EP2078866A1 - Diffuseur variable et compresseur - Google Patents

Diffuseur variable et compresseur Download PDF

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Publication number
EP2078866A1
EP2078866A1 EP07708290A EP07708290A EP2078866A1 EP 2078866 A1 EP2078866 A1 EP 2078866A1 EP 07708290 A EP07708290 A EP 07708290A EP 07708290 A EP07708290 A EP 07708290A EP 2078866 A1 EP2078866 A1 EP 2078866A1
Authority
EP
European Patent Office
Prior art keywords
diffuser
vanes
vane
wall member
fixed
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Withdrawn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
EP07708290A
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German (de)
English (en)
Inventor
Hirotaka Higashimori
Isao Tomita
Takashi Shiraishi
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
Original Assignee
Mitsubishi Heavy Industries Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Publication of EP2078866A1 publication Critical patent/EP2078866A1/fr
Withdrawn legal-status Critical Current

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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
    • F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/462—Fluid-guiding means, e.g. diffusers adjustable 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
    • F04D23/00—Other rotary non-positive-displacement 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
    • F04D29/40—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
    • F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/462—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps
    • F04D29/464—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps adjusting flow cross-section, otherwise than by using adjustable stator blades
    • 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
    • F05D2210/00—Working fluids
    • F05D2210/10—Kind or type
    • F05D2210/12—Kind or type gaseous, i.e. compressible
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S415/00—Rotary kinetic fluid motors or pumps
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

Definitions

  • the present invention relates to a variable diffuser applied to, for example, centrifugal compressors and mixed flow compressors, and a compressor furnished with this variable diffuser.
  • FIG. 17 is a cross-sectional view showing the main parts of a conventional centrifugal compressor.
  • the centrifugal compressor 10 shown in the drawing compresses fluids, such as gas and air introduced from the exterior of a housing 11, by means of the rotation of an impeller 13, which is provided with a plurality of vanes 12, within the housing 11.
  • the flow of the fluid (air flow), which is formed in this manner, is delivered to the exterior through an impeller exit (hereunder also referred to as the "diffuser entrance") 14 that becomes the outer peripheral end of the impeller 13, a diffuser 15, and a scroll (omitted from the drawing).
  • Reference symbol 16 in the figure is a shaft axis about which the impeller 13 rotates.
  • the diffuser 15 mentioned above is an air flow passage provided between the impeller exit 14 and the scroll, and has a function of restoring static pressure from dynamic pressure by decelerating the air flow that is discharged from the impeller exit 14.
  • This diffuser 15 is normally formed by a pair of opposing walls, and in the explanation below, one wall amongst the opposing pair is referred to as a shroud side wall 17, and the other is referred to as a hub side wall 18.
  • examples of the diffuser 15 mentioned above include a vaned diffuser furnished with a diffuser vane (hereunder referred to as a "vane") 19 such as is shown in FIG. 18 , and a vaneless diffuser that does not have a vane 19.
  • a common centrifugal compressor that is furnished with a vaned diffuser employs a fixed vane diffuser in which the vane 19 is immovable.
  • a variable diffuser in which the vane leading edge angle ⁇ k shown in FIG. 20 (hereunder referred to as "vane angle ⁇ k") can be varied by making the vane 19 movable, is employed.
  • a general construction of the variable diffuser is, for example, as shown in FIG. 18 , one that varies the vane angle ⁇ k by providing a pivot shaft 20 to the vane 19, and supporting the vane 19 on the shroud side wall 17 and the hub side wall 18, as well as rotating the vane 19 about this pivot shaft 20.
  • a drive unit in which the angle of a plurality of diffuser vanes is variable by a simple construction has been proposed.
  • This drive unit is furnished with a large gear that rotates by means of an actuator, and the like, and a plurality of gears that engage the large gear, and the angle is varied by turning the diffuser vanes that are connected to the gears.
