movement amount of the compressor impeller 1a and the shaft 2 differs.
  • the fitting projection 2a is provided at the shaft 2, and the fitting hole 1e is provided in the compressor impeller 1a.
  • the two-way screw 3 is arranged greatly recessed in the interior of the shaft 2. For that reason, it is possible to allow the two-way screw 3 to escape from the root region of the maximum diameter portion in the compressor impeller 1a where the load becomes great due to the highest stress acting, and so it is possible to reduce the load that acts on the two-way screw 3.
  • an axial force that can mitigate loosening of the axial force due to thermal expansion may be applied to the two-way screw 3.
  • the present invention is not limited thereto, and it is also possible to adopt a constitution in which the two-way screw 3, instead of the fitting hole 3c, is equipped with a fitting projection that a tool is capable of fitting.
  • the present invention is not limited thereto, and it can also be applied to a turbocompressor in which a compressor impeller 1a is fastened to both ends of one shaft, a turbocompressor that is provided with a plurality of shafts and in which a compressor impeller is provided at each shaft, and a turbocompressor that is provided with other equipment such as a cooler or the like that cools the compressed gas.
  • S1 ⁇ S4 turbocompressor turbomachinery
  • 1 Compressor 1a compressor impeller (impeller), 1b compressor housing, 1c base portion, 1d wing, 1e fitting hole
  • If exposure hole 1g intake opening, 1h diffuser, 1i scroll flow passage, 2 shaft, 2a fitting projection, 3 two-way screw, 3a impeller screwing region, 3b shaft screwing region, 3c fitting hole, 4 drive unit, 5 pin member (rotation inhibiting member), 7 fitting projection (rotation inhibiting member), 6 fitting hole (rotation inhibiting means), 8 lock bolt.

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

Claims (11)

  1. Turbomachine (S1, S2, S3, S43), comprenant une roue (1a) pouvant être entraînée en rotation, et un arbre (2) configuré pour transmettre une puissance de rotation à la roue (1a) ;
    dans laquelle la turbomachine (S1, S2, S3, S4) comprend un vis à deux voies (3) dont un premier côté d'extrémité sert de région de vissage de la roue (3a), vissée ensemble avec la roue (1a), et dont un deuxième côté d'extrémité sert de région de vissage de l'arbre (3b) vissé ensemble avec l'arbre (2), la direction de rotation du filet de vis formé au niveau de la région de vissage de la roue (3a) et la direction de rotation du filet de vis formé au niveau de la région de vissage du filet de vis formé au niveau de la région de vissage de l'arbre (3b) étant réalisées dans des directions opposées ; et
    la roue (1a) et l'arbre (2) sont fixés par la vis à deux voies (3) ;
    caractérisée en ce que la vis à deux voies (3) est formée à partir d'un matériau présentant une conductivité thermique supérieure à celle de la roue (1a).
  2. Turbomachine (S1, S2, S3, S4) selon la revendication 1,
    dans laquelle la vis à deux voies (3) est formée à partir d'un matériau d'acier dans le cas où la roue (1a) est formée à partir d'un alliage de titane.
  3. Turbomachine (S2, S3) selon la revendication 1, comprenant en outre un élément d'empêchement de la rotation (5, 6, 7) empêchant le déplacement rotatif de la roue (1a) par rapport à l'arbre (2).
  4. Turbomachine (S2) selon la revendication 3, dans laquelle l'élément empêchant la rotation (5, 6, 7), la direction de l'axe de rotation (L) de la roue (1a) servant de direction longitudinale, est un trou d'ajustement pourvu au niveau d'une position décalée de l'axe de rotation (L) de la roue (1a) et un élément de goupille (5) ajusté dans le trou d'ajustement pourvu au niveau d'une position décalée de l'axe de rotation (L) de l'arbre (2).
  5. Turbomachine (S2) selon la revendication 4, dans laquelle l'élément de goupille (5) est agencé dans plusieurs intervalles à espacement égal centrés sur l'axe de rotation (L) de la roue (1a).
  6. Turbomachine (S3) selon la revendication 3, dans laquelle l'élément empêchant une rotation (5, 6, 7) comprend :
    une saillie d'ajustement (7) dont la forme externe, vue à partir de la direction de l'axe de rotation (L) de la roue (1a) est déviée de la forme du corps de rotation, et fait saillie dans la direction de l'axe de rotation (L) par rapport à la roue (1a) ou à l'arbre (2) ; et
    un trou d'ajustement (6) pourvu dans la roue (1a) ou l'arbre (2), là où la saillie d'ajustement (7) n'est pas pourvue, et dans lequel la saillie d'ajustement (7) est ajustée.
  7. Turbomachine (S3) selon la revendication 6, dans laquelle la saillie d'ajustement (7) a une forme dont le centre de gravité se situe sur l'axe de rotation (L).
  8. Turbomachine (S4) selon la revendication 1, comprenant en outre un boulon de verrouillage (8) butant contre la vis à deux voies (3) à partir de la direction de l'axe de rotation (L) de la roue (1a).
  9. Turbomachine (S1, S2, S3, S4) selon l'une quelconque des revendications 1 à 8, dans laquelle la direction de rotation du filet de vis formé sur la région de vissage de la roue (3a) est ajustée à une direction dans laquelle la puissance de fixation entre la vis à deux voies (3) et la roue (1a) est accrue par suite d'une force de réaction lorsque la roue (1a) est entraînée en rotation.
  10. Turbomachine (S1, S2, S3, S4) selon l'une quelconque des revendications 1 à 9, dans laquelle un trou d'ajustement (3c) ou une saillie d'ajustement pouvant ajuster un outil (10) faisant tourner la vis à deux voies (3), est pourvu(e) sur la face d'extrémité du côté de la roue de la vis à deux voies (3), un trou d'exposition (1f) exposant le trou d'ajustement (3c) ou la saillie d'ajustement étant pourvu dans la roue (1a).
  11. Turbomachine (S1 S2, S3, S4) selon la revendication 10, dans laquelle le trou d'ajustement (3c) ou la saillie d'ajustement pouvant ajuster un outil (10) faisant tourner la vis à deux voies (3), a une forme dont le centre de gravité se situe sur l'axe de rotation (L) de la roue (1a).
EP12749591.9A 2011-02-21 2012-02-21 Turbomachine Active EP2679827B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011034519A JP5589889B2 (ja) 2011-02-21 2011-02-21 ターボ機械
PCT/JP2012/054077 WO2012115086A1 (fr) 2011-02-21 2012-02-21 Turbomachine

Publications (3)

Publication Number Publication Date
EP2679827A1 EP2679827A1 (fr) 2014-01-01
EP2679827A4 EP2679827A4 (fr) 2016-03-09
EP2679827B1 true EP2679827B1 (fr) 2019-09-04

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Application Number Title Priority Date Filing Date
EP12749591.9A Active EP2679827B1 (fr) 2011-02-21 2012-02-21 Turbomachine

Country Status (6)

Country Link
US (1) US20130330193A1 (fr)
EP (1) EP2679827B1 (fr)
JP (1) JP5589889B2 (fr)
KR (1) KR101501761B1 (fr)
CN (1) CN103370544A (fr)
WO (1) WO2012115086A1 (fr)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB201221429D0 (en) * 2012-11-28 2013-01-09 Napier Turbochargers Ltd Impeller shaft
GB201314270D0 (en) 2013-08-09 2013-09-25 Aeristech Ltd Aerodynamic enhancements in compressors
DE102013015563A1 (de) * 2013-09-20 2015-03-26 Abb Turbo Systems Ag Abgasturbolader
KR101825509B1 (ko) * 2014-03-26 2018-02-05 가부시키가이샤 아이에이치아이 임펠러 체결 구조 및 터보 압축기
CN104019057B (zh) * 2014-05-26 2016-08-24 河南众力空分设备有限公司 一种悬臂式叶轮与传动轴的传动连接装置
WO2016188524A1 (fr) * 2015-05-27 2016-12-01 Schaeffler Technologies AG & Co. KG Rotor pour turbocompresseur à gaz d'échappement et turbocompresseur à gaz d'échappement
JP2018114565A (ja) * 2017-01-16 2018-07-26 三菱マテリアル株式会社 切削工具
CA3054660C (fr) 2017-02-27 2022-05-03 Third Pole, Inc. Systemes et methodes pour la generation ambulatoire d'oxyde nitrique
CN111801500A (zh) * 2018-02-20 2020-10-20 松下知识产权经营株式会社 轮毂、旋转风扇、电动风机、电动吸尘器以及干手器
CN109372582A (zh) * 2018-12-16 2019-02-22 阜宁隆德机械制造有限责任公司 一种外置传动叶轮
US11585348B2 (en) * 2019-03-14 2023-02-21 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Compressor wheel device and supercharger
US11739763B2 (en) * 2021-11-11 2023-08-29 Progress Rail Locomotive Inc. Impeller attach mechanism

Family Cites Families (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2010525A (en) * 1934-02-26 1935-08-06 Ingersoll Rand Co Locking device for pump impellers
US2602683A (en) * 1945-03-03 1952-07-08 Sulzer Ag Rotor for turbomachines
US3813038A (en) * 1971-09-13 1974-05-28 H Pryor Railroad tie
JPS5588016U (fr) * 1978-12-12 1980-06-18
JPS5711298U (fr) * 1980-06-25 1982-01-20
JPS6139498U (ja) * 1984-08-17 1986-03-12 株式会社クボタ ポンプ羽根車とポンプ軸との取付け構造
JPH0552356U (ja) 1991-12-17 1993-07-13 株式会社安川電機 ターボ機械のインペラ取付装置
JPH0557450U (ja) 1992-01-07 1993-07-30 株式会社安川電機 ターボ機械のインペラ取付装置
JP3523717B2 (ja) * 1995-05-19 2004-04-26 株式会社 神崎高級工機製作所 漁網用結束機
EP0903465B1 (fr) * 1997-09-19 2003-09-03 ABB Turbo Systems AG Connexion entre roue de compresseur et arbre pour turbomachines à haute vitesse
US6290467B1 (en) * 1999-12-03 2001-09-18 American Standard International Inc. Centrifugal impeller assembly
CN2508043Y (zh) * 2001-08-24 2002-08-28 石季尧 双向螺纹反向自锁自攻螺钉
JP2003181755A (ja) * 2001-12-14 2003-07-02 Hitachi Plant Eng & Constr Co Ltd 配管磨き装置
JP4364516B2 (ja) * 2003-01-16 2009-11-18 株式会社鶴見製作所 ポンプ用羽根車におけるボス部の固定機構
US6986644B2 (en) * 2003-05-02 2006-01-17 Envirotech Pumpsystems, Inc. Hard material impeller and methods and apparatus for construction
US7052241B2 (en) * 2003-08-12 2006-05-30 Borgwarner Inc. Metal injection molded turbine rotor and metal shaft connection attachment thereto
CN2797725Y (zh) * 2005-05-11 2006-07-19 欣业企业股份有限公司 家俱用固定件
JP4876867B2 (ja) * 2006-11-27 2012-02-15 株式会社Ｉｈｉ ターボ圧縮機のロータ
CN201148992Y (zh) * 2007-12-28 2008-11-12 上海东方泵业(集团)有限公司 叶轮的轴向调节结构
JP5880706B2 (ja) * 2012-06-11 2016-03-09 株式会社Ihi ターボ機械

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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Publication number Publication date
WO2012115086A1 (fr) 2012-08-30
EP2679827A4 (fr) 2016-03-09
JP5589889B2 (ja) 2014-09-17
EP2679827A1 (fr) 2014-01-01
KR101501761B1 (ko) 2015-03-11
KR20130129276A (ko) 2013-11-27
JP2012172576A (ja) 2012-09-10
CN103370544A (zh) 2013-10-23
US20130330193A1 (en) 2013-12-12

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