WO2016042817A1 - Compresseur centrifuge - Google Patents

Compresseur centrifuge Download PDF

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Publication number
WO2016042817A1
WO2016042817A1 PCT/JP2015/059343 JP2015059343W WO2016042817A1 WO 2016042817 A1 WO2016042817 A1 WO 2016042817A1 JP 2015059343 W JP2015059343 W JP 2015059343W WO 2016042817 A1 WO2016042817 A1 WO 2016042817A1
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WO
WIPO (PCT)
Prior art keywords
wall portion
impeller
casing
hub
shroud
Prior art date
Application number
PCT/JP2015/059343
Other languages
English (en)
Japanese (ja)
Inventor
穣 枡谷
吉田　悟
Original Assignee
三菱重工業株式会社
三菱重工コンプレッサ株式会社
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 三菱重工業株式会社, 三菱重工コンプレッサ株式会社 filed Critical 三菱重工業株式会社
Priority to US15/511,593 priority Critical patent/US20170261001A1/en
Publication of WO2016042817A1 publication Critical patent/WO2016042817A1/fr

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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
    • 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
    • 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
    • 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
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid 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
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0207—Surge control by bleeding, bypassing or recycling fluids

Definitions

  • the present invention relates to a centrifugal compressor in which a vaneless diffuser is provided on the outlet side of the impeller.
  • centrifugal compressors are used in petrochemical plants and natural gas plants.
  • a configuration using a vaneless diffuser in which no vane is provided in the diffuser portion on the outlet side of the impeller is widely adopted.
  • the configuration using the vaneless diffuser has an advantage that the structure is simple, and if the flow angle is appropriate, the loss is small, the operating range is wide, and no fluid excitation force is generated on the impeller.
  • vaneless diffusers when the flow angle increases, cause loss, and also cause rotational stall that causes uneven flow in the circumferential direction, which may be caused by pressure fluctuations, shaft vibration, discharge pipe vibration, etc. Will occur. It is known that this turning stall occurs particularly when the centrifugal compressor is operated in a small flow rate region.
  • the flow rate of the turning stall at the time when the turning stall first occurs in the vaneless diffuser is reduced while suppressing the decrease in the efficiency of the centrifugal compressor.
  • a configuration for further reducing the turning stall start flow rate is being sought.
  • This invention is made in view of such a situation, Comprising: It aims at providing the centrifugal compressor which aimed at the small flow volume of a turning stall start flow rate in the structure which provided the fluid circulation flow path. .
  • a centrifugal compressor includes a vaneless diffuser provided on an outlet side of an impeller, and a fluid in a first wall portion of a hub casing that forms the vaneless diffuser.
  • a fluid circulation passage having an inlet opened and a fluid outlet opened in a second wall portion of the hub casing facing the rear surface of the hub disk of the impeller.
  • the vaneless diffuser includes at least the first wall portion of the hub casing.
  • the vaneless diffuser has a channel width smaller than the outlet width of the impeller by projecting toward the wall portion side of the shroud casing facing the first wall portion, and the hub casing is connected to the outlet of the impeller.
  • An inclined wall portion that connects the second wall portion and the first wall portion, starting from the entrance of the vane-less diffuser, is provided.
  • the fluid inlet is opened in the first wall portion of the hub casing forming the vaneless diffuser
  • the fluid outlet is opened in the second wall portion of the hub casing facing the back surface of the hub disk of the impeller. Since the flow path is provided, a part of the high-pressure fluid can be circulated to the inlet side of the vaneless diffuser by the fluid circulation flow path, and the flow rate of the fluid flowing through the vaneless diffuser can be increased. For this reason, the turning stall occurrence point can be shifted to the small flow rate side by the increased flow rate ratio, and the occurrence of turning stall can be suppressed.
  • the vaneless diffuser projects at least the first wall portion of the hub casing toward the wall portion of the shroud casing facing the first wall portion, thereby reducing the flow path width of the vaneless diffuser to the outlet width of the impeller.
  • the hub casing has an inclined wall portion that starts between the outlet of the impeller and the inlet of the vaneless diffuser and connects the second wall portion and the first wall portion.
  • the flow path width of the vaneless diffuser is narrowed by the inclined wall, the flow in the vaneless diffuser is smooth even at a small flow rate with a small fluid flow rate, and the turning stall point is further reduced to the smaller flow rate side. Can be shifted to.
