CN113586513A - High-efficiency long-flow-passage impeller low-specific-speed centrifugal pump - Google Patents

High-efficiency long-flow-passage impeller low-specific-speed centrifugal pump Download PDF

Info

Publication number
CN113586513A
CN113586513A CN202110837936.XA CN202110837936A CN113586513A CN 113586513 A CN113586513 A CN 113586513A CN 202110837936 A CN202110837936 A CN 202110837936A CN 113586513 A CN113586513 A CN 113586513A
Authority
CN
China
Prior art keywords
impeller
centrifugal pump
cover plate
inducer
long
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.)
Pending
Application number
CN202110837936.XA
Other languages
Chinese (zh)
Inventor
卜学兵
王越
孙中国
席光
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.)
Xian Jiaotong University
Original Assignee
Xian Jiaotong University
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 Xian Jiaotong University filed Critical Xian Jiaotong University
Priority to CN202110837936.XA priority Critical patent/CN113586513A/en
Publication of CN113586513A publication Critical patent/CN113586513A/en
Pending legal-status Critical Current

Links

Images

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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2238—Special flow patterns
    • 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
    • F04D29/06—Lubrication
    • F04D29/061—Lubrication especially adapted for liquid 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
    • F04D29/08—Sealings
    • F04D29/086—Sealings especially adapted for liquid 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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/24—Vanes
    • F04D29/242—Geometry, shape
    • 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
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid 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
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F04D29/4293—Details of fluid inlet or outlet

Landscapes

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

Abstract

The invention discloses a high-efficiency long-flow-passage impeller low-specific-speed centrifugal pump which comprises a centrifugal impeller, an inducer, a transmission shaft, a centrifugal pump shell and a sealing structure, wherein the inducer is arranged in the centrifugal impeller; the centrifugal impeller and the inducer are in rigid connection and are coaxially arranged with the transmission shaft; the centrifugal impeller comprises a front cover plate and a rear cover plate which adopt single arc transition; the sealing structures are respectively arranged on the outer side of the front cover plate and the outer side of the rear cover plate. The invention properly prolongs the axial length, ensures that the angle distribution of the blades of the centrifugal impeller is smoother, reduces the impact loss of the inlet of the centrifugal impeller, obviously improves the working efficiency of the low specific speed centrifugal pump, and solves the problem of low efficiency of the low specific speed centrifugal pump due to the long and narrow characteristic of the impeller flow channel of the low specific speed centrifugal pump, which causes large friction loss of the impeller disc and large impact loss of the inlet.

