EP3012461A1 - Zentrifugalverdichter - Google Patents

Zentrifugalverdichter Download PDF

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Publication number
EP3012461A1
EP3012461A1 EP13887157.9A EP13887157A EP3012461A1 EP 3012461 A1 EP3012461 A1 EP 3012461A1 EP 13887157 A EP13887157 A EP 13887157A EP 3012461 A1 EP3012461 A1 EP 3012461A1
Authority
EP
European Patent Office
Prior art keywords
flow path
path width
diffuser section
side wall
fluid
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.)
Withdrawn
Application number
EP13887157.9A
Other languages
English (en)
French (fr)
Other versions
EP3012461A4 (de
Inventor
Shuichi Yamashita
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.)
Mitsubishi Heavy Industries Ltd
Mitsubishi Heavy Industries Compressor Corp
Original Assignee
Mitsubishi Heavy Industries Ltd
Mitsubishi Heavy Industries Compressor Corp
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.)
Filing date
Publication date
Application filed by Mitsubishi Heavy Industries Ltd, Mitsubishi Heavy Industries Compressor Corp filed Critical Mitsubishi Heavy Industries Ltd
Publication of EP3012461A1 publication Critical patent/EP3012461A1/de
Publication of EP3012461A4 publication Critical patent/EP3012461A4/de
Withdrawn legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • 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
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet

Definitions

  • the present invention relates to a centrifugal compressor.
  • a centrifugal compressor As a compressor used in a plant or the like, a centrifugal compressor is known. Several improvements are proposed in order to enable miniaturization of the centrifugal compressor, or operation at a small flow rate.
  • Patent Literature 1 discloses a centrifugal compressor in which a flow path width of one part of a diffuser is narrowed by use of a variable diaphragm mechanism in order to enable operation at a small flow rate.
  • Patent Literature 2 discloses a centrifugal compressor in which a flow path height of a diffuser flow path is gradually increases and a flow path width is enlarged in order to attain miniaturization and enlarge an operating range to a large flow rate side.
  • the present invention has been made in view of the above circumstances, and an object of the invention is to provide a centrifugal compressor in which a malfunction such as shaft vibration due to rotating stall and degradation of performance due to friction losses or the like are suppressed.
  • a centrifugal compressor includes: an impeller that is rotatable around an axis, and discharges fluid, which flows in an axial direction along the axis, in a direction inclined from the axial direction; a casing section that houses the impeller; and a diffuser section that circulates the fluid discharged from the impeller, wherein the impeller includes a hub and a shroud that are arranged along the axial direction side by side, and a plurality of blades that are arranged between the hub and the shroud, wherein a flow path width of the diffuser section at an inflow position where the fluid flows in the diffuser section is narrower than a flow path width of the impeller at a discharge position where the fluid discharges from the impeller, and wherein a flow path width enlarged section wider than the flow path width of the diffuser section at the inflow position is provided on a downstream side with respect to the inflow position of the diffuser section.
  • the centrifugal compressor according to the present invention includes: the impeller that discharges the fluid, which flows along the axial direction, in the direction inclined from the axial direction; the casing section that houses the impeller; and the diffuser section that circulates the fluid discharged from the impeller, wherein the impeller has the hub and the shroud that are arranged along the axial direction side by side, and the plurality of blades that are arranged between the hub and the shroud.
  • the flow path width of the diffuser section at the inflow position where the fluid flows in the diffuser section is narrower than the flow path width of the impeller at the discharge position where the fluid discharges from the impeller.
  • the flow velocity of the fluid at the inflow position where the fluid flows in the diffuser section is sufficiently increased, and occurrence of rotating stall is suppressed, so that it is possible to suppress a malfunction such as shaft vibration due to rotating stall.
  • the flow path width enlarged section wider than the flow path width of the diffuser section at the inflow position is provided on a downstream side with respect to the inflow position of the diffuser section.
  • the diffuser section is defined by a hub side wall provided on a side of the hub, and a shroud side wall provided on a side of the shroud
  • the hub side wall at the flow path width enlarged section is disposed in a direction in which the flow path width of the diffuser section enlarges with respect to the hub side wall at the inflow position
  • the shroud side wall at the flow path width enlarged section is disposed in a direction in which the flow path width of the diffuser section enlarges with respect to the shroud side wall at the inflow position.