  • the end of the inclined wall portion connected to the first wall portion is located on the radially outer side than the radially inner end portion of the impeller in the wall portion of the shroud casing.
  • the inclination angle of the inclined wall portion on the hub casing side can be formed more gently than on the shroud casing side, so that the main flow circulates in the main fluid flow without disturbing the flow of the main fluid blown from the impeller outlet. The flow can be smoothly merged.
  • the first wall portion of the hub casing protrudes toward the wall portion side of the shroud casing from the hub side extension line extending radially outward from the outlet of the impeller, and the hub side protruding length from the hub side extension line to the first wall portion. Is preferably 50% or less of the exit width of the impeller. According to this configuration, it is possible to suppress a decrease in the efficiency of the centrifugal compressor while shifting the turning stall occurrence point to the small flow rate side.
  • the wall portion of the shroud casing protrudes toward the first wall portion side of the hub casing from the shroud side extension line extending radially outward from the outlet of the impeller, and the shroud side protrusion length from the shroud side extension line to the wall portion is: It is preferably 20% or less of the outlet width of the impeller. Within this range, the effect of shifting the turning stall occurrence point to the small flow rate side is exhibited.
  • the vaneless diffuser projects at least the first wall portion of the hub casing toward the wall portion side of the shroud casing facing the first wall portion, thereby the vaneless diffuser.
  • the hub casing is formed to be smaller than the outlet width of the impeller, and the hub casing is connected between the second wall portion and the first wall portion, starting from the impeller outlet and the vaneless diffuser inlet. Therefore, by flowing the circulating flow blown out from the outlet of the fluid circulation channel along the inclined wall portion, it can smoothly merge with the fluid main flow blown out from the impeller outlet. The flow of fluid in the less diffuser is not disturbed.
  • the flow path width of the vaneless diffuser is narrowed by the inclined wall, the flow in the vaneless diffuser is smooth even at a small flow rate with a small fluid flow rate, and the turning stall point is further reduced to the smaller flow rate side. Can be shifted to.
  • FIG. 1 is a longitudinal sectional view of a centrifugal compressor according to this embodiment.
  • FIG. 2 is a cross-sectional view of a main part showing a configuration in the vicinity of the vaneless diffuser.
  • FIG. 3 is a graph showing the relationship between the flow coefficient, the pressure coefficient, and the efficiency in Comparative Examples 1 to 8 and Examples.
  • FIG. 4 is a graph showing the relationship between the flow coefficient at the turning stall start point and the efficiency of the design point.
  • FIG. 5 is a cross-sectional view of a main part showing a configuration in the vicinity of a vaneless diffuser according to another embodiment.
  • FIG. 1 is a longitudinal sectional view of a centrifugal compressor according to this embodiment.
  • the centrifugal compressor 1 includes a casing 2 configured by combining a plurality of parts, and a rotating shaft 5 that is rotatably supported around the axis L in the casing 2 via a bearing (not shown). And closed type impellers 6 and 6 provided so as to rotate integrally with the rotary shaft 5. That is, the centrifugal compressor 1 of the present embodiment is a two-stage centrifugal compressor.
  • the centrifugal compressor 1 is driven by a driving device (not shown), and the impellers 6 and 6 are rotated to rotate the impellers 6 and 6 through a suction port 10 provided in the casing 2. Etc. are sucked.
  • a suction passage 11 is connected to the suction port 10 via a suction space 10A formed in the casing 2, and the suction passage 11 bends along the axis L direction (axial direction) of the rotary shaft 5.
  • the first stage impeller 6 is opened facing the suction port 6A.
  • Centrifugal force is applied to the fluid sucked from the suction port 10 by the rotation of the first stage impeller 6, and the kinetic energy is pressured by the first stage vaneless diffuser 12 provided at the outlet 6 ⁇ / b> B of the impeller 6. Converted into energy. Further, this fluid is guided through the return bend 14 and the return vane 15 to the suction port 6A of the second stage impeller 6 which is the next stage compression stage.
  • the compressed fluid is similarly given a centrifugal force by the second stage impeller 6, and the kinetic energy is converted into pressure energy by the second stage vaneless diffuser 12, and further becomes a high pressure compressed fluid to the scroll 16. Discharged.
  • the scroll 16 is then sent to a discharge pipe (not shown) via a discharge port 17 provided in the casing 2.
  • symbol 18 in FIG. 1 is a balance piston provided in order to adjust the thrust of the impeller 6.
  • the vaneless diffuser 12 is provided in communication with the exit side of the space where the impeller 6 rotates, and a flow path for converting the kinetic energy of the fluid to which the centrifugal force is given by the impeller 6 into pressure energy and sending it out.
  • a rotating stall may occur in which the circumferential flow becomes non-uniform.
  • the present embodiment employs the following configuration.
  • FIG. 2 is a cross-sectional view of the main part showing the configuration in the vicinity of the vaneless diffuser.
  • the vaneless diffuser 12 is formed by a shroud casing 2A and a hub casing 2B that constitute the casing 2.
  • the hub casing 2B is provided with a fluid circulation passage (bypass passage, also simply referred to as bypass) 21 for circulating the fluid in the vaneless diffuser 12 back to the vicinity of the blower outlet (impeller outlet) 6B of the impeller 6. It has been. Specifically, as shown in FIG.
  • the fluid circulation channel 21 includes an inlet 21 ⁇ / b> A and an outlet 21 ⁇ / b> B, and the inlet 21 ⁇ / b> A opens to the first wall portion 22 of the hub casing 2 ⁇ / b> B that forms the vaneless diffuser 12.
  • the outlet 21B opens to the second wall portion 23 of the hub casing 2B facing the back surface of the hub disk 6C constituting the impeller 6.
  • the fluid circulation passage 21 takes in a part of the high-pressure compressed fluid that has passed through the vaneless diffuser 12 from the inlet 21A and blows it out from the outlet 21B to blow out the vaneless diffuser 12 and the impeller 6 outlet 6B. And a part of the compressed fluid is circulated.
  • a plurality of fluid circulation channels 21 may be provided, and the outlet 21B of the fluid circulation channel 21 is formed to face the back surface of the hub disk 6C of the impeller 6.
  • the fluid blown out from the outlet 21 ⁇ / b> B is given a circumferential flow velocity by the back surface of the hub disk 6 ⁇ / b> C of the impeller 6 as the impeller 6 rotates.
  • the circumferential flow velocity when the fluid blown out from the outlet 21B merges with the fluid main flow blown out from the impeller 6 can be set to a circumferential flow velocity substantially equal to the fluid main flow.
  • first wall portion 22 of the hub casing 2B is formed so as to protrude from the second wall portion 23 toward the wall portion 31 side of the shroud casing 2A facing the first wall portion 22.
  • first wall portion 22 of the hub casing 2B is a hub side that extends radially outward (in the direction of arrow A in FIG. 2) of the impeller 6 from the end of the air outlet 6B of the impeller 6 on the hub casing 2B side. It protrudes toward the wall 31 side of the shroud casing 2A from the extension line HA.
  • the first wall portion 22 and the second wall portion 23 are connected by an inclined wall portion 24.
  • the wall portion 31 of the shroud casing 2A is also the hub casing 2B from the shroud side extension line SA extending from the end of the air outlet 6B of the impeller 6 on the shroud casing 2A side to the radially outer side of the impeller 6. It protrudes toward the first wall portion 22 side.
  • the shroud casing 2 ⁇ / b> A includes a horizontal wall 30 that faces the air outlet 6 ⁇ / b> B of the impeller 6 and extends in the direction of the axis L of the rotating shaft 5, and the horizontal wall 30 and the wall portion 31 are connected via a connecting wall 32.
  • the connecting wall 32 can adopt various shapes, and may be an R wall or an inclined wall formed with a predetermined radius of curvature.
  • the end 31 ⁇ / b> A on the radially inner side of the impeller 6 in the wall portion 31 described above serves as a connection portion with the connection wall 32.
  • the wall portion 31 of the shroud casing 2A and the first wall portion 22 of the hub casing 2B both extend within the projection plane of the air outlet 6B of the impeller 6, and the wall portion 31 and the first wall portion 22.
  • the flow path width D of the vaneless diffuser 12 is formed smaller than the width (outlet width) W of the outlet 6B of the impeller 6.
  • the flow path width D of the vaneless diffuser 12 is formed so as to narrow the width W of the air outlet 6B of the impeller 6.
  • the hub side projection length HD is 50 of the width W of the outlet 6B of the impeller 6. % Or less is preferable.
  • the shroud side projection length SD is the width W of the outlet 6B of the impeller 6. It is preferable to make it 50% or less.
  • the shroud side protrusion length SD is preferably 20% or less of the width W of the air outlet 6B of the impeller 6.
  • the diaphragm of the first wall portion 22 of the hub casing 2B will be described.
  • the first wall portion 22 protrudes so as to gradually extend into the projection plane of the air outlet 6B of the impeller 6 by the inclined wall portion 24.
  • the shape of the inclined wall portion (protrusion) 24 is important.
  • the inclined wall portion 24 is connected to the second wall portion 23 between the air outlet 6B of the impeller 6 and the inlet (position of the horizontal wall 30) of the vaneless diffuser 12 in the radial direction of the impeller 6. 24A is provided.
  • the end 24B of the inclined wall portion 24 is provided at a position radially outside the end portion 31A on the radially inner side of the impeller 6 in the wall portion 31 of the shroud casing 2A.