Description

High-efficiency long-flow-passage impeller low-specific-speed centrifugal pump
Technical Field
The invention belongs to the field of turbo pumps, and particularly relates to a high-efficiency long-flow-passage impeller low-specific-speed centrifugal pump.
Background
The liquid rocket engine turbo pump adopts a gas turbine to drive an oxidizer pump and a fuel pump to pressurize and convey a propellant, and the efficiency of the oxidizer pump and the fuel pump is improved as a main means for improving the specific impulse performance of the engine; the fuel pump is usually a low specific speed centrifugal pump, the working speed reaches tens of thousands of revolutions per minute, however, the impeller disc friction loss and the inlet impact loss of the low specific speed centrifugal pump are large due to the long and narrow characteristic of an impeller flow channel of the low specific speed centrifugal pump, and the efficiency of the low specific speed centrifugal pump is low; meanwhile, the industries such as aviation ships and petrochemical equipment generally adopt low specific speed centrifugal pumps to finish low-flow medium high-pressure conveying. Therefore, the structure improvement and the efficiency optimization are carried out aiming at the centrifugal pump with low specific speed, and the centrifugal pump has important value for improving the product performance and the overall system performance.
Disclosure of Invention
The invention aims to solve the problems in the prior art and provides a high-efficiency long-flow-passage impeller low-specific-speed centrifugal pump.
In order to achieve the purpose, the invention adopts the following technical scheme to realize the purpose:
a high-efficiency long-flow-passage impeller low-specific-speed centrifugal pump comprises a centrifugal impeller, an inducer, a transmission shaft and a sealing structure;
the centrifugal impeller and the inducer are in rigid connection, and are coaxially arranged with the transmission shaft;
the centrifugal impeller comprises a front cover plate and a rear cover plate which adopt single arc transition;
the sealing structures are respectively arranged on the outer side of the front cover plate and the outer side of the rear cover plate.
The invention is further improved in that:
the centrifugal impeller is provided with a plurality of long blades and short blades, the inlet end of each short blade deflects to the pressure surface of the adjacent long blade, and the outlet end of each short blade deflects to the suction surface of the adjacent long blade.
The front cover plate and the rear cover plate are inclined, and the inclination angle of the front cover plate is 2 times of that of the rear cover plate.
A plurality of balance holes are arranged among the plurality of long blades and are circumferentially distributed at positions close to the suction surfaces of the long blades.
The outer side of the front cover plate is provided with a front cover plate sealing surface, and the outer side of the rear cover plate is provided with a rear cover plate sealing surface.
The sealing structure comprises a sealing static ring and a floating ring, and the floating ring is arranged on the outer side of the sealing surface of the front cover plate; the sealing static ring is arranged on the outer side of the sealing surface of the rear cover plate.
The sealing static ring is arranged on the sealing static ring base, and labyrinth seals are further arranged on the outer side of the sealing static ring.
And the sealing surface of the front cover plate is sprayed with a diamond-like carbon or chromium-based wear-resistant self-lubricating coating.
The centrifugal impeller is of a closed straight blade structure; the inducer adopts an equal-pitch inlet section with blade inlet cascade cavitation erosion number and a variable-pitch outlet section with gradually-increased rim blade angle; the wrapping angle ratio of the inducer equal-pitch inlet section is 0.3.
The outer side of the centrifugal impeller is also provided with a volute, and the volute is a rectangular volute.
Compared with the prior art, the invention has the following beneficial effects:
the high-efficiency long-flow-channel impeller low-specific-speed centrifugal pump is adopted, the centrifugal impeller and the inducer are connected through the rectangular spline and coaxially work, the phase angles of the rectangular spline on the centrifugal impeller and the inducer and the structures of the centrifugal impeller and the inducer are controlled in a quantized mode, the inlet edge of the centrifugal impeller and the inlet edge of the inducer are guaranteed to be in the optimal phase angle, the long-flow-channel single-arc transitional front cover plate and the long-flow-channel single-arc transitional rear cover plate are adopted, the over-transition radius of the front cover plate and the over-transition radius of the rear cover plate are adjusted and increased, the axial length is properly expanded, the blade angle distribution of the centrifugal impeller is guaranteed to be smoother, the impact loss of the inlet of the centrifugal impeller is reduced, and the working efficiency of the low-specific-speed centrifugal pump is obviously improved. Furthermore, both the front cover plate and the rear cover plate have inclination angles, and the streamline inclination angle of the front cover plate is 2 times of that of the rear cover plate, so that the flow area of the centrifugal impeller is ensured to be uniformly changed.