  • both side walls at the flow path width enlarged section of the diffuser section are disposed in the direction in which the flow path width of the diffuser section enlarges, and it is possible to suppress degradation of performance due to, for example, friction losses caused by increase in the flow velocity of the fluid, compared to a case where the flow path width from the inflow position of the diffuser section to the downstream side is the same.
  • the diffuser section is defined by a hub side wall provided on a side of the hub, and a shroud side wall provided on a side of the shroud, and the hub side wall at the flow path width enlarged section is disposed in a direction in which the flow path width of the diffuser section enlarges with respect to the hub side wall at the inflow position.
  • the hub side wall of the diffuser section at the flow path width enlarged section is disposed in the direction in which the flow path width of the diffuser section enlarges, so that it is possible to suppress degradation of performance due to, for example, friction losses caused by increase in the flow velocity of the fluid, compared to a case where the flow path width from the inflow position of the diffuser section to the downstream side is the same.
  • the hub side wall is disposed in the direction in which the flow path width of the diffuser section enlarges, and therefore it is possible to form the flow path in which the fluid is stably circulated, in a case where the discharge direction in which fluid discharges from the impeller is directed to a direction of the hub side wall with respect to a direction orthogonal to the axial direction.
  • the diffuser section is defined by a hub side wall provided on a side of the hub, and a shroud side wall provided on a side of the shroud, and the shroud side wall at the flow path width enlarged section is disposed in a direction in which the flow path width of the diffuser section enlarges with respect to the shroud side wall at the inflow position.
  • the shroud side wall of the diffuser section at the flow path width enlarged section is disposed in the direction in which the flow path width of the diffuser section enlarges, so that it is possible to suppress degradation of performance due to, for example, friction losses caused by increase in the flow velocity of the fluid, compared to a case where the flow path width from the inflow position of the diffuser section to the downstream side is the same.
  • a shape of the hub side wall may be a tapered shape in which the flow path width gradually enlarges along a circulating direction of the fluid at an intermediate position between the inflow position of the diffuser section and the flow path width enlarged section
  • a shape of the shroud side wall may be a tapered shape in which the flow path width gradually enlarges along the circulating direction of the fluid at the intermediate position of the diffuser section.
  • a shape of the hub side wall may be a tapered shape in which the flow path width gradually enlarges along a circulating direction of the fluid at an intermediate position between the inflow position of the diffuser section and the flow path width enlarged section.
  • a shape of the shroud side wall may be a tapered shape in which the flow path width gradually enlarges along a circulating direction of the fluid at an intermediate position between the inflow position of the diffuser section and the flow path width enlarged section.
  • a shape of the hub side wall may be a stepped shape in which the flow path width enlarges along a circulating direction of the fluid stepwise at an intermediate position between the inflow position of the diffuser section and the flow path width enlarged section
  • a shape of the shroud side wall may be a stepped shape in which the flow path width enlarges along the circulating direction of the fluid stepwise at the intermediate position of the diffuser section.
  • the flow path connecting the inflow position and the downstream side can be formed at the intermediate position of the diffuser section by a relatively easy machining process.
  • a shape of the hub side wall may be a stepped shape in which the flow path width enlarges along a circulating direction of the fluid stepwise at an intermediate position between the inflow position of the diffuser section and the flow path width enlarged section.
  • the flow path connecting the inflow position and the downstream side can be formed at the intermediate position of the diffuser section by a relatively easy machining process.
  • a shape of the shroud side wall may be a stepped shape in which the flow path width enlarges along a circulating direction of the fluid stepwise at an intermediate position between the inflow position of the diffuser section and the flow path width enlarged section.
  • the flow path connecting the inflow position and the downstream side can be formed at the intermediate position of the diffuser section by a relatively easy machining process.
  • a ratio of the flow path width of the diffuser section at the inflow position to the flow path width of the impeller at the discharge position is not less than 0.5 and less than 0.8.
  • the flow path width of the diffuser section at the inflow position is made to be a sufficiently narrow width, and the flow velocity of the fluid at the inflow position where the fluid flows in the diffuser section is sufficiently increased, and occurrence of rotating stall is suppressed, so that it is possible to suppress a malfunction such as shaft vibration due to rotating stall.
  • a ratio of a flow path width of the diffuser section at the flow path width enlarged section to the flow path width of the impeller at the discharge position is not less than 0.8 and not more than 1.0.