  • the inclined wall portion 24 can be formed to have a gentle throttle, and the circulating flow can be smoothly flowed into the main fluid flow without disturbing the flow of the main fluid flow blown from the outlet 6B of the impeller 6. Can be joined.
  • the inclined wall portion 24 includes not only a flat wall formed at a predetermined angle but also a curved wall having a curved surface, for example. Next, examples and comparative examples will be described.
  • Comparative Example 1 In Comparative Example 1, the wall portion 31 of the shroud casing 2A protrudes from the shroud side extension line SA, and the first wall portion 22 of the hub casing 2B is formed on the hub side extension line HA.
  • the shroud casing 2A and the hub casing 2B each have an inclined wall portion (not shown), and the end of the inclined wall portion on the shroud casing 2A side is formed radially outward from the end of the inclined wall portion of the hub casing 2B. (SH side loose protrusion).
  • the shroud side protrusion length SD of the wall portion 31 of the shroud casing 2A is 40% of the width W of the blower outlet 6B of the impeller 6, and the flow path width D of the vaneless diffuser 12 and the width W of the blower outlet 6B are The ratio D / W is 0.6.
  • the fluid circulation channel 21 is not provided.
  • Comparative Example 3 In Comparative Example 3, there is only a corner R portion having a small radius of curvature R between the wall portion 31 of the shroud casing 2A and the horizontal wall 30 (SH side sudden protrusion). Other configurations are the same as those of the first comparative example.
  • Comparative Example 5 In Comparative Example 5, there is only a corner R portion having a small radius of curvature R between the wall portion 31 and the horizontal wall 30 of the shroud casing 2A (SH side sudden protrusion). Other configurations are the same as those in Comparative Example 4.
  • the fluid circulation channel 21 is provided in the first wall portion 22 and the second wall portion 23 of the hub casing 2B.
  • the fluid circulation channel 21 has a position where the radius R2 of the opening center of the inlet 21A of the fluid circulation channel 21 satisfies 1.1R1 ⁇ R2 ⁇ 1.4R1 when the radius of the outlet 6B of the impeller 6 is R1. Is open.
  • Other configurations are the same as those of the first comparative example.
  • Comparative Example 7 In Comparative Example 7, there is only a corner R portion with a small radius of curvature R between the wall portion 31 of the shroud casing 2A and the horizontal wall 30 (SH side sudden protrusion). Other configurations are the same as those in Comparative Example 6.
  • the wall portion 31 of the shroud casing 2A protrudes from the shroud side extension line SA, and the first wall portion 22 of the hub casing 2B also protrudes from the hub side extension line HA.
  • the shroud side protrusion length SD is 17% of the width W of the air outlet 6B of the impeller 6, and the hub side protrusion length HD is 23% of the width W of the air outlet 6B of the impeller 6. For this reason, the ratio D / W of the flow path width D of the vaneless diffuser 12 and the width W of the outlet 6B is 0.6.
  • the inclined wall portion 24 of the hub casing 2B has a terminal end 24B provided in the vicinity of the inlet 21A of the fluid circulation channel 21, and narrows the channel width D of the vaneless diffuser 12 with a gentle inclination (the hub side is loose). Protruding).
  • Other configurations are the same as those of Comparative Example 6.
  • FIG. 3 is a graph showing the relationship between the flow coefficient, the pressure coefficient, and the efficiency in Comparative Examples 1 to 8 and Examples
  • FIG. 4 shows the flow coefficient and design point of the turning stall start point (in FIG. 3). It is a graph which shows the relationship with the efficiency of a vertical broken line position. In FIG. 4, the ratio is expressed as a ratio based on Comparative Example 1.
  • the shroud side protrusion length SD is preferably 20% or less of the width W of the air outlet 6B of the impeller 6.
  • the shroud side protrusion length SD is 17% of the width W of the air outlet 6B of the impeller 6, and the hub side protrusion length HD is 23% of the width W of the air outlet 6B of the impeller 6.
  • the ratio D / W of the flow path width D of the vaneless diffuser 12 and the width W of the outlet 6B is set to 0.6.
  • the end 24B of the inclined wall portion 24 of the hub casing 2B is located at a position radially outside the end portion 31A on the radially inner side of the impeller 6 in the wall portion 31 of the shroud casing 2A. Is provided.
  • the inclined wall portion 24 can be formed to have a gentle throttle, and the circulating flow can smoothly join the fluid main flow without disturbing the flow of the fluid main flow blown from the outlet 6B of the impeller 6. be able to. Therefore, as shown in FIG. 4, the turning stall starting point can be greatly shifted to the small flow rate side, and the turning stall can be prevented from occurring until the surge point. Furthermore, the efficiency can be made higher than in a configuration in which the flow passage width D of the vaneless diffuser 12 is greatly reduced to have the same rotational stall occurrence point in the state where the fluid circulation passage 21 is not provided. In the example, even if the width ratio D / W is not reduced to 0.4 of Comparative Example 5, the same turning stall occurrence point can be realized at 0.6, and the efficiency is higher than that of Comparative Example 5. Understandable.