Furthermore, the centrifugal impeller of the high-efficiency long-flow-channel low-specific-speed centrifugal pump adopts long and short composite blades, the short blades are uniformly arranged among the long-blade flow channels at intervals, meanwhile, the inlet end of each short blade deflects to the pressure surface of the adjacent long blade, and the outlet end of each short blade deflects to the suction surface of the adjacent long blade on the other side, so that the flow balanced distribution principle of the blades during working is met, the typical wake-jet phenomenon of the centrifugal impeller with the low specific speed is weakened, the flow field distribution in the flow channel of the centrifugal impeller is ensured to be more uniform, and the pressure pulsation of the flow field is reduced.
Furthermore, balance holes are additionally arranged between adjacent long blades of the centrifugal impeller, are uniformly distributed in the circumferential direction and are biased to be close to the suction surface of the long blades, high-pressure backflow of the balance holes is guided to the suction surface of the long blades, the low-pressure area of the suction surface of the blades is reduced, and the flow field distribution of the inlet area of the centrifugal impeller is optimized and improved.
Furthermore, the centrifugal impeller is of a closed straight blade structure, the induction wheel is in a conical hub cylindrical blade tip induction wheel in a structural form, the induction wheel is of a combined structure of a uniform-pitch inlet section and a variable-pitch outlet section, the phase angle between the inlet edge of the centrifugal impeller and a rectangular spline on the structure of the centrifugal impeller can be controlled in a quantized mode, the phase angle between the induction wheel and the rectangular spline on the structure of the induction wheel can be controlled in a quantized mode, the inlet edge of the centrifugal impeller and the outlet edge of the induction wheel are guaranteed to be in the optimal phase angle, and the inlet pressure of the centrifugal impeller is guaranteed to meet working requirements while cavitation resistance of the induction wheel is improved; meanwhile, the axial distance of the structure type is short, the whole structure of the product is compact, the operation is efficient, and the economical efficiency and the reliability of the product are obviously improved.
Furthermore, the centrifugal pump volute is a rectangular volute obtained by machining, so that the size precision and the surface roughness of the inner wall surface of the volute can meet the design requirements, the friction loss of the volute is reduced, and the product performance dispersion difference of batches is reduced.
Drawings
In order to more clearly explain the technical solutions of the embodiments of the present invention, the drawings needed to be used in the embodiments will be briefly described below, it should be understood that the following drawings only illustrate some embodiments of the present invention, and therefore should not be considered as limiting the scope, and for those skilled in the art, other related drawings can be obtained according to the drawings without inventive efforts.
FIG. 1 is a schematic structural view of a high efficiency long flow path centrifugal impeller low specific speed centrifugal pump of the present invention;
FIG. 2 is a schematic structural view of a centrifugal impeller and an inducer according to the present invention;
FIG. 3 is a perspective view of the centrifugal impeller and inducer axis of the present invention;
FIG. 4 is a cross-sectional view of a centrifugal impeller flow channel in an embodiment of the present invention;
FIG. 5 is a diagram showing a structure of a comparative example of a centrifugal impeller according to an embodiment of the present invention;
FIG. 6 is a graph comparing performance curves of centrifugal pumps in embodiments of the present invention.
Wherein: 1-centrifugal impeller; 2-inducer; 3, driving a shaft; 4-sealing the static ring; 5-sealing the static ring base; 6-floating ring baffle; 7-a floating ring; 8-a limit nut; 9-a centrifugal pump housing; 10-shaft sleeve; 11-an oxidant pump housing; 12-labyrinth seal; 13-a gasket; 14-a fastening screw; 15-a return conduit; 16-a support bearing; 101-a front cover plate; 102-a rear cover plate; 103-long leaf; 104-short leaf; 105-a balancing hole; 106-centrifugal impeller drive splines; 107-front cover plate sealing face; 108 — back cover plate sealing face; 201-inducer blade; 202-inducer drive splines; 901-volute.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are some, but not all, embodiments of the present invention. The components of embodiments of the present invention generally described and illustrated in the figures herein may be arranged and designed in a wide variety of different configurations.
Thus, the following detailed description of the embodiments of the present invention, presented in the figures, is not intended to limit the scope of the invention, as claimed, but is merely representative of selected embodiments of the invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
It should be noted that: like reference numbers and letters refer to like items in the following figures, and thus, once an item is defined in one figure, it need not be further defined and explained in subsequent figures.
In the description of the embodiments of the present invention, it should be noted that if the terms "upper", "lower", "horizontal", "inner", etc. are used for indicating the orientation or positional relationship based on the orientation or positional relationship shown in the drawings or the orientation or positional relationship which is usually arranged when the product of the present invention is used, the description is merely for convenience and simplicity, and the indication or suggestion that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and thus, cannot be understood as limiting the present invention. Furthermore, the terms "first," "second," and the like are used merely to distinguish one description from another, and are not to be construed as indicating or implying relative importance.