  • a centrifugal compressor that is furnished with a vaned diffuser provision of a second stationary vane that is freely rotatable with an object of expanding the operation on the small flow rate side has been proposed.
  • Patent Documents 2 and 3 for example, refer to Patent Documents 2 and 3
  • the vane 19 of the variable diffuser in a case where the vane shape of the vane is designed, it is given a shape such that the flow rate is in the middle of a desired flow rate variation range. Accordingly, in conventional variable diffusers in which the vane 19 is turned about the pivot shaft 20 and the vane angle ⁇ k is variable, variations in the characteristics occur as shown in FIG. 19 . That is to say, the flow rate range, which is prescribed by the surge flow rate Qs and the choke flow rate Qc, for example as shown in FIG.
  • the flow angle ⁇ and the vane angle ⁇ k of the vane 19 take variations of respectively different inclinations. Consequently, since the incidence (In) in the small flow rate region and the large flow rate region becomes large, there is a problem in that the efficiency decreases due to an increase in losses.
  • the incidence is a value that is defined by the difference between the vane leading edge angle ⁇ k and the flow angle ⁇ .
  • a space ⁇ (refer to FIG.
  • variable diffusers have a problem in the efficiency decreasing due to increases in the incidence and leaks from the space ⁇ , it is desired for these problems to be solved and to further improve the efficiency.
  • the present invention has been achieved taking the above circumstances into account, with an object thereof in providing a variable diffuser in which the efficiency can be further improved, and a compressor furnished with this variable diffuser.
  • variable diffuser is one which in a variable diffuser in which a diffuser passage, which restores a static pressure from a dynamic pressure by decelerating an air flow that is discharged from an outer peripheral end of an impeller that rotates within a housing, is formed between a hub side wall and a shroud side wall, and diffuser vanes are provided in the diffuser passage, is characterized in that said diffuser vanes are alternately fixed in the circumferential direction to a wall member that forms the hub side wall and the shroud side wall, and there is provided a driving device that turns either one of the wall members about the same axis as the rotation of the impeller.
  • the throat area can be varied without changing the vane leading edge angle.
  • the space 5 formed between the diffuser vane and the hub side wall and the shroud side wall decreases since it becomes either one of the faces.
  • a movable range of the wall member which turns as a result of the driving device to be set such that it encompasses the entire width of an interval between adjacent diffuser vanes that are fixed on the wall member of the fixed side.
  • a leading edge radius (R1) of a diffuser vane provided on a turning side of the wall member it is preferable for a leading edge radius (R1) of a diffuser vane provided on a turning side of the wall member to be set larger than a leading edge radius (R2) of a diffuser vane provided on a fixed side of the wall member (R1 > R2).
  • a vane leading edge angle ( ⁇ k1) of a diffuser vane provided on a turning side of the wall member is set smaller than a leading edge angle ( ⁇ k2) of a diffuser vane provided on a fixed side of the wall member at the same radial position ( ⁇ k1 ⁇ ⁇ k2).
  • a vane leading edge angle ( ⁇ k1) of a diffuser vane provided on a turning side of the wall member is set larger than a leading edge angle ( ⁇ k2) of a diffuser vane provided on a fixed side of the wall member at the same radial position ( ⁇ k1 > ⁇ k2).
  • a diffuser vane provided on a fixed side of the wall member it is preferable for a diffuser vane provided on a fixed side of the wall member to be a low chord-pitch ratio vane.
  • a trailing edge radius (R3) of a diffuser vane provided on a turning side of the wall member it is preferable for a trailing edge radius (R3) of a diffuser vane provided on a turning side of the wall member to be set larger than a trailing edge radius (R4) of a diffuser vane provided on a fixed side of the wall member (R3 > R4).