  • the flow path width of the diffuser section at the flow path width enlarged section is made to be a sufficiently wide width, so that it is possible to suppress degradation of performance due to, for example, friction losses caused by increase in the flow velocity of the fluid, compared to a case where the flow path width from the inflow position of the diffuser section to the downstream side is the same.
  • the impeller discharges the fluid, which flows along the axial direction, in a direction orthogonal to the axial direction.
  • a flow rate coefficient is not less than 0.01 and not more than 0.05.
  • the present invention it is possible to provide a centrifugal compressor in which a malfunction such as shaft vibration due to rotating stall is suppressed, and degradation of performance due to friction losses or the like is suppressed.
  • FIG. 1 is a longitudinal sectional view of the centrifugal compressor 10 of the first embodiment.
  • FIG. 2 is a front view of the centrifugal compressor 10 of the first embodiment.
  • the centrifugal compressor 10 illustrated in FIG. 1 includes an impeller 13 rotatable around an axis A, a casing section 11 housing the impeller 13, a diffuser section 15 for circulating fluid discharged from the impeller 13, and a volute section 16 provided downstream of the diffuser section 15.
  • FIG. 2 is a front view when viewing a position where fluid flows in the impeller 13 along the axial direction of axis A.
  • the impeller 13, the diffuser section 15, the casing section 11, and the volute section 16 are partially omitted.
  • the centrifugal compressor 10 of the first embodiment is a centrifugal compressor whose flow rate coefficient is a relatively small flow rate coefficient, namely not less than 0.01 and not more than 0.05.
  • the impeller 13 is connected to a driving device such as a motor and a turbine (not illustrated) through a rotary shaft (not illustrated) along the axis A, and is rotatable around the axis A.
  • the impeller 13 has a hub 1 and a shroud 2 arranged along the axial direction of axis A, and a plurality of blades 3 arranged between the hub 1 and the shroud 2. Although only one blade 3 is illustrated in FIG. 1 , a plurality of the blades 3 are arranged at equal intervals in a circumferential direction with the axis A as the center, between the hub 1 and the shroud 2 ( FIG. 2 ).
  • the impeller 13 is provided with a space defined by an inner wall 1a of the hub 1 and an inner wall 2a of the shroud 2, and the space is partitioned into a plurality of spaces by the plurality of blades 3. Then, the impeller 13 applies radial centrifugal force to fluid flowing along the axial direction (direction illustrated by the arrow in FIG. 1 ), discharges the fluid in a direction orthogonal to the axial direction (inclined direction; radial direction of the impeller 13), and allows the fluid to flow in the diffuser section 15.
  • the diffuser section 15 is a fluid flow path defined by a hub side wall 15a provided on the hub 1 side and a shroud side wall 15b provided on the shroud 2 side. As illustrated in FIG. 2 , the diffuser section 15 is provided so as to surround a discharge position provided on a whole circumference of the impeller 13. In the diffuser section 15, the flow velocity of the fluid discharged from the discharge position of the impeller 13 is reduced, so that kinetic energy (dynamic pressure) applied to the fluid is converted into pressure energy (static pressure).
  • the fluid is compressed, and flows in a volute section (volute chamber) 16 communicated with diffuser section 15.
  • the compressed fluid that flows in the volute section 16 is discharged to a discharge pipe (not illustrated) through a discharge port (not illustrated).
  • the driving device such as the motor and the turbine (not illustrated) rotates the impeller 13 around the axis A.
  • the impeller 13 rotates, so that fluid taken from a suction port (not illustrated) is introduced into the casing section 11.
  • centrifugal force in the direction orthogonal to the axis A radial direction
  • the fluid, to which the centrifugal force is applied is discharged from the impeller 13, and flows in the diffuser section 15.
  • the flow velocity of the fluid that flows in the diffuser section 15 reduces, and the fluid becomes compressed fluid to be discharged to the volute section 16.
  • the compressed fluid that flows in the volute section 16 is discharged to the discharge pipe (not illustrated) through the discharge port (not illustrated).
  • a flow path width W2 of the diffuser section 15 at an inflow position where fluid flows in the diffuser section 15 is narrower than a flow path width W1 of the impeller 13 at a discharge position where the fluid is discharged from the impeller 13.