Furthermore, the term "horizontal", if present, does not mean that the component is required to be absolutely horizontal, but may be slightly inclined. For example, "horizontal" merely means that the direction is more horizontal than "vertical" and does not mean that the structure must be perfectly horizontal, but may be slightly inclined.
In the description of the embodiments of the present invention, it should be further noted that unless otherwise explicitly stated or limited, the terms "disposed," "mounted," "connected," and "connected" should be interpreted broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
The invention is described in further detail below with reference to the accompanying drawings:
referring to fig. 1-4, a high-efficiency long-flow-passage impeller low-specific-speed centrifugal pump comprises a centrifugal impeller 1, an inducer 2, a transmission shaft 3, a centrifugal pump shell 9 and a sealing structure; the centrifugal impeller 1 and the inducer 2 are connected through a transmission spline and transmit torque, and the centrifugal impeller 1 and the inducer 2 are coaxially arranged with the transmission shaft 3; the centrifugal impeller 1 comprises a front cover plate 101 and a rear cover plate 102 which adopt long-flow-channel single-arc transition, and the transition radius of the front cover plate 101 and the rear cover plate 102 is adjusted and increased; the sealing structures are provided on the outer sides of the front cover plate 101 and the rear cover plate 102, respectively. The centrifugal impeller 1 is provided with a plurality of long blades 103 and short blades 104, the inlet end of each short blade 104 is deviated to the pressure surface of the adjacent long blade 103, and the outlet end of each short blade 104 is deviated to the suction surface of the adjacent long blade 103. Both the front cover plate 101 and the rear cover plate 102 have inclination angles, and the inclination angle of the front cover plate 101 is 2 times the inclination angle of the rear cover plate 102. A plurality of balance holes 105 are formed among the plurality of long blades 103, and the balance holes 105 are circumferentially distributed at positions close to the suction surfaces of the long blades 103. A front cover sealing surface 107 is provided on the outer side of the front cover 101, and a rear cover sealing surface 108 is provided on the outer side of the rear cover 102. The sealing structure comprises a sealing static ring 4 and a floating ring 7, wherein the floating ring 7 is arranged on the outer side of the front cover plate sealing surface 107; the stationary seal ring 4 is disposed outboard of the rear cover plate sealing surface 108. The static sealing ring 4 is arranged on the static sealing ring base 5, and a labyrinth seal 12 is further arranged on the outer side of the static sealing ring 4. The front cover plate sealing surface 107 is sprayed with a diamond-like carbon or chromium-based wear-resistant self-lubricating coating. The inducer 2 adopts an equal-pitch inlet section with smaller blade inlet cascade cavitation number and a variable-pitch outlet section with gradually-increased rim blade angle; the wrapping angle ratio of the equal-pitch inlet section of the inducer 2 is 0.3. The volute 901 of the centrifugal pump housing 9 is of the rectangular volute type, the volute 901 being disposed outside the centrifugal impeller 1.
The working principle of the invention is as follows:
referring to fig. 1, a specific embodiment of the high-efficiency long-flow-channel impeller low specific speed centrifugal pump provided by the present invention is described by taking a fuel pump in a turbo pump of a liquid rocket engine as an example, where the low specific speed centrifugal pump includes a centrifugal impeller 1 and an inducer 2 with optimized and improved structures, the centrifugal impeller 1 and the inducer 2 transmit torque through a rectangular spline, the centrifugal impeller 1 and the inducer 2 are mounted on a transmission shaft 3 to coaxially work, a back pump cavity of the centrifugal impeller 1 realizes gap sealing through a sealing stationary ring 4, and discharges to an external space after passing through a labyrinth seal 12 again, and the labyrinth seal 12 is mounted on an oxidant pump housing 11 through a fastening screw 14; the pump end supporting bearing 16 is lubricated and cooled by a medium provided by a backflow guide pipe 15 after the gap of a pump cavity of the centrifugal impeller 1 is sealed and decompressed, and then the medium flows back to the inlet of the inducer 2 through a gap formed between the shaft sleeve 10 and the centrifugal pump shell 9; the front pump cavity of the centrifugal impeller 1 is sealed by a floating ring 7, and after sealing, leakage media flow back to the inlet of the centrifugal impeller 1 through the tail edge of the inducer 2; the sealing static ring 4 is arranged on the sealing static ring base 5 and is screwed and fixed on the oxidant pump shell 11 in a thread form, the floating ring 5 is tightly locked on the end surface of the floating ring baffle 6 when in work, and the floating ring baffle 6 is fixed on the matching surface of the centrifugal pump shell 9 by adopting a limit nut 8; the oxidant pump shell 11 and the centrifugal pump shell 9 are statically sealed by a sealing gasket 13.
The volute 901 on the centrifugal pump shell 9 is a rectangular volute, the dimensional accuracy and the surface roughness of the volute 901 are ensured by adopting machining means, and the surface roughness of a flow channel in the volute 901 is not more than Ra3.2.