  • the setting of the fixed side and the turning side may be reversed. That is to say, the entrance radius (R2) of the diffuser vane provided on the fixed side of the wall member may be set larger than the entrance radius (R1) of the diffuser vane provided on the turning side of the wall member (R2 > R1). Furthermore, the vane leading edge angle ( ⁇ k2) of the diffuser vane provided on the fixed side of the wall member may be set smaller than the leading edge angle ( ⁇ k1) of the diffuser vane provided on the turning side of the wall member at the same radial position ( ⁇ k2 ⁇ ⁇ k1). Furthermore, the diffuser vane provided on the turning side of the wall member may be made a low chord-pitch ratio vane. Furthermore, the trailing edge radius (R4) of the diffuser vane provided on the fixed side of the wall member may be set larger than the trailing edge radius (R3) of the diffuser vane provided on the turning side of the wall member (R4 > R3).
  • the driving device prefferably be furnished with a sliding mechanism section that moves a turning side of the wall member back and forth between a space formation position and a space reduction position with respect to a fixed side of the wall member.
  • the compressor according to the present invention comprises a variable diffuser according to any of claim 1 to claim 9 on the peripheral end of the impeller that rotates within the housing.
  • the throat area can be varied without changing the leading edge angle of the movable side, efficiency decreases resulting from increases in the incidence can be resolved, and accordingly, a variable diffuser with further improved efficiency and a compressor furnished with this variable diffuser can be provided. Furthermore, since the space ⁇ formed between the diffuser vane and the hub side wall and the shroud side wall becomes only one of the faces and decreases, it becomes possible to resolve efficiency decreases resulting from leaks from the space ⁇ .
  • variable diffuser and a compressor according to the present invention is described with reference to the drawings.
  • variable diffuser 30 shown in FIG. 1 restores a static pressure from a dynamic pressure by decelerating the air flow that is discharged from the peripheral end of an impeller that rotates within the housing of a centrifugal compressor, a mixed flow compressor, or the like.
  • this variable diffuser 30 as well as a diffuser passage 33 being formed between the opposing shroud side wall 31a and hub side wall 32a, movable diffuser vanes (hereunder called the "movable vanes”) 34 and fixed diffuser vanes (hereunder called the "fixed vanes”) 35 are provided within the diffuser passage 33.
  • the vanes are made movable by providing the shroud side wall 31a with the movable vanes 34, although they may be made movable by providing the hub side wall 32a with the movable vanes 34.
  • the movable vanes 34 are fixed on a movable circular plate (wall member) that forms the shroud side wall 31a, and the fixed vanes 35 are fixed on a fixed circular plate (wall member) 32 that forms the hub side wall 32a.
  • the movable vanes 34 and the fixed vanes 35 are made the same vane shape, and with respect to the shroud side wall 31a and the hub side wall 32a, a plurality (vane number N) of the same respective number is positioned in the circumferential direction at a predetermined pitch.
  • FIG. 1 (a) shows a state where the movable circular plate 31 and the fixed circular plate 32, which is an opposing pair, have been separated.
  • the movable circular plate 31 and the fixed circular plate 32 slide in the combination direction shown by the arrow in the drawing and are integrated, such that the movable vanes 34 of the shroud side wall 31a and the fixed vanes 35 of the hub side wall 32a become alternately positioned in a predetermined reference position in the circumferential direction at the same pitch. That is to say, in an assembled state in which the movable circular plate 31 and the fixed circular plate 32 have been integrated, the movable vanes 31 and the fixed vanes 32 are alternately arranged in a reference position in the circumferential direction at the same pitch.
  • the cross-sectional view of FIG. 1 (b) shows the A-A cross-section of FIG. 1 regarding a diffuser passage 33 that is formed by integrating the movable circular plate 31 and the fixed circular plate 32.
  • This driving device 40 is, for example, configured by a gear driving section 41 that is provided on the upper end section of the movable circular plate 31, and a sliding mechanism section 45 that is provided on the lower end section.