  • a flow path width enlarged section 15c in which the flow path width of the diffuser section 15 is enlarged is provided on the downstream side of the inflow position where the fluid flows in the diffuser section 15, in order to suppress the losses due to the friction.
  • the flow path width W1 expresses a length in a direction along the axis A (axial direction).
  • the flow path width W1 is equal to a distance in the axial direction between the inner wall 1a of the hub 1 and the inner wall 2a of the shroud 2 at the discharge position where the fluid is discharged from the impeller 13.
  • the flow path width W2 expresses a length in the direction along the axis A.
  • the flow path width W2 is equal to a distance in the axial direction between the hub side wall 15a and the shroud side wall 15b at the inflow position where the fluid flows in the diffuser section 15.
  • the flow path width of the diffuser section 15 (distance in the axial direction between the hub side wall 15a and the shroud side wall 15b) in a range in a circulating direction of the fluid (direction orthogonal to the axial direction) from the inflow position where the fluid flows in the diffuser section 15 to L1 is constant, namely the flow path width W2. Then, at a position (intermediate position) where the distance from the inflow position is between L1 and L2, the hub side wall 15a that defines the diffuser section 15 has a tapered shape in which the flow path width gradually enlarges along the circulating direction of the fluid.
  • the shroud side wall 15b that defines the diffuser section 15 also has a tapered shape in which the flow path width gradually enlarges along the circulating direction of the fluid.
  • the hub side wall 15a at a position where the distance from the inflow position where the fluid flows in the diffuser section 15 is between L2 and L3 is disposed in a direction in which the flow path width of the diffuser section 15 enlarges with respect to the hub side wall 15a at the inflow position where the fluid flows in the diffuser section 15.
  • the shroud side wall 15b is disposed in a direction in which the flow path width of the diffuser section 15 enlarges with respect to the shroud side wall 15b at the inflow position where the fluid flows in the diffuser section 15.
  • the flow path width of the diffuser section 15 is constant, namely a flow path width W3.
  • the flow path width enlarged section 15c that is wider than the flow path width of the diffuser section 15 at the inflow position of the diffuser section 15 is provided on the downstream side in the circulating direction of the fluid with respect to the inflow position where the fluid flows in the diffuser section 15.
  • the shape of the hub side wall 15a and the shape of the shroud side wall 15b are desirably horizontally symmetrical with respect to the center axis of the flow path.
  • a ratio of the flow path width W2 of the diffuser section 15 at the inflow position to the flow path width W1 of the impeller 13 at the discharge position is not less than 0.5 and less than 0.8. Additionally, a ratio of the flow path width W3 of the diffuser section 15 at the flow path width enlarged section 15c to the flow path width W1 of the impeller 13 at the discharge position is not less than 0.8 and not more than 1.0. However, as described above, the respective ratios are selected such that the flow path width W3 of the diffuser section 15 at the flow path width enlarged section 15c is wider than the flow path width W2 of the diffuser section 15 at the inflow position.
  • the centrifugal compressor 10 of the first embodiment includes the impeller 13 that discharges fluid, which flows along the axial direction, in the inclined direction from the axial direction (radial direction orthogonal to the axial direction), the casing section 11 that houses the impeller 13, and the diffuser section 15 that circulates the fluid discharged from the impeller 13, wherein the impeller 13 has the hub 1 and the shroud 2 arranged along the axial direction side by side, and the plurality of blades 3 arranged between the hub 1 and the shroud 2.
  • the flow path width W2 of the diffuser section 15 at the inflow position where the fluid flows in the diffuser section 15 is narrower than the flow path width W1 of the impeller 13 at the discharge position where the fluid is discharged from the impeller 13.
  • the flow velocity of the fluid at the inflow position where the fluid flows in the diffuser section 15 is sufficiently increased, and occurrence of rotating stall is suppressed, so that it is possible to suppress a malfunction such as shaft vibration due to rotating stall.
  • the flow path width enlarged section 15c having the flow path width W3 wider than the flow path width of the diffuser section 15 at the inflow position of the diffuser section 15 is provided downstream with respect to the inflow position of the diffuser section 15.