Referring to fig. 2-3, the centrifugal impeller 1 is of a closed straight blade structure, the inducer 2 is of a conical hub cylindrical blade tip inducer structure, the phase angle between the inlet edge of the long blade 103 on the centrifugal impeller 1 and the rectangular spline 106 of the centrifugal impeller 1 on the structure of the centrifugal impeller is controlled quantitatively, and the phase angle between the inducer blade 201 on the inducer 2 and the rectangular spline 202 of the inducer 2 on the structure of the inducer is controlled quantitatively, so that the inlet edge of the centrifugal impeller 1 and the outlet edge of the inducer 2 are in the optimal phase angle. The centrifugal impeller 1 is a long-runner centrifugal impeller, wherein the streamline of the front cover plate 101 and the streamline of the rear cover plate 102 both adopt a long-runner single-arc transition design, the long-and-narrow runner characteristic of the conventional impeller with low specific speed is distinguished, the axial length of the centrifugal impeller 1 is properly extended, the transition radius R1 of the front cover plate 101 of the centrifugal impeller and the transition radius R2 of the rear cover plate of the centrifugal impeller are adjusted and increased, and the angular distribution of blades of the centrifugal impeller is ensured to be smoother.
The inclination angle of the front cover plate 101 of the centrifugal impeller 1 is alpha1nThe back cover plate 102 has an inclination angle α2nAnd α1n≈2α2nThe uniform change of the flow area of the centrifugal impeller 1 is ensured, and the axial plane projection structure of the long-flow-channel centrifugal impeller 1 has the characteristic similar to that of an oblique flow blade of a conventional mixed flow pump model. See fig. 1, bThe leakage sealing structure at the position of the front cover plate 101 of the central impeller 1 is sealed by adopting a floating ring seal 7, wherein a sealing surface 107 of the front cover plate 101 of the central impeller 1 is sprayed with a diamond-like carbon or chromium-based wear-resistant self-lubricating coating, so that the unilateral radial clearance between the floating ring 7 and the sealing surface 107 of the front cover plate is ensured to be 0.15-0.2 mm; a rear cover plate sealing surface 108 at the position of a rear cover plate 102 of the centrifugal impeller 1 and the sealing static ring 4 form clearance sealing, and the unilateral radial clearance is adjusted and guaranteed to be 0.12-0.16 mm.
The inducer 2 adopts an equal-pitch inlet section with a smaller blade inlet cascade cavitation number and a variable-pitch outlet section with a rim blade angle gradually changing, wherein the wrap angle proportion of the equal-pitch inlet section of the inducer 2 is 0.28, and the blade number Z of the inducer 2 is 3.
Referring to fig. 4, the centrifugal impeller 1 is of a long and short composite blade structure, the number of the long blades 103 is 6, the number of the short blades 104 is 6, the short blades 104 are uniformly arranged between the flow channels of the long blades 103 at intervals, meanwhile, the inlet ends of the short blades 104 are biased to the pressure surfaces of the adjacent long blades 104, and the outlet ends of the short blades 104 are biased to the suction surfaces of the adjacent long blades 103 on the other side. Balance holes 105 are additionally arranged between adjacent long blades of the centrifugal impeller 1, and the balance holes 105 are uniformly distributed in the circumferential direction and are offset to the positions close to the suction surfaces of the long blades 103.
The embodiment is further explained by combining a certain type of liquid oxygen kerosene engine turbine pump, the fuel delivered by the turbine pump is kerosene, the specific speed of the design working condition is 56, and the rated speed is 32000 r/min. Referring to fig. 3 and 5, the design of a two-pass centrifugal impeller 1 and an inducer 2 is completed, wherein the inducer 2 is designed according to a combination mode of a uniform pitch inlet section and a variable pitch outlet section, the structural parameters are completely consistent, the centrifugal impeller 1 in fig. 5 is an impeller axial plane projection obtained according to a conventional design method of a low specific speed centrifugal pump, and the centrifugal impeller 1 in fig. 3 is a novel centrifugal impeller with a lengthened flow passage and increased transition radius. Structural parameter D of centrifugal impeller 1 in FIG. 31n:D4n、L1n:L3n、L5n:L6n、B1n、b2n、α1nAnd alpha2nStructural parameter D of centrifugal impeller 1 in FIG. 51m:D4m、L1m:L3m、L5m:L6m、B1m、b2m、α1mAnd alpha2mAre all the same, wherein the centrifugal impeller 1 has an outer diameter D3m＝D3n＝116(mm)，α1m＝α1n＝16°，α2m＝α2n8 degrees; the structural parameter R shown in FIG. 31n＝18mm、R2n27mm and L4n43mm, structural parameter R shown in FIG. 51m＝8mm、R2m＝21mm、L4m＝37mm。
Referring to fig. 6, the working efficiency of the conventional prototype pump and the long-runner impeller centrifugal pump is analyzed, and the efficiency of the fuel pump adopting the lengthened runner design under the design working condition is 61.7%, the efficiency of the conventional prototype pump under the design working condition is 58.5%, and the efficiency is improved by 3.2%; meanwhile, the efficiency of the fuel pump with improved design is improved to different degrees in the full flow range besides the working condition with small flow.
The above is only a preferred embodiment of the present invention, and is not intended to limit the present invention, and various modifications and changes will occur to those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims (10)