  • the turning range ⁇ in this case is, compared to the pitch at which the movable vanes 31 and the fixed vanes 32 are alternately arranged in the circumferential direction in the predetermined reference position mentioned above, essentially approximately doubled although a difference corresponding to the thickness of the vanes is generated. In other words, the movable range ⁇ becomes the entire width between adjacent fixed vanes 35.
  • the gear driving section 41 is a configuration in which a rack gear section 42 and a pinion gear 43 formed on the upper end face of the movable circular plate 31 are intermeshed.
  • the pinion gear 43 is connected to a drive source such as an electric motor (not shown in the drawing), and is turnable as necessary in the desired direction.
  • the sliding mechanism section 45 is a portion in which the movable circular plate 31 is connected with respect to the housing 11 such that it is slidable in the circumferential direction.
  • a convex-shaped guide rail 46 formed on the housing 11 and a concave groove section 47 formed on the lower end face of the movable circular plate 31 are engaged, and the movable circular plate 31 is configured such that it slides along the guide rail 46.
  • a leakage stopping measure (not shown in the drawing) is provided between the guide rail 46 and the concave groove section 47 in order to prevent leaking of the high pressure air flow, in which a static pressure has been restored at the exit of the diffuser passage 33, from the back face of the movable circular plate 31 to the entrance side of the diffuser passage 33.
  • the movable circular plate 31 is guided by the sliding mechanism section 45 and turned in the same axis as the rotation axis of the impeller gear driving section 41 as a result of the turning of the pinion gear 43, and therefore, it relatively moves with respect to an immobile fixed circular plate 32.
  • the movable vanes 34 which are integral with the movable circular plate 31, are moved from the reference position in both circumferential directions within the range of the movable range ⁇ . That is to say, the movable vanes 34 rotate towards the fixed vanes 35 on both adjacent sides by turning from the reference position where they are arranged at the same pitch, and as shown by the imaginary line in FIG.
  • FIG. 2 (a) shows a case where the movable vanes 34 are in the reference position.
  • the respective same number (N) are arranged in the circumferential direction at the same pitch.
  • the throats A11 and A12 which are formed between the movable vane 34 and the fixed vanes 35 that are adjacent on both sides become equal. Consequently, the throat area of the variable diffuser 30 becomes a value in which the number N of movable vanes 34 has been multiplied to the total value (A11 + A12) of the throats formed on both sides of the movable vanes 34.
  • FIG. 2 (b) shows a state where the movable vanes 34 are making contact with the pressure face of the fixed vanes 35.
  • the throat A11 becomes a maximum (A11max).
  • A11max the maximum throat becomes larger than the total value of the throats at the reference position mentioned above (A11max > A11 + A12), and the area of the throats increases by approximately 1.2 to 1.3 times.
  • the state in which the throat area becomes a maximum is referred to as the throat maximum position.
  • the movable vanes 34 have turned in the opposite direction from the reference position, since there is no change in that both vanes are making contact at some point, it becomes the same result.
  • Fig. 2 (c) shows a case where the movable vanes 34 are in an intermediate position between FIG. 2 (a) and FIG. 2 (b) .
  • the throat area in this case is an approximately intermediate value between the reference position and the throat maximum position. Accordingly, by turning the movable vanes 34 in a range within the movable range ⁇ , the throat area can be appropriately varied in a range between approximately 1.2 to 1.3 times the reference value.
  • the number of diffuser vanes which consists of the number of movable vanes 34 and fixed vanes 35, essentially changes such that it doubles from N vanes to 2N vanes. That is to say, in a case where N movable vanes 34 are installed to the movable circular plate 31, and N fixed vanes 35 are installed to the fixed circular plate 32, 2N diffuser vanes are present in a state where the movable vanes 34 and the fixed vanes 35 are mutually separated. However, in a state where the adjacent movable vanes 34 and fixed vanes 35 are mutually making contact, the air flow essentially flows between N diffuser vanes.
  • the flow rate of the compressor characteristic is varied. That is to say, since the throat area increases by approximately 1.2 to 1.3 times, it is possible to widen the flow rate range by varying the choke flow rate Qc shown in FIG. 19 by 20 to 30%.