  • the diffuser section 15 is defined by the hub side wall 15a provided on the hub 1 side, and the shroud side wall 15b provided on the shroud 2 side. Then, the hub side wall 15a at the flow path width enlarged section 15c is disposed in the direction in which the flow path width of the diffuser section 15 enlarges with respect to the hub side wall 15a at the inflow position. Additionally, the shroud side wall 15b at the flow path width enlarged section 15c is disposed in the direction in which the flow path width of the diffuser section 15 enlarges with respect to the shroud side wall 15b at the inflow position.
  • the both side walls at the flow path width enlarged section 15c of the diffuser section 15 are disposed in the direction in which the flow path width of the diffuser section 15 enlarges, so that it is possible to suppress degradation of performance due to, for example, friction losses caused by increase in the flow velocity of the fluid, compared to the case where the flow path width from the inflow position of the diffuser section 15 to the downstream side is the same flow path width, namely the flow path width W2.
  • the shape of the hub side wall 15a is the tapered shape in which the flow path width gradually enlarges along the circulating direction of the fluid at the intermediate position between the inflow position of the diffuser section 15 and the flow path width enlarged section 15c
  • the shape of the shroud side wall 15b is the tapered shape in which the flow path width gradually enlarges along the circulating direction of the fluid at the intermediate position of the diffuser section 15.
  • the ratio of the flow path width W2 of the diffuser section 15 at the inflow position to the flow path width W1 of the impeller 13 at the discharge position is not less than 0.5 and less than 0.8.
  • the flow path width W2 relative to the flow path width W1 is made to be a sufficiently narrow width, and the flow velocity of the fluid at the inflow position where the fluid flows in the diffuser section 15 is sufficiently increased, and occurrence of rotating stall is suppressed, so that it is possible to suppress a malfunction such as shaft vibration due to rotating stall.
  • the ratio of the flow path width W3 of the diffuser section 15 at the flow path width enlarged section 15c to the flow path width W1 of the impeller 13 at the discharge position is not less than 0.8 and not more than 1.0.
  • the flow path width W3 relative to the flow path width W1 is made to be a sufficiently wide width, and it is possible to suppress degradation of performance due to, for example, friction losses caused by increase in the flow velocity of the fluid, compared to the case where the flow path width from the inflow position of the diffuser section 15 to the downstream side is the same flow path width, namely the flow path width W2.
  • FIG. 3 is a longitudinal sectional view of the centrifugal compressor 10 of the second embodiment.
  • the both side walls (the hub side wall 15a and the shroud side wall 15b) of the diffuser section 15 at the flow path width enlarged section 15c is disposed in the direction in which the flow path width of the diffuser section 15 enlarges.
  • one side wall (hub side wall 15a) of a diffuser section 15 at a flow path width enlarged section 15c is disposed in a direction in which a flow path width of the diffuser section 15 enlarges.
  • the second embodiment is a modification of the first embodiment.
  • Configurations other than the shape of the hub side wall 15a which defines the diffuser section 15 are similar to those of the first embodiment, and therefore the description of the configurations will be omitted.
  • the hub side wall 15a at the flow path width enlarged section 15c is disposed in the direction in which the flow path width of the diffuser section 15 enlarges with respect to the hub side wall 15a at an inflow position.
  • the shroud side wall 15b at the flow path width enlarged section 15c and the shroud side wall 15b at the inflow position are disposed such that the positions in the axial direction are the same.
  • the centrifugal compressor 10 illustrated in FIG. 3 discharges fluid, which flows in an impeller 13, in a direction orthogonal to the axial direction
  • a modification in which the centrifugal compressor discharges fluid in a direction inclined to the hub side wall 15a with respect to the direction orthogonal to the axial direction is applicable.
  • the fluid that flows in the diffuser section 15 includes a velocity component in a direction in which the fluid vertically abuts on the hub side wall 15a. Accordingly, a loss due to friction is more easily generated at the hub side wall 15a than the shroud side wall 15b, and therefore suppression of a friction loss generated at the hub side wall 15a is desirable.
  • the hub side wall 15a is disposed in the direction in which the flow path width of the diffuser section 15 enlarges, and therefore it is possible to form the flow path in which the fluid is stably circulated, and a friction loss caused by the hub side wall 15a is suppressed, in a case where a discharge direction in which fluid discharged from the impeller 13 is directed (inclined) to the direction of the hub side wall 15a with respect to the direction orthogonal to the axial direction.
  • a compressor of a type of discharge in a direction inclined to the hub side wall 15a with respect to the direction orthogonal to the axial direction of the impeller 13 is called a mixed flow compressor.