1. A high-efficiency long-flow-passage impeller low-specific-speed centrifugal pump is characterized by comprising a centrifugal impeller (1), an inducer (2), a transmission shaft (3) and a sealing structure;
the centrifugal impeller (1) and the inducer (2) are rigidly connected, and the centrifugal impeller (1) and the inducer (2) are coaxially arranged with the transmission shaft (3);
the centrifugal impeller (1) comprises a front cover plate (101) and a rear cover plate (102) which adopt single arc transition;
the sealing structures are respectively arranged on the outer side of the front cover plate (101) and the outer side of the rear cover plate (102).
2. A high efficiency long flow path impeller low specific speed centrifugal pump as claimed in claim 1 wherein said centrifugal impeller (1) is provided with a plurality of long blades (103) and short blades (104), said short blades (104) having inlet ends biased toward the pressure surface of the adjacent long blades (103) and outlet ends biased toward the suction surface of the adjacent long blades (103).
3. A high efficiency long flowpath impeller low specific speed centrifugal pump as claimed in claim 2 wherein said front shroud (101) and back shroud (102) are both inclined and the front shroud (101) inclination is 2 times the back shroud (102) inclination.
4. A high efficiency long flowpath impeller low specific speed centrifugal pump as claimed in claim 3 wherein a plurality of balancing holes (105) are provided between said plurality of long vanes (103), said balancing holes (105) being circumferentially distributed adjacent the suction surface of the long vanes (103).
5. A high efficiency long flow path impeller low specific speed centrifugal pump as claimed in claim 1 wherein said front shroud (101) is provided with a front shroud seal surface (107) on the outside and said back shroud (102) is provided with a back shroud seal surface (108) on the outside.
6. A high efficiency long flowpath impeller low specific speed centrifugal pump according to claim 5, wherein said sealing structure comprises a sealing stationary ring (4) and a floating ring (7), said floating ring (7) being disposed outboard of the front shroud sealing face (107); the sealing static ring (4) is arranged on the outer side of the rear cover plate sealing surface (108).
7. A high efficiency long flow path impeller low specific speed centrifugal pump according to claim 6, wherein said static sealing ring (4) is provided on the static sealing ring base (5), and the outer side of the static sealing ring (4) is further provided with labyrinth seals (12).
8. A high efficiency long flowpath impeller low specific speed centrifugal pump as claimed in claim 6, characterized in that said front shroud seal face (107) is coated with a diamond-like or chrome based wear resistant self lubricating coating.
9. A high efficiency long flow path impeller low specific speed centrifugal pump according to any one of claims 1 to 8, wherein said centrifugal impeller (1) is of a closed straight blade configuration; the inducer (2) adopts an equal-pitch inlet section with a blade inlet cascade cavitation number and a variable-pitch outlet section with a rim blade angle gradually changed; the wrapping angle ratio of the equal-pitch inlet section of the inducer (2) is 0.3.
10. A high efficiency long flow path impeller low specific speed centrifugal pump according to claim 9, wherein a volute (901) is further provided outside the centrifugal impeller (1), and the volute (901) is a rectangular volute.
CN202110837936.XA 2021-07-23 2021-07-23 High-efficiency long-flow-passage impeller low-specific-speed centrifugal pump Pending CN113586513A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202110837936.XA CN113586513A (en) 2021-07-23 2021-07-23 High-efficiency long-flow-passage impeller low-specific-speed centrifugal pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202110837936.XA CN113586513A (en) 2021-07-23 2021-07-23 High-efficiency long-flow-passage impeller low-specific-speed centrifugal pump