  • the fixed vanes 35 and also the vane leading edge angle (vane angle) ⁇ of the movable vanes 34 are normally fixed, compared to a conventional variable diffuser in which the vane angle ⁇ varies as a result of the turning of the vane 19, as shown by the two-dot chain line in FIG. 21 , the change in the incidence is very small. Accordingly, since a compressor that is furnished with this variable diffuser 30 can reduce the increasing losses when the incidence becomes large, the efficiency can be improved over conventional technology. Furthermore, since one end of the movable vanes 34 and the fixed vanes 35 are fixed to a wall that forms the diffuser passage 33, a space ⁇ is consequently formed only in one of the vane width directions. Accordingly, compared to the conventional structure in which the vane 19 is turned, since the area of the space ⁇ can be reduced by half, the losses resulting from leakage of the air flow are reduced by half, and the efficiency can be improved.
  • the entrance radius R1 is set larger than the entrance radius R2 of the fixed vanes 35. That is to say, the entrance radius R1 of the movable vanes 34A is, in a case where the movable vanes 34A are in an intermediate position between the adjacent fixed vanes 35, set such that the leading edges of the movable vanes 34A are on the upstream side with respect to the throat A2 formed between the adjacent fixed vanes 35.
  • the throat area varies only within a range in which the leading edges of the movable vanes 34A are upstream with respect to the intersection point X between the throat A2 and the radius R1.
  • FIG. 3 (a) in a case where the movable vanes 34A are positioned approximately in the center of the fixed vanes 35, the throat area becomes a minimum.
  • FIG. 3 (b) in a case where the movable vanes 34A are positioned upstream of the throat A2, the total value of the throat A11 and the throat A12 (A11 + A12) gradually increases.
  • FIG. 3 (b) in a case where the movable vanes 34A are positioned approximately in the center of the fixed vanes 35, the throat area becomes a minimum.
  • FIG. 3 (b) in a case where the movable vanes 34A are positioned upstream of the throat A2, the total value of the throat A11 and the throat A12 (A11 + A12) gradually increases.
  • FIG. 3 (b) in a case where the movable vanes 34A are positioned approximately in the center of the fixed vanes 35, the throat area becomes a minimum.
  • FIG. 3 (b) in a case where the movable vanes
  • the vane ends of the movable vanes 34 and the fixed vanes 35 mutually overlap with a limited space, and it becomes a state where the vane thickness of the diffuser vane leading edges has become thick.
  • Such an increase in the vane thickness not only becomes a problem that increases the throat area to the maximum, but it also increases damage to the vane leading edges.
  • the leading edges of the movable vanes 34A are positioned downstream of the leading edges of the fixed vanes 35. Accordingly, compared to the state shown in FIG. 2 (b) , the sizes of the throat becomes A2 > A11max.
  • the vane leading edge angle (vane angle) ⁇ k1 is set smaller than the vane angle ⁇ k2 of the fixed vanes 35, and the movable vanes 34B are driven from the middle between the fixed vanes 35 towards the negative pressure faces of the fixed vanes 35. If made such a configuration, although the maximum value of the throat A12 becomes small compared to the throat A2, in a state where two vanes have been made to overlap, the average vane angle ⁇ k can be decreased.
  • the flow angle ⁇ at the maximum angle becomes smaller, and from the comparison between the solid line representation and the broken line representation, it can be understood that the performance when the flow rate is low has been improved. Furthermore, also at an intermediate angle, from the comparison between the solid line representation and the broken line representation, it can be understood that the performance at the time of a small flow rate when the flow angle ⁇ is small has been improved, though not as much as at the time of a maximum angle.