  • the shroud side protrusion length SD and the hub side protrusion length HD are set to 40% of the width W of the air outlet 6B of the impeller 6.
  • the hub side protrusion length HD (and the shroud side protrusion length SD) is preferably set to 50% or less of the width W of the air outlet 6B of the impeller 6.
  • the centrifugal compressor 1 includes the vaneless diffuser 12 provided on the air outlet 6B side of the impeller 6 and the first wall portion 22 of the hub casing 2B that forms the vaneless diffuser 12.
  • the vaneless diffuser 12 includes a fluid circulation channel 21 having an inlet 21A opened and an outlet 21B opened in the second wall portion 23 of the hub casing 2B facing the rear surface of the hub disk 6C of the impeller 6.
  • the flow path width D of the vaneless diffuser 12 is formed smaller than the width W of the outlet 6B of the impeller 6, and the hub casing 2B 24 A between the air outlet 6B of the impeller 6 and the inlet of the vaneless diffuser 12 is a starting end 24A, and the second wall 23 and the first wall 22 are connected. That includes a sloped wall portion 24. For this reason, by flowing the circulating flow blown from the outlet 21B of the fluid circulation channel 21 along the inclined wall portion 24, the fluid main flow blown from the blower outlet 6B of the impeller 6 can be smoothly merged. The fluid flow in the vaneless diffuser 12 is not disturbed.
  • the flow path width D of the vaneless diffuser 12 is narrowed by the inclined wall portion 24, the flow in the vaneless diffuser 12 becomes smooth even at a small flow rate with a small fluid flow rate. It can be shifted to a smaller flow rate side.
  • the inclined wall portion 24 has a terminal end 24B connected to the first wall portion 22 radially outside the end portion 31A on the radially inner side of the impeller 6 in the wall portion 31 of the shroud casing 2A. Therefore, the inclination angle of the inclined wall portion 24 of the hub casing 2B can be formed more gently than the shroud casing 2A side, so that the flow of the main fluid that is blown out from the outlet 6B of the impeller 6 is not disturbed. The circulating flow can smoothly join the fluid main flow. Therefore, when the flow rate is small, the flow in the vaneless diffuser 12 can be kept smooth, and the turning stall occurrence point can be shifted to the small flow rate side.
  • the first wall portion 22 of the hub casing 2B protrudes toward the wall portion 31 side of the shroud casing 2A from the hub side extension line HA extending radially outward from the air outlet 6B of the impeller 6; Since the hub-side protruding length HD from the hub-side extension line HA to the first wall portion 22 is 50% or less of the width W of the air outlet 6B of the impeller 6, the centrifugal stall generation point is shifted to the small flow rate side while centrifugal A decrease in the efficiency of the compressor 1 can be suppressed.
  • the wall portion 31 of the shroud casing 2A protrudes toward the first wall portion 22 side of the hub casing 2B from the shroud side extension line SA extending radially outward from the blower outlet 6B of the impeller 6; Since the shroud side protrusion length SD from the shroud side extension line SA to the wall portion 31 is 20% or less of the outlet width W of the impeller 6, the effect of shifting the turning stall occurrence point to the small flow rate side is exhibited.
  • FIG. 5 is a cross-sectional view of a main part showing a configuration in the vicinity of a vaneless diffuser according to another embodiment.
  • the same components as those of the above-described embodiment are denoted by the same reference numerals and description thereof is omitted.
  • both the wall portion 31 of the shroud casing 2A and the first wall portion 22 of the hub casing 2B are configured to extend within the projection plane of the air outlet 6B of the impeller 6, but the shroud casing 2A It is good also as a structure which arrange
  • the impeller 6 and the vaneless diffuser 12 are provided in the two-stage centrifugal compressor 1, but if the compressor includes the impeller and the vaneless diffuser, a single-stage centrifugal It is applicable to a compressor and a multistage centrifugal compressor having three or more stages.
  • the wall portion 31 of the shroud casing 2A is connected to the horizontal wall 30 via the connecting wall 32 formed with a predetermined radius of curvature.
  • An inclined wall that extends from the front end of the horizontal wall 30 toward the end portion 31 ⁇ / b> A of the wall portion 31 may be employed.
  • the end portion 31 ⁇ / b> A on the inner side in the radial direction of the impeller 6 in the wall portion 31 serves as a connection portion with the connection wall 32.

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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Abstract

L'invention vise à réduire le débit d'écoulement de début de calage de rotation. A cet effet, l'invention porte sur un compresseur centrifuge, qui comprend : un diffuseur sans aubes (12) disposé sur un côté de sortie de refoulement (6B) d'une hélice (6) ; et une trajectoire d'écoulement de circulation de fluide (21) ayant une entrée (21A) qui s'ouvre dans une première section paroi (22) d'un carter de moyeu (2B) constituant le diffuseur sans aubes (12), et ayant également une sortie (21B) qui s'ouvre dans une seconde partie paroi (23) du carter de moyeu (2B) faisant face à une surface arrière de disque de moyeu (6C) dans l'hélice (6). En résultat de la saillie de la première section paroi (22) sur le côté de section paroi (31) du carter de carénage (2A), la largeur de trajectoire d'écoulement (D) du diffuseur sans aubes (12) est inférieure à la largeur (W) de la sortie de refoulement (6B) dans l'hélice (6). De plus, le carter de moyeu (2B) comprend une section paroi inclinée (24) ayant une extrémité saillante (24A) entre la sortie de refoulement (6B) de l'hélice (6) et l'entrée du diffuseur sans aubes (12), ladite section paroi inclinée (24) reliant la seconde section paroi (23) et la première section paroi (22).
PCT/JP2015/059343 2014-09-18 2015-03-26 Compresseur centrifuge WO2016042817A1 (fr)

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US15/511,593 US20170261001A1 (en) 2014-09-18 2015-03-26 Centrifugal compressor

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JP2014-190467 2014-09-18
JP2014190467A JP6242775B2 (ja) 2014-09-18 2014-09-18 遠心圧縮機

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WO2016042817A1 true WO2016042817A1 (fr) 2016-03-24

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