Publications (1)

Publication Number Publication Date
CN113586513A true CN113586513A (en) 2021-11-02

Family

ID=78249334

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202110837936.XA Pending CN113586513A (en) 2021-07-23 2021-07-23 High-efficiency long-flow-passage impeller low-specific-speed centrifugal pump

Country Status (1)

Country Link
CN (1) CN113586513A (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114033699A (en) * 2021-11-17 2022-02-11 卢浩男 Reciprocating circulation centrifugal water pump
CN114396383A (en) * 2022-01-10 2022-04-26 成都凯天电子股份有限公司 Oil-gas mixed transportation system

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114033699A (en) * 2021-11-17 2022-02-11 卢浩男 Reciprocating circulation centrifugal water pump
CN114033699B (en) * 2021-11-17 2024-06-11 河南裕鸿机电科技有限公司 Centrifugal water pump with reciprocating circulation
CN114396383A (en) * 2022-01-10 2022-04-26 成都凯天电子股份有限公司 Oil-gas mixed transportation system

Similar Documents

Publication Publication Date Title
KR100530824B1 (en) Mixed flow turbine and mixed flow turbine rotor blade
JP4047330B2 (en) Independent passage diffuser
CN102287398B (en) Small-sized high-speed centrifugal pump suitable for flow regulation in wide range
CN113586513A (en) High-efficiency long-flow-passage impeller low-specific-speed centrifugal pump
US20160281732A1 (en) Impeller with offset splitter blades
CN105782073B (en) Multistage radial compressor baffle
US20160281727A1 (en) Apparatus, system, and method for compressing a process fluid
EP2221487B1 (en) Centrifugal compressor
US7273352B2 (en) Inlet partial blades for structural integrity and performance
JP2024086911A (en) Impeller and centrifugal compressor
WO2018155546A1 (en) Centrifugal compressor
WO2016160393A1 (en) Diffuser having multiple rows of diffuser vanes with different solidity
US11187242B2 (en) Multi-stage centrifugal compressor
CN215292999U (en) High-efficiency long-flow-passage impeller low-specific-speed centrifugal pump
US20200355198A1 (en) Impeller for centrifugal compressor, centrifugal compressor, and turbocharger
US11236669B2 (en) Turbine and turbocharger
US11125235B2 (en) Centrifugal compressor with diffuser with throat
JP4348043B2 (en) Fuel pump for gas turbine
JP5656164B2 (en) Turbo pump
US11885338B2 (en) Housing for a centrifugal compressor
US11781556B2 (en) High energy density turbomachines
CN114483646A (en) Impeller of rotary machine and rotary machine
WO2017047110A1 (en) Inducer and pump
US11982292B2 (en) Scroll casing and centrifugal compressor
WO1996008655A1 (en) Low specific speed impeller

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination