EP2784327B1 - Compresseur centrifuge - Google Patents

Compresseur centrifuge Download PDF

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Publication number
EP2784327B1
EP2784327B1 EP13174085.4A EP13174085A EP2784327B1 EP 2784327 B1 EP2784327 B1 EP 2784327B1 EP 13174085 A EP13174085 A EP 13174085A EP 2784327 B1 EP2784327 B1 EP 2784327B1
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EP
European Patent Office
Prior art keywords
sealing
protrusion
sealing protrusion
centrifugal compressor
blades
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
EP13174085.4A
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German (de)
English (en)
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EP2784327A2 (fr
EP2784327A3 (fr
Inventor
Kyung Kook Kim
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Doosan Heavy Industries and Construction Co Ltd
Original Assignee
Doosan Heavy Industries and Construction Co Ltd
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Publication of EP2784327A2 publication Critical patent/EP2784327A2/fr
Publication of EP2784327A3 publication Critical patent/EP2784327A3/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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • 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
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F04D29/162—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of a centrifugal flow wheel
    • 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
    • F04D29/08—Sealings
    • 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

Definitions

  • aspects of the present inventive concept relate to a centrifugal compressor, and more particularly, to a centrifugal compressor capable of minimizing leakage of a fluid in the process of compressing the fluid and having high aerodynamic performance.
  • a centrifugal compressor signifies a device for compressing a fluid by converting kinetic energy into pressure energy through a centrifugal force by sucking the fluid in a rotational axis direction of a high-speed rotor or an impeller and circumferentially exhausting the fluid.
  • the centrifugal compressor has been extensively applied to various industrial fields such as various types of air conditioning facilities and gas turbine systems.
  • a general centrifugal compressor includes an impeller 10 having a rotary hub 11 connected to a driving shaft 40 and a plurality of blades 12 radially provided about a rotational axis X-X' of the rotary hub 11.
  • the centrifugal compressor includes a housing 20 formed with an inlet into which a fluid to be compressed is introduced and an outlet through which the compressed fluid is discharged and provided with an inner surface 21 fixedly adjacent to the blades 12 and a diffuser 30 that reduces a dynamic pressure component of a voltage component increased due to force received from the impeller 10 and increases a static pressure component thereof.
  • An impeller used for the general centrifugal compressor constructed as described above is classified into an open impeller and a shroud impeller according to the capacity and performance thereof.
  • an impeller where outer ends of the blades 12 are open may be called an open impeller 10 or an unshrouded impeller having no shrouds.
  • the shroud impeller 10 includes a shroud 13 that connects outer ends of a plurality of blades 12 provided in the rotary hub 11 to each other while surrounding the outer ends of the blades 12.
  • a closed fluid path for a fluid to be compressed is formed by adjacent blades 12 and the shroud 13 so that flow loss may be reduced as compared with that of the open impeller, thereby representing higher compression efficiency.
  • shroud 13 serves as a reinforcing structure connecting the blades 12 to each other so that the shroud impeller 10 has strength higher than that of the open impeller.
  • the shroud impeller has a very complicated three-dimensional structure and thus processing is not easy and a manufacturing cost is considerably increased.
  • FIG. 2B shows a method of mechanically processing a monolithic rotor having a disc shape by a cutting tool 50 controlled using a numerical control tool, which is disclosed in U.S. Patent US 7,305,762 B2 .
  • the above patent may not be compatible with a complicated inner fluid path due to the structural problem, and there is a limitation in processing due to a shape of the cutting tool and the manufacturing cost is increased.
  • FIG. 2B shows a method of manufacturing an impeller by bonding an upstream impeller member and a downstream impeller member to each other after the upstream impeller member and the downstream impeller member are separately processed, which is disclosed in Japanese unexamined patent publication JP 2010-121612 A .
  • Korean patent registration KR 10-0745507 B1 discloses a technology for providing a partial shroud at an outlet of an impeller.
  • a centrifugal compressor according to the preamble of claim 1 is known from JP 2003 293993 A .
  • JP 2009 156122 A discloses a centrifugal compressor having a shrouded impeller.
  • a slit is provided through the shroud along a circumferential direction thereof in order to provide a flow path for fluid to be returned to the inlet of the impeller in a space between the shroud and an impeller housing.
  • JP S61 171899 A discloses an impeller having a non-shrouded region in the vicinity of the fluid inlet in the region where the impeller blades are formed almost in parallel to the axial rotation direction. However, in the region in which the profile of the impeller blades starts to be curved towards the fluid outlet, the blades are provided with a shroud. With this configuration, it is intended to prevent dust or foreign materials from adhering to the device.
  • US 6 039 535 A , JP H11 280 694 A and WO 2010/033192 A1 are examples of fully shrouded impellers. Further, it is known from those documents to provide a seal between an outer side of a full shroud and an inner side of a corresponding impeller housing.
  • Exemplary embodiment have been made in an effort to solve the above-described problems, and an aspect of the present inventive concept provides a centrifugal compressor capable of minimizing leakage of a fluid in the process of compressing the fluid and having high aerodynamic performance by providing a sealing unit between an impeller and an inner surface of a housing.
  • a centrifugal compressor having higher strength as compared with an open impeller and superior workability as compared with a shroud impeller.
  • a centrifugal compressor including an impeller including a plurality of blades radially disposed about a rotational axis; a housing formed with an inlet into which a fluid to be compressed by the impeller is introduced and an outlet through which a compressed fluid is discharged and having an inner surface adjacent to the blades; a first sealing unit disposed adjacent to the inlet and configured to seal between outer ends of the blades and the inner surface, the first sealing unit comprising a partial shroud disposed adjacent to the inlet to partially surround outer peripheral portions of the outer ends of the blades.
  • the first sealing unit is configured to allow a flow of the fluid that has passed through the inlet of the housing to be introduced toward the blades of the impeller and prevent the fluid introduced into the blades from flowing back to the inlet through the gap formed between the blades and the inner surface.
  • the compressor comprises a second sealing unit disposed adjacent to the outlet and sealing a gap between the outer ends of the plurality of blades and the innder surface.
  • the second sealing unit includes a second partial shroud disposed adjacent to the outlet to partially surround the outer peripheral portions of the outer ends of the blades.
  • the first sealing unit may include at least one first sealing protrusion protruding toward the inner surface from the first partial shroud, a rear end of the first sealing protrusion is fixed to the first partial shroud, and a front end of the first sealing protrusion is spaced apart from the inner surface by a predetermined interval.
  • the first sealing protrusion may be integrally formed with the first partial shroud.
  • the centrifugal compressor may further include a first sealing pad on the inner surface adjacent to the first sealing protrusion, wherein the first sealing pad may include a material having hardness lower than hardness of the first sealing protrusion.
  • the first sealing pad may be formed with a first sealing groove having a shape corresponding to a shape of the first sealing protrusion, and a front end of the first sealing protrusion is inserted into the first sealing groove.
  • the first sealing unit may include a second sealing protrusion protruding toward the first partial shroud from the inner surface, a rear end of the second sealing protrusion is fixed to the inner surface, and a front end of the second sealing protrusion is spaced apart from the first partial shroud by a predetermined interval.
  • the second sealing protrusion may be integrally formed with the housing.
  • the first sealing unit may further include a first support member having one surface attached to the inner surface and an opposite surface formed with the second sealing protrusion.
  • the second sealing protrusion may be integrally formed with the first support member.
  • the centrifugal compressor may further include a second sealing pad on an outer surface of the first partial shroud adjacent to the second sealing protrusion, wherein the second sealing pad may include a material having hardness lower than hardness of the second sealing protrusion.
  • the second sealing pad may be formed with a second sealing groove having a shape corresponding to a shape of the second sealing protrusion, and a front end of the second sealing protrusion is inserted into the second sealing groove.
  • the second sealing unit may further include a third sealing protrusion protruding toward the inner surface from the second partial shroud, a rear end of the third sealing protrusion is fixed to the second partial shroud, and a front end of the third sealing protrusion is spaced apart from the inner surface by a predetermined interval.
  • the third sealing protrusion may be integrally formed with the second partial shroud.
  • the centrifugal compressor may further include a third sealing pad on the inner surface adjacent to the third sealing protrusion, wherein the third sealing pad may include a material having hardness lower than hardness of the third sealing protrusion.
  • the third sealing pad may be formed with a third sealing groove having a shape corresponding to a shape of the third sealing protrusion, and a front end of the third sealing protrusion is inserted into the third sealing groove.
  • the second sealing unit may further include a fourth sealing protrusion protruding toward the second partial shroud from the inner surface, a rear end of the fourth sealing protrusion is fixed to the inner surface, and a front end of the fourth sealing protrusion is spaced apart from the second partial shroud by a predetermined interval.
  • the fourth sealing protrusion may be integrally formed with the housing.
  • the second sealing unit may further include a second support member having one surface attached to the inner surface and an opposite surface formed with the fourth sealing protrusion.
  • the fourth sealing protrusion may be integrally formed with the second support member.
  • the centrifugal compressor may further include a fourth sealing pad on an outer surface of the second partial shroud adjacent to the fourth sealing protrusion, wherein the fourth sealing pad may include a material having hardness lower than hardness of the fourth sealing protrusion.
  • the fourth sealing pad may be formed with a fourth sealing groove having a shape corresponding to a shape of the fourth sealing protrusion, and a front end of the fourth sealing protrusion is inserted into the fourth sealing groove.
  • a sealing unit includes the first sealing unit disposed adjacent to the inlet and the second sealing unit disposed adjacent to the outlet, the first sealing unit includes the first partial shroud disposed adjacent to the inlet to partially surround the outer peripheral portions of the outer ends of the blades, and the second sealing unit includes the second partial shroud disposed adjacent to the outlet to partially surround the outer peripheral portions of the outer ends of the blades.
  • the first sealing unit is configured to allow a flow of the fluid that has passed through the inlet of the housing to be introduced toward the blades of the impeller and prevent the fluid introduced into the blades from flowing back to the inlet through the gap formed between the blades and the inner surface.
  • the first sealing unit may include a first sealing protrusion protruding toward the inner surface from the first partial shroud, and the second sealing unit may include a third sealing protrusion protruding toward the inner surface from the second partial shroud.
  • a rear end of the first sealing protrusion may be fixed to the first partial shroud, a front end of the first sealing protrusion may be spaced apart from the inner surface by a predetermined interval, a rear end of the third sealing protrusion may be fixed to the second partial shroud, and a front end of the third sealing protrusion may be spaced apart from the inner surface by a predetermined interval.
  • the first sealing unit may include a second sealing protrusion protruding toward the first partial shroud from the inner surface
  • the second sealing unit may include a fourth sealing protrusion protruding toward the second partial shroud from the inner surface.
  • a rear end of the second sealing protrusion may be fixed to the inner surface, a front end of the first sealing protrusion may be spaced apart from the first partial shroud by a predetermined interval, a rear end of the fourth sealing protrusion may be fixed to the inner surface, and a front end of the fourth sealing protrusion may be spaced apart from the second partial shroud by a predetermined interval.
  • the centrifugal compressor according to the present inventive concept includes the sealing unit to seal the gap formed between the impeller and the inner surface of the housing, so the leakage of fluid to be compressed can be prevented at the fluid inlet and the fluid outlet, thereby maximizing the compression efficiency.
  • the partial shrouds are provided at portions of the impeller adjacent to the fluid inlet and the fluid outlet, so the centrifugal compressor may have higher strength suitable for high-speed rotation as compared with the open impeller and may have superior workability as compared with the shroud impeller.
  • the centrifugal compressor according to the present inventive concept may have the precise profile tolerance and can be manufactured at a lower cost while ensuring the structural stability.
  • FIG. 3 is an axial cross-sectional view showing a centrifugal compressor according to a first example and FIGS. 4 and 5 are partially enlarged views of the centrifugal compressor shown in FIG. 3 .
  • the centrifugal compressor includes an impeller 100 and a housing 200.
  • the impeller 100 includes a rotary hub 110 rotating about a rotational axis X-X' by receiving power from a driving shaft (not shown) and a plurality of blades 120 radially provided on the rotary hub 110 about the rotational axis X-X'.
  • the housing 200 receives the impeller 100 therein and is formed with an inner surface 211 adjacent to the blades 120.
  • the rotary hub 110 is connected to the driving shaft (not shown) and receives rotating force from the driving shaft.
  • the rotary hub 110 may be made from a material having predetermined strength suitable for high speed.
  • the rotary hub 110 may be fabricated by heat-treating chromium-molybdenum steel, nickel chromium-molybdenum steel, or stainless steel.
  • the rotary hub 110 may have a conical shape having a sectional area gradually reduced in the direction of the rotational axis X-X'.
  • a front center portion of the conical shape in the direction of the rotational axis X-X' becomes an inlet 220 of a fluid
  • a rear peripheral portion of the conical shape in the radial direction becomes an outlet of the fluid.
  • an inclined surface of a peripheral side in the conical shape of the rotary hub is illustrated as a curve surface having a predetermined curvature in FIG. 3 , the present inventive concept is not limited thereto.
  • the blades 120 are radially disposed on the inclined surface of the rotary hub 110 while being spaced apart from each other by a predetermined interval.
  • the blades 120 may have a three-dimensional curved shape by taking specifications of a compressor, such as application purpose, compression capacity and flow velocity, into consideration.
  • the blades 120 may be integrally formed with the rotary hub 110. It is also possible to bond the blade to the rotary hub 110 through a welding scheme after processing the blade by using a material the same as that of the rotary hub 110.
  • the welding scheme may not provide sufficient strength required for the high-speed impeller 100.
  • the strength of the impeller 100 according to the present inventive concept can be reinforced by a first partial shroud 310 or a second partial, the impeller 100 may have the condition applicable for the high-rotation compressor.
  • the housing 200 has an internal space for receiving the impeller 100 and is configured to serve as a stator to rotatably support the impeller 100.
  • the housing 200 includes a cover member 210, which forms the inlet 220 of a fluid to be compressed and the outlet 230 of the compressed fluid and has an inner surface 211 adjacent to the blades 120.
  • the centrifugal compressor according to the first example includes a first sealing unit 300 disposed adjacent to the inlet 220 to seal a gap formed between outer ends of the blades 120 and the inner surface 211.
  • the centrifugal compressor according to the first example includes the first sealing unit 300 to prevent the leakage of fluid to be compressed at the inlet 220.
  • the first sealing unit 300 is a non-contact type sealing unit, for instance, a labyrinth sealing unit.
  • a labyrinth sealing unit In order to implement the labyrinth sealing unit, there is provided a first partial shroud 310 having an annular shape and disposed adjacent to the inlet to partially surround the outer ends of the blades 120 and at least one first sealing protrusion 320a protruding toward the inner surface 211 from the first partial shroud 310.
  • the first partial shroud 310 has a cylindrical shape configured to partially surround outer ends of the blades 120 adjacent to the inlet 220.
  • the first partial shroud 310 may be integrally formed with the blades 120 or may be fabricated separately from the blades 120 and bonded to the outer ends of the blades 120 through a welding scheme.
  • the first partial shroud 310 partially surrounds the outer ends of the blades 120 adjacent to the inlet 220, the fluid introduced into the inlet 220 can be prevented from being leaked through a gap between the blades 120 and the inner surface 211 of the housing 200.
  • the centrifugal compressor may have higher strength as compared with the open impeller 100 and may have the simple structure.
  • the first sealing unit 320a seals a gap formed between the first partial shroud 310 and the inner surface 211 through the labyrinth sealing scheme. That is, the first sealing unit 320a may allow a flow f1 of the fluid that has passed through the inlet 220 of the housing 200 to be introduced toward the blades 120 of the impeller 100 and prevent the fluid introduced into the blades 120 from flowing back to the inlet 220 through the gap formed between the blades 120 and the inner surface 211, so that the compression efficiency can be improved approximate to the compression efficiency of the shroud impeller.
  • the sealing protrusion 320a has a rear end 320a-1 fixed to the first partial shroud 310 and a front end 320a-2 protruding toward the inner surface 211 so that a predetermined gap is formed between the front end 320a-2 and the inner surface 211 (see, C in FIG. 4 ).
  • the first sealing protrusion 320a may be separately fabricated as an individual member and the rear end 320a-1 of the first sealing protrusion 320a may be bonded to the first partial shroud 310 through the welding scheme, or the first sealing protrusion 320a may be integrally formed with the first partial shroud 310.
  • the first partial shroud 310 may serve as a support member for the first sealing protrusion 320a.
  • the first sealing protrusion 320a prevents the fluid from flowing rearward or forward in the axial direction and it is preferable to provide a plurality of first sealing protrusions 320a as shown in FIG. 3 .
  • the number of the first sealing protrusion is not limited, but may be variously adjusted by taking specifications of a compressor, such as application purpose, compression capacity and flow velocity, into consideration.
  • the first sealing protrusion 320a may serve as a rotator and the inner surface 211 of the housing 200 may serve as a stator in labyrinth sealing.
  • the centrifugal compressor according to the first example may further include a first sealing pad 330a having an annular shape.
  • the first sealing pad 330a has hardness lower than the first sealing protrusion 320a and is provided on the inner surface 211 in opposition to the first sealing protrusion 320a.
  • the first sealing protrusion 320a serves as the rotator and the inner surface 211 of the housing 200 serves as the stator so that vibration may occurs in the direction perpendicular to the rotating axis due to the rotation of the impeller 100 when the centrifugal compressor is operated.
  • the first sealing protrusion 320a serving as the rotator may interfere with the inner surface 211 serving as the stator, and thus the inner surface 211 may be worn or the first sealing protrusion 320a may be deformed.
  • the gap for maintaining the labyrinth sealing may be excessively enlarged, thereby deteriorating the sealing performance.
  • the example provides the first sealing pad 330a to prevent the wear or deformation.
  • the first sealing pad 330a is formed on the inner surface 211 of the housing 200 corresponding to the first sealing protrusion 320a by using a material having low plastic deformation and predetermined elasticity, such as a resin, a coating, a honeycomb or a light-weight material.
  • the first sealing pad 330a may be fabricated by using a material having hardness lower than that of the first sealing protrusion 320a.
  • the predetermined gap C can be ensured between the front end 320a-2 of the first sealing protrusion 320a and the first sealing pad 330a so that the high sealing performance can be achieved.
  • the sealing pad 330a of the centrifugal compressor according to the first example is formed with a first sealing groove 340 having a shape corresponding to a shape of the first sealing protrusion 320a and the front end 320a-2 of the first sealing protrusion 320a may be fitted into the first sealing groove 340.
  • a diameter of the impeller 110 rotating at a high speed during the operation of the centrifugal compressor may be enlarged due to centrifugal force and heat and the first sealing protrusion 320a may penetrate into the first sealing pad 330a.
  • the first sealing pad 330a may be made from a material having hardness lower than that of the first sealing protrusion 320a.
  • the sealing protrusion and sealing pad according to other embodiments of the present inventive concept also may have the above feature.
  • the first sealing groove 340 into which the front end 320a-2 of the first sealing protrusion 320a is partially inserted, is formed in the first sealing pad 330a, a sealing area between the front end 320a-2 of the first sealing protrusion 320a and the first sealing pad 330a can be increased, so that the sealing efficiency can be improved.
  • the wear and deformation caused by the vibration of the impeller 100 can be diminished and the higher sealing performance can be ensured.
  • FIG. 6 is an axial cross-sectional view showing a centrifugal compressor according to a second example
  • FIGS. 7 to 9 are partially enlarged views of the centrifugal compressor shown in FIG. 6 .
  • the description about the elements and structures that have been described in the first example will be omitted in order to avoid redundancy.
  • the centrifugal compressor according to the second example includes at least one second sealing protrusion 320b protruding toward the first partial shroud 310 from the inner surface 211 of the housing 200.
  • the second sealing protrusion 320b includes a rear end 320b-1 fixed to the inner surface 211 and a front end 320b-2 spaced apart from the first partial shroud 310 by a predetermined distance C.
  • the sealing protrusion constituting the first sealing unit 300 protrudes toward the first partial shroud 310 from the inner surface 211 of the housing 200.
  • the second sealing protrusion 320b may be integrally formed with the housing 200.
  • the second sealing protrusion 320b may be attached to an inner surface of a first support member 350 having an annular shape and inserted into the inner surface 211 of the housing 200.
  • the second sealing protrusion 320b may be separately prepared as an individual member such that the rear end 320b-1 of the second sealing protrusion 320b can be attached to the inner surface of the first support member 350 through a welding scheme or the second sealing protrusion 320b may be integrally formed with the inner surface of the first support member 350.
  • the manufacturing cost for the first partial shroud 310 and the impeller 100 which are relatively expensive and complicate in shapes, can be reduced.
  • the second sealing protrusion 320b serves as a stator and the first partial shroud 310 may serve as a rotator.
  • a second sealing pad 330b can be formed on an outer surface of the first partial shroud 310 to prevent the sealing protrusion from being worn and deformed.
  • the second sealing pad 330b is also formed by using a material having low plastic deformation and predetermined elasticity as well as hardness lower than that of the second sealing protrusion 320b.
  • the second sealing pad 330b is formed with a second sealing groove 340 having a shape corresponding to a shape of the second sealing protrusion 320b as shown in FIG. 9 .
  • the front end 320b-2 of the second sealing protrusion 320b may be inserted into the second sealing groove 340.
  • FIG. 10 is an axial cross-sectional view showing a centrifugal compressor according to a third example and FIGS. 11 and 12 are partially enlarged views of the centrifugal compressor shown in FIG. 10 .
  • the description about the elements and structures that have been described in the first and second examples will be omitted in order to avoid redundancy.
  • the centrifugal compressor according to the third example includes a second sealing unit 400 adjacent to the outlet 230 of the housing 200.
  • the centrifugal compressor according to the third example includes the second sealing unit 400 to prevent the leakage of the fluid flow f2 at the outlet 230 of the compressed fluid.
  • the second sealing unit 400 includes a second partial shroud 410 having an annular shape and disposed adjacent to the outlet 230 to partially surround the outer ends of the blades 120 and at least one third sealing protrusion 420a protruding toward the inner surface 211 from the second partial shroud 410.
  • a rear end 420a-1 of the third sealing protrusion 420a is fixed to the second partial shroud 410 and a front end 420a-2 of the third sealing protrusion 420a is spaced apart from the inner surface 211 by a predetermined distance (see C of FIG. 11 ) such that the third sealing protrusion 420a serves as a rotator and the inner surface 211 of the housing 200 serves as a stator, thereby implementing the labyrinth sealing.
  • the second partial shroud 410 has a hollow disc shape corresponding to a shape of the blades 120 adjacent to the outlet 230 of the fluid.
  • the second partial shroud 410 partially surrounds the outer ends of the blades 120 to serve as a support member for the third sealing protrusion 420a.
  • the outer ends of the blades adjacent to the outlet 230 of the fluid can be securely fixed by the second partial shroud 410, thereby implementing a high-strength structure.
  • the second partial shroud 410 may be integrally formed with the blades 120 or may be separately prepared and attached to the outer ends of the blades 120 through a welding scheme.
  • the third sealing protrusion 420a may be prepared as an individual member.
  • the rear end 420a-1 of the third sealing protrusion 420a may be attached to the second partial shroud 410 through a welding scheme or may be integrally formed with the first partial shroud.
  • the centrifugal compressor according to the third example may further include a third sealing pad 430a provided at the inner surface 211 in opposition to the third sealing protrusion 420a and having an annular shape .
  • the third sealing pad 420a may have hardness lower than that of the third sealing protrusion 420a and may be formed by using a material having low plastic deformation and predetermined elasticity.
  • the third sealing pad 430a is formed with a third sealing groove 440 having a shape corresponding to a shape of the third sealing protrusion 420a.
  • the front end 420a-2 of the third sealing protrusion 420a may be inserted into the third sealing groove 440.
  • FIG. 13 is an axial cross-sectional view showing a centrifugal compressor according to a fourth example
  • FIGS. 14 to 16 are partially enlarged views of a centrifugal compressor shown in FIG. 13 .
  • the description about the elements and structures that have been described in the first to third examples will be omitted in order to avoid redundancy.
  • the centrifugal compressor according to the fourth example includes a second sealing unit 400 having at least one fourth sealing protrusion 420b protruding toward the second partial shroud 410 from the inner surface 211 of the housing.
  • the fourth sealing protrusion 420b includes a rear end 420b-1 fixed to the inner surface 211 and a front end 420b-2 spaced part from the second partial shroud 410 by a predetermined distance C.
  • the sealing protrusion constituting the second sealing unit 400 protrudes toward the second partial shroud 410 from the inner surface 211 of the housing 200.
  • the fourth sealing protrusion 420b may be integrally formed with the housing 200 as shown in FIG. 13 .
  • the fourth sealing protrusion 420b may be attached to an inner surface of a second support member 450 having an annular shape and inserted into the inner surface 211 of the housing 200.
  • the fourth sealing protrusion 420b may be separately prepared as an individual member.
  • the rear end 420b-1 of the fourth sealing protrusion 420b may be attached to the inner surface of the second support member 450 through a welding scheme or may be integrally formed with the inner surface of the second support member 450.
  • a fourth sealing pad 430b may be provided to prevent the wear and deformation of the sealing protrusion.
  • the fourth sealing pad 430b may be formed on the outer surface of the second partial shroud 410.
  • the fourth sealing pad 430b may be formed by using a material having low plastic deformation and predetermined elasticity as well as hardness lower than that of the second sealing protrusion.
  • the fourth sealing pad 430b is formed with a fourth sealing groove 440 having a shape corresponding to a shape of the fourth sealing protrusion 420b.
  • the front end 420b-2 of the fourth sealing protrusion 420b may be inserted into the fourth sealing groove 440.
  • FIG. 17 is an axial cross-sectional view showing a centrifugal compressor according to a first exemplary embodiment of the present invention.
  • the centrifugal compressor according to the first exemplary embodiment includes a first sealing unit 300 adjacent to the inlet 220 of the housing 200 and a second sealing unit 400 adjacent to the outlet 230 of the housing 200.
  • the centrifugal compressor according to the first embodiment of the present invention includes the first sealing unit 300 according to the first example and the second sealing unit 400 according to the third example.
  • the centrifugal compressor according to the first exemplary embodiment includes the first sealing unit 300 having a first partial shroud 310 and a first sealing protrusion 320a and the second sealing unit 400 having a second partial shroud 410 and a third sealing protrusion 420a.
  • the fluid leakage can be effectively prevented at the inlet 220 and the outlet 230 of the housing 200, so that the efficiency of the impeller 100 can be upgraded to the level of the typical shroud impeller.
  • the blades 120 adjacent to the inlet 220 of the housing 200 can be reinforced by the first partial shroud 310 and the blades adjacent to the outlet 230 of the housing 200 can be reinforced by the second partial shroud 410 so that the strength of the impeller 100 can be improved to the level of the typical shroud impeller.
  • the technical features of the first sealing pad and the first sealing groove according to the first example and the technical features of the third sealing pad and the third sealing groove according to the third example can be adopted in the first exemplary embodiment illustrated in FIG. 17 .
  • FIG. 18 is an axial cross-sectional view showing the centrifugal compressor according to a second exemplary embodiment of the present invention.
  • the centrifugal compressor includes a first sealing unit 300 adjacent to the inlet 220 of the housing 200 and a second sealing unit 400 adjacent to the outlet 230 of the housing 200.
  • the first sealing unit 300 includes at least one second sealing protrusion 320b protruding toward the first partial shroud 310 from the inner surface 211 of the housing 200 and the second sealing unit 400 includes at least one fourth sealing protrusion 420b protruding toward the second partial shroud 410 from the inner surface 211 of the housing 200
  • the centrifugal compressor according to the second exemplary embodiment includes the first sealing unit 300 according to the second example and the second sealing unit 400 according to the fourth example.
  • the centrifugal compressor according to the second exemplary embodiment includes the first sealing unit 300 having the first partial shroud 310 and the second sealing protrusion 320b and the second sealing unit 400 having the second partial shroud 410 and the fourth sealing protrusion 420b.
  • the technical features of the second sealing pad and the second sealing groove according to the second example and the technical features of the fourth sealing pad and the fourth sealing groove according to the fourth example can be adopted in the second embodiment illustrated in FIG. 18 .
  • first sealing unit 300 according to the first example and the second sealing unit 400 according to the fourth example and the technical features of the first sealing unit 300 according to the second example and the second sealing unit 400 according to the third example can be adopted in the second exemplary embodiment without departing from the scope of the present invention.

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

Claims (15)

  1. Compresseur centrifuge comprenant:
    une hélice (100) comprenant une pluralité de pales (120) disposées radialement autour d'un axe de rotation (X-X');
    un logement (200) comprenant une entrée (220) dans laquelle un fluide à comprimer par l'hélice (100) est introduit, une sortie (230) à travers laquelle le fluide comprimé est évacué, et une surface interne (211) adjacente à la pluralité de pales (120);
    une première unité d'étanchéité (300) disposée adjacente à l'entrée (220) et scellant un espace entre les extrémités externes de la pluralité de pales (120) et la surface interne (211), la première unité d'étanchéité (300) étant configurée pour permettre un flux (f1) du fluide qui a traversé l'entrée (220) du logement (200) pour être introduit vers les pales (120) de l'hélice (100) et empêcher le fluide introduit dans les pales (120) de refouler vers l'entrée (220) à travers l'espace formé entre les pales (120) et la surface interne (211), la première unité d'étanchéité(300) comprenant une première enveloppe partielle (310) disposée adjacente à l'entrée (220) pour entourer partiellement les parties périphériques externes des extrémités externes de la pluralité de pales (120),
    caractérisé par
    une deuxième unité d'étanchéité (400) disposée adjacente à la sortie (230) et scellant un espace entre les extrémités externes de la pluralité de pales (120) et la surface interne (211), la deuxième unité d'étanchéité (400) comprenant une deuxième enveloppe partielle (410) disposée adjacente à la sortie (230) pour entourer partiellement les parties périphériques externes des extrémités externes de la pluralité de pales (120).
  2. Compresseur centrifuge selon la revendication 1, dans lequel la première unité d'étanchéité (300) comprend au moins une première saillie d'étanchéité (320a) faisant saillie vers la surface interne (211) à partir de la première enveloppe partielle (310), une extrémité arrière (320a-1) de la première saillie d'étanchéité (320a) est fixée à la première enveloppe partielle (310) et une extrémité avant (320a-2) de la première saillie d'étanchéité (320a) est espacée de la surface interne (211) d'un intervalle prédéterminé.
  3. Compresseur centrifuge selon la revendication 2, comprenant en outre un premier tampon d'étanchéité (330a) sur la surface interne (211) adjacent à la première saillie d'étanchéité (320a), dans laquelle le premier tampon d'étanchéité (330a) comprend un matériau ayant une dureté inférieure à une dureté de la première saillie d'étanchéité (320a).
  4. Compresseur centrifuge selon la revendication 3, dans lequel le premier tampon d'étanchéité (330a) comprend une première rainure d'étanchéité (340) comprenant une forme correspondant à une forme de la première saillie d'étanchéité (320a), et une extrémité avant (320a-2) de la première saillie d'étanchéité (320a) est insérée dans la première rainure d'étanchéité (340).
  5. Compresseur centrifuge selon la revendication 1, dans lequel la première unité d'étanchéité (300) comprend une seconde saillie d'étanchéité (320b) faisant saillie vers la première enveloppe partielle (310) à partir de la surface interne (211), une extrémité arrière (320b-1) de la deuxième saillie d'étanchéité (320b) est fixée à la surface interne (211), et une extrémité avant (320b-2) de la seconde saillie d'étanchéité (320b) est espacée de la première enveloppe partielle (310) d'un intervalle prédéterminé.
  6. Compresseur centrifuge selon la revendication 5, dans lequel la première unité d'étanchéité (300) comprend en outre un premier élément support (350) comprenant une surface fixée à la surface interne (211) et une surface opposée formée avec la deuxième saillie d'étanchéité (320b).
  7. Compresseur centrifuge selon la revendication 5, comprenant en outre un deuxième tampon d'étanchéité (330b) sur une surface externe de la première enveloppe partielle (310) adjacente à la deuxième saillie d'étanchéité (320b), dans lequel le deuxième tampon d'étanchéité (330b) comprend un matériau ayant une dureté inférieure à la dureté de la deuxième saillie d'étanchéité (320b).
  8. Compresseur centrifuge selon la revendication 7, dans lequel le deuxième tampon d'étanchéité (330b) comprend une deuxième rainure d'étanchéité (340) comprenant une forme correspondant à une forme d'une deuxième saillie d'étanchéité (320b) et une extrémité avant (320b-2) de la deuxième saillie d'étanchéité (320b) est insérée dans la deuxième rainure d'étanchéité (340).
  9. Compresseur centrifuge selon l'une quelconque des revendications précédentes, dans lequel la deuxième l'unité d'étanchéité (400) comprend en outre une troisième saillie d'étanchéité (420a) faisant saillie vers la surface interne (211) de la deuxième enveloppe partielle (410), une extrémité arrière (420a-1) de la troisième saillie d'étanchéité (420a) est fixée à la deuxième enveloppe partielle (410), et une extrémité avant (420a-2) de la troisième saillie d'étanchéité (420a) est espacée de la surface interne (211) par un intervalle prédéterminé.
  10. Compresseur centrifuge selon la revendication 9, comprenant en outre un troisième tampon d'étanchéité (430a) sur la surface interne (211) adjacente à la troisième saillie d'étanchéité (420a), dans laquelle le troisième tampon d'étanchéité (430a) comprend un matériau ayant une dureté inférieure à une dureté de la troisième saillie d'étanchéité (420a).
  11. Compresseur centrifuge selon la revendication 10, dans lequel le troisième tampon d'étanchéité (430a) comprend une troisième rainure d'étanchéité (440) comprenant une forme correspondant à une forme de la troisième saillie d'étanchéité (420a) et une extrémité avant (420a-2) de la troisième saillie d'étanchéité (420a) est insérée dans la troisième rainure d'étanchéité (440).
  12. Compresseur centrifuge selon l'une quelconque des revendications 1 à 8, dans lequel la deuxième l'unité d'étanchéité (400) comprend en outre une quatrième saillie d'étanchéité (420b) faisant saillie vers la deuxième enveloppe partielle (410) de la surface interne (211), une extrémité arrière (420b-1) de la quatrième saillie d'étanchéité (420b) est fixée à la surface interne (211), et une extrémité avant (420b-2) de la quatrième saillie d'étanchéité (420b) est espacée de la deuxième enveloppe partielle (410) d'un intervalle prédéterminé.
  13. Compresseur centrifuge selon la revendication 12, dans lequel la deuxième unité d'étanchéité (400) comprend en outre un deuxième élément support (450) comprenant une surface fixée sur la surface interne (211) et une surface opposée formée avec la quatrième saillie d'étanchéité (420b).
  14. Compresseur centrifuge selon la revendication 12, comprenant en outre un quatrième tampon d'étanchéité (430b) sur une surface externe de la deuxième enveloppe partielle (410) adjacente à la quatrième saillie d'étanchéité (420b), dans laquelle le quatrième tampon d'étanchéité (430b) comprend un matériau ayant une dureté inférieure à une dureté de la quatrième saillie d'étanchéité (420b).
  15. Compresseur centrifuge selon la revendication 14, dans lequel le quatrième tampon d'étanchéité (430b) est formé avec une quatrième rainure d'étanchéité (440) comprenant une forme correspondant à une forme de la quatrième saillie d'étanchéité (420b), et une extrémité avant (420b-2) de la quatrième saillie d'étanchéité (420b) est insérée dans la quatrième rainure d'étanchéité (440).
EP13174085.4A 2013-03-25 2013-06-27 Compresseur centrifuge Active EP2784327B1 (fr)

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EP2784327A2 (fr) 2014-10-01
US20180202451A1 (en) 2018-07-19
KR20140116628A (ko) 2014-10-06
US20140286761A1 (en) 2014-09-25
EP2784327A3 (fr) 2015-04-22
KR101501477B1 (ko) 2015-03-12

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