  • the vane leading edge angle (vane angle) ⁇ k1 is set larger than the vane angle ⁇ k2 of the fixed vanes 35 at the same radial position, and the movable vanes 34C are driven from the middle of the fixed vanes 35 towards the pressure face of the fixed vanes 35. If made such a configuration, in the same manner to the second embodiment mentioned above, in regard to the throat, A2 becomes a maximum value.
  • a fifth embodiment of the present invention is described based on FIG. 8 to FIG. 10 .
  • vaned diffusers those in which the shortest distance between adjacent vanes is not formed in the perpendicular direction from the vane negative pressure face, or in other words, those in which a throat is not formed, are generally distinguished by being called a "low chord-pitch ratio diffuser".
  • This low chord-pitch ratio diffuser has the following characteristics.
  • a vaneless diffuser since the surge flow rate Qs is small and the choke flow rate Qc is large, it has a characteristic in that although the flow rate range is wide, the efficiency is low.
  • the surge flow rate Qs since the surge flow rate Qs is large, and the choke flow rate Qc is only 10 to 20% larger than the surge flow rate Qs, it has a characteristic in that although the flow rate range is narrow, the efficiency is high.
  • the low chord-pitch ratio diffuser since a throat is not formed, the choke flow rate Qc becomes larger than in the vaned diffuser, and the surge flow rate Qs becomes larger than in the vaned diffuser.
  • the low chord-pitch ratio diffuser has a characteristic in that the efficiency becomes higher than the vaneless diffuser.
  • the movable vanes, in which a throat is not formed are called "low chord-pitch ratio vanes”.
  • FIG. 10 shows, as the characteristics of the diffuser, in regard to the vaned diffuser and the low chord-pitch ratio diffuser, the relationship between the pressure restoration factor and the number of vanes.
  • the vane leading edge of the movable vane 34D is set such that it becomes on the upstream side with respect to the imaginary throat A2 formed between adjacent fixed vanes 35.
  • the fixed vanes 35 are low chord-pitch ratio vanes in the same manner as the embodiment shown in FIG. 8 , and furthermore, the trailing edge radius R3 of the movable vanes 34E is set larger than the trailing edge radius R4 of the fixed vanes 35.
  • the following characteristics can be obtained. That is to say, as shown in FIG. 9 (a) , in a case where the movable vanes 34E and the fixed vanes 35 are separated and the number of vanes becomes 2N, since the vane area of the movable vanes 34E becomes larger than the low chord-pitch ratio diffuser, the pressure restoration factor rises.
  • the movable vanes 34E are in the position shown in FIG. 9 (b) , it exhibits wide-range characteristics in which a throat is not formed. Then, in a case where the movable vanes 34E are in the position shown in FIG. 9 (c) , a high pressure restoration factor is exhibited in the same manner as the normal vaned diffuser in which the number of vanes has been made N vanes.
  • FIG. 11 relates to the sliding mechanism section 45 of the driving device 40 that turns the movable circular plate 31, and in particular, relates to a suitable structure for reducing the space ⁇ between the wall of the fixed circular plate 32 and the movable vanes 34.
  • a driving device 40A shown in FIG. 11 is furnished with a sliding mechanism section 45A that is configured by a guiding groove 48 that is formed on the housing 11, and a convex section 49 that is provided on the lower end section of the movable circular plate 31.
  • a guiding face 48a On one side face of the guiding groove 48, a guiding face 48a, to which circular arc-shaped (radius R) concavities and convexities are formed, is provided.
  • a sliding face 49a On the convex section 49 side, with respect to the side face that opposes the guiding face 48a, a sliding face 49a to which the same circular arc-shaped (radius R) concavities and convexities are formed, is provided.
  • This sliding face 49a makes contact with the guiding face 48a, and as a result of the movable circular plate 31 turning, the circular arc-shaped concave and convex contact positions that are formed on both faces move in the circumferential direction.
  • a sealing member 50 that exhibits a sealing function by making contact with a face that becomes the outer circumferential side of the movable circular plate 31 viewed from the diffuser passage 33 side. This sealing member 50 prevents the air flow which flows through the diffuser passage 33, from passing through the sliding mechanism section 45A and leaking.
  • the movable circular plate 31 moves according to the concave and convex contact positions with the guiding face 48a and the sliding face 49a, in a direction that approaches or a direction that separates from the fixed circular plate 32, and the interfacial distance with the fixed circular plate 32 is varied.
  • this interfacial distance variation is specifically described with reference to FIG. 12 and FIG. 13 .
  • the space ⁇ formed between the end of the movable vanes 34 and the hub side wall 32a is, as shown in FIG. 13 , varied within a range from a maximum value at the space forming position (indicated by the chain in the drawing) to a minimum value at the space reduction position (indicated by the solid line in the drawing).
  • FIG. 12 (b) shows the change in the space ⁇ that corresponds to the movable range ⁇ of the movable circular plate 31.
  • the minimum space at the space reduction position can, by optimizing the concavities and convexities of the guiding face 48a and the concavities and convexities of the sliding face 49a, be made ⁇ ⁇ 0, which is equivalent to almost none. Consequently, at the space reduction position, since the leakage amount that passes through the space ⁇ decreases, the efficiency of the compressor furnished with the variable diffuser can be improved.
  • the sliding mechanism section 45A mentioned above it is preferable for the sliding mechanism section 45A mentioned above to utilize the space reduction position at which the concavities and convexities of the guiding face 48a and the concavities and convexities of the sliding face 49a engage, and for it to be turned in stages at the pitch of the concavities and the convexities. That is to say, since the position of the movable vanes 34 is fixed in stages, it becomes possible to prevent fluctuations of the vane position resulting from play in the driving device 40A and vibrations from the exterior, and the characteristics of the compressor can be stabilized.
  • a sliding face 51 is formed on the shroud side wall 31a, which becomes the interval between the movable vanes 34, and on the hub side wall 32a, which becomes the interval between the fixed vanes, in order to obtain satisfactory slidability even in a state where there is no space ⁇ .
  • the sliding face is formed by applying a fluororesin such as 4-fluoroethylene. In such a configuration, smooth turning of the movable circular plate 31 becomes possible even if there is no space ⁇ .
  • the guiding face 48a and the sliding face 49a were made a circular arc shape, although as in a first modified example shown in FIG. 15 , it is acceptable for it to be made a guiding face 48b and a sliding face 49b having mutually identical sine wave-shaped concavities and convexities.
  • a second modified example shown in FIG. 16 it may be made a configuration in which a guiding groove 48' is formed on the housing 11 which becomes the fixed side, and freely turning rotation rings 52 are installed in a necessary number at appropriate positions on this guiding groove 48'.
  • the circular arc-shaped or sine wave-shaped sliding face 49a slides with respect to the rotation rings 52. Therefore in the same manner as with the guiding faces 48a and 48b mentioned above, the space ⁇ can be eliminated at the space reduction position.
  • the setting of the fixed side and the turning side may be reversed. That is to say, the same respective operating effects can be obtained even if the magnitude of the entrance radius of the fixed vanes and the entrance radius of the movable vanes are reversed, or the magnitude of the vane leading edge angle of the fixed vanes and the vane leading edge angle of the movable vanes is reversed, or the vanes of the fixed vanes and the movable vanes that are made the low chord-pitch ratio vanes are reversed, and furthermore, if the magnitude of the trailing edge radius of the fixed vanes and the trailing edge radius of the movable vanes are reversed.
  • variable diffuser structure of the present invention efficiency decreases resulting from increases in the incidence, and leakage from the space ⁇ are resolved, and a variable diffuser, in which the efficiency is even more improved, can be provided. Accordingly, in regard to compressors such as centrifugal compressors and mixed flow compressors, that are furnished with this variable diffuser, the performance thereof can be even more improved.
  • compressors such as centrifugal compressors and mixed flow compressors, that are furnished with this variable diffuser, the performance thereof can be even more improved.
  • the present invention is in no way restricted to the embodiments mentioned above, and appropriate changes are possible within a range that does not depart from the gist of the present invention.
  • the diffuser and the compressor of the present invention is, for example, applicable to turbochargers, marine superchargers, aeronautical small gas turbines, and industrial centrifugal compressors and mixed flow compressors.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP07708290A 2006-10-30 2007-02-09 Diffuseur variable et compresseur Withdrawn EP2078866A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006294408A JP4795912B2 (ja) 2006-10-30 2006-10-30 可変ディフューザ及び圧縮機
PCT/JP2007/052354 WO2008053605A1 (fr) 2006-10-30 2007-02-09 Diffuseur variable et compresseur

Publications (1)

Publication Number Publication Date
EP2078866A1 true EP2078866A1 (fr) 2009-07-15

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EP07708290A Withdrawn EP2078866A1 (fr) 2006-10-30 2007-02-09 Diffuseur variable et compresseur

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US (1) US20100129204A1 (fr)
EP (1) EP2078866A1 (fr)
JP (1) JP4795912B2 (fr)
KR (1) KR20080059352A (fr)
CN (1) CN101326373A (fr)
WO (1) WO2008053605A1 (fr)

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EP2650547A1 (fr) * 2010-12-10 2013-10-16 Toyota Jidosha Kabushiki Kaisha Compresseur centrifuge
WO2017129342A1 (fr) * 2016-01-28 2017-08-03 Siemens Aktiengesellschaft Turbomachine à diffuseur à aubes

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JP5010722B2 (ja) * 2010-08-31 2012-08-29 三菱重工業株式会社 遠心圧縮機のディフューザおよびこれを備えた遠心圧縮機
KR101026990B1 (ko) 2010-12-23 2011-04-11 한국기계연구원 유량 조절형 터빈
CN102562674A (zh) * 2012-02-14 2012-07-11 大同北方天力增压技术有限公司 一种涡轮增压器可调叶片扩压器结构
US20130280060A1 (en) * 2012-04-23 2013-10-24 Shakeel Nasir Compressor diffuser having vanes with variable cross-sections
US10527059B2 (en) 2013-10-21 2020-01-07 Williams International Co., L.L.C. Turbomachine diffuser
EP3289202B1 (fr) * 2015-04-30 2024-01-03 Concepts NREC, LLC Canaux de diffuseur
JP6704843B2 (ja) * 2016-12-07 2020-06-03 三菱重工エンジン＆ターボチャージャ株式会社 遠心圧縮機及びターボチャージャ
JP6926550B2 (ja) * 2017-03-15 2021-08-25 株式会社Ihi 遠心圧縮機
JP7145588B2 (ja) * 2017-06-14 2022-10-03 日立グローバルライフソリューションズ株式会社 電動送風機及びそれを備えた電気掃除機
CN111373155B (zh) 2017-09-25 2022-09-02 江森自控科技公司 紧凑可变几何形状的扩散器机构
CN109723674B (zh) * 2019-01-24 2024-01-26 上海海事大学 一种用于压气机转子的可转动内端壁机匣
JP7258728B2 (ja) * 2019-11-19 2023-04-17 株式会社日立インダストリアルプロダクツ 遠心式流体機械
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EP2650547A4 (fr) * 2010-12-10 2014-04-23 Toyota Motor Co Ltd Compresseur centrifuge
WO2017129342A1 (fr) * 2016-01-28 2017-08-03 Siemens Aktiengesellschaft Turbomachine à diffuseur à aubes

Also Published As

Publication number Publication date
JP4795912B2 (ja) 2011-10-19
CN101326373A (zh) 2008-12-17
KR20080059352A (ko) 2008-06-27
JP2008111368A (ja) 2008-05-15
WO2008053605A1 (fr) 2008-05-08
US20100129204A1 (en) 2010-05-27

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