  • the compressor is not called the mixed flow compressor, but called a centrifugal compressor which means a compressor that converts fluid flowing in the axial direction into fluid including a velocity component in a direction orthogonal to an axis A (centrifugal direction).
  • a flow path width W2 of the diffuser section 15 at the inflow position where the fluid flows in the diffuser section 15 is narrower than a flow path width W1 of the impeller 13 at a discharge position where the fluid is discharged from the impeller 13.
  • the hub side wall 15a at the flow path width enlarged section 15c is disposed in the direction in which the flow path width of the diffuser section 15 enlarges with respect to the hub side wall 15a at the inflow position.
  • the hub side wall 15a of the diffuser section 15 at the flow path width enlarged section 15c is disposed in the direction in which the flow path width of the diffuser section 15 enlarges, so that it is possible to suppress degradation of performance due to, for example, friction losses caused by increase in the flow velocity of the fluid, compared to a case where the flow path width from the inflow position of the diffuser section 15 to the downstream side is the same flow path width, namely the flow path width W2.
  • the shape of the hub side wall 15a is a tapered shape in which the flow path width gradually enlarges along a circulating direction of the fluid at an intermediate position between the inflow position of the diffuser section 15 and the flow path width enlarged section 15c.
  • FIG. 4 is a longitudinal sectional view of the centrifugal compressor 10 of the third embodiment.
  • the both side walls (the hub side wall 15a and the shroud side wall 15b) of the diffuser section 15 at the flow path width enlarged section 15c is disposed in the direction in which the flow path width of the diffuser section 15 enlarges.
  • one side wall (shroud side wall 15b) of a diffuser section 15 at a flow path width enlarged section 15c is disposed in a direction in which a flow path width of the diffuser section 15 enlarges.
  • the third embodiment is a modification of the first embodiment. Configurations other than the shape of the shroud side wall 15b which defines the diffuser section 15 are similar to those of the first embodiment, and therefore the description of the configurations will be omitted.
  • the shroud side wall 15b at the flow path width enlarged section 15c is disposed in the direction in which the flow path width of the diffuser section 15 enlarges with respect to the shroud side wall 15b at an inflow position.
  • the hub side wall 15a at the flow path width enlarged section 15c and the hub side wall 15a at the inflow position are disposed such that the positions in the axial direction are the same.
  • a flow path width W2 of the diffuser section 15 at the inflow position where the fluid flows in the diffuser section 15 is narrower than a flow path width W1 of the impeller 13 at a discharge position where the fluid is discharged from the impeller 13.
  • the shroud side wall 15b at the flow path width enlarged section 15c is disposed in the direction in which the flow path width of the diffuser section 15 enlarges with respect to the shroud side wall 15b at the inflow position.
  • the shroud side wall 15b of the diffuser section 15 at the flow path width enlarged section 15c is disposed in the direction in which the flow path width of the diffuser section 15 enlarges, so that it is possible to suppress degradation of performance due to, for example, friction losses caused by increase in the flow velocity of the fluid, compared to a case where the flow path width from the inflow position of the diffuser section 15 to the downstream side is the same flow path width, namely the flow path width W2.
  • the shape of the shroud side wall 15b is the tapered shape in which the flow path width gradually enlarges along a circulating direction of the fluid at the intermediate position of the diffuser section 15.
  • FIG. 5 is a longitudinal sectional view of the centrifugal compressor 10 of the fourth embodiment.
  • both the hub side wall 15a and the shroud side wall 15b have tapered shapes in which the flow path width gradually enlarges along the circulating direction of fluid.
  • a flow path width of a diffuser section 15 (distance in the axial direction between a hub side wall 15a and a shroud side wall 15b) in a range in the circulating direction of the fluid (direction orthogonal to the axial direction) from an inflow position where the fluid flows in the diffuser section 15 to L4 is constant, namely a flow path width W2. Then, at a position where the distance from the inflow position is between L4 and L3, the flow path width of the diffuser section 15 is constant, namely a flow path width W3.
  • the diffuser section 15 may be formed in a stepped shape of two steps, three steps, or more steps, and the flow path width of the diffuser section may be gradually enlarge.
  • both the hub side wall 15a and the shroud side wall 15b are provided with stepped shapes.
  • the stepped shape may be provided in any one of the hub side wall 15a and the shroud side wall 15b, and the stepped shape may not be provided in the other wall.
  • the hub side wall 15a at the flow path width enlarged section 15c, and the hub side wall 15a at the inflow position are disposed such that the positions in the axial direction are the same.
  • the shroud side wall 15b at the flow path width enlarged section 15c, and the shroud side wall 15b at the inflow position are disposed such that the positions in the axial direction are the same.
  • a flow path width W2 of the diffuser section 15 at the inflow position where the fluid flows in the diffuser section 15 is narrower than a flow path width W1 of an impeller 13 at a discharge position where the fluid is discharged from the impeller 13.
  • the flow path width enlarged section 15c having the flow path width W3, which is wider than the flow path width W2 of the diffuser section 15 at the inflow position of the diffuser section 15, is provided on the downstream side with respect to the inflow position of the diffuser section 15.
  • the shape of the hub side wall 15a is the stepped shape in which the flow path width enlarges along the circulating direction of the fluid stepwise at the intermediate position between the inflow position of the diffuser section 15 and the flow path width enlarged section 15c
  • the shape of the shroud side wall 15b is the stepped shape in which the flow path width gradually enlarges along the circulating direction of the fluid at the intermediate position of the diffuser section 15.
  • FIG. 6 is a longitudinal sectional view of the centrifugal compressor 10 of the fifth embodiment.
  • the centrifugal compressor 10 of the fifth embodiment is a multistage centrifugal compressor in which fluid compressed by an impeller 13 and a diffuser section 15 at the first stage flows in an impeller 13 and a diffuser section 15 at a next stage.
  • the fifth embodiment is a modification of the first embodiment. Configurations are similar to those of the first embodiment except that a return bend 17 and a return vane 18 are provided in place of the volute section 16, and therefore the description of the configurations will be omitted.
  • compressed fluid that flows in the flow path width enlarged section 15c of the diffuser section 15 flows in the volute section 16 provided downstream of the flow path width enlarged section 15c.
  • compressed fluid that flows in a flow path width enlarged section 15c of the diffuser section 15 flows in the return bend 17 provided downstream of the flow path width enlarged section 15c.
  • the compressed fluid that flows in the return bend 17 is guided to the impeller 13 at the next stage (second stage) via the return vane 18.
  • the fluid guided to the impeller 13 at the second stage is discharged to the diffuser section 15 at the second stage.
  • the fluid further compressed in the diffuser section 15 at the second stage is guided to a volute section 16 similar to the volute section illustrated in FIG. 1 of the first embodiment.
  • fluid guided to an impeller 13 at a second stage is discharged to a diffuser section 15 at a second stage.
  • the fluid further compressed in the diffuser section 15 at the second stage flows in a return bend 17 at the second stage.
  • the compressed fluid that flows in the return bend 17 at the second stage is guided to an impeller 13 at a next state (third stage) via the return vane 18.
  • the fluid guided to the impeller 13 at the third stage is discharged to a diffuser section 15 at the third stage.
  • the fluid further compressed in the diffuser section 15 at the third stage is guided to a volute section 16 similar to the volute section illustrated in FIG. 1 of the first embodiment.
  • the two-stage or the three-stage centrifugal compressor 10 is employed as the centrifugal compressor 10, so that it is possible to further increase a compression ratio of fluid. Additionally, an effect similar to the effect of the first embodiment can be exerted by the shapes of the impeller 13 and the diffuser section 15 at each stage.
  • the shape of the diffuser section 15 at each stage not only the shape described in the first embodiment, but also any shape described in the second embodiment to the fourth embodiment can be employed.
  • the two-stage and the three-stage centrifugal compressor 10 are described. However, a modification of a four or more stage centrifugal compressor 10 may be employed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP13887157.9A 2013-06-20 2013-06-20 Zentrifugalverdichter Withdrawn EP3012461A4 (de)

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PCT/JP2013/066989 WO2014203379A1 (ja) 2013-06-20 2013-06-20 遠心圧縮機

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EP3012461A4 EP3012461A4 (de) 2017-02-08

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CN105121864A (zh) 2015-12-02
CN105121864B (zh) 2017-06-09
EP3012461A4 (de) 2017-02-08
WO2014203379A1 (ja) 2014-12-24
US20160108920A1 (en) 2016-04-21

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