CN111550433A - Sealing ring with guide vanes in centrifugal pump - Google Patents
Sealing ring with guide vanes in centrifugal pump Download PDFInfo
- Publication number
- CN111550433A CN111550433A CN202010412372.0A CN202010412372A CN111550433A CN 111550433 A CN111550433 A CN 111550433A CN 202010412372 A CN202010412372 A CN 202010412372A CN 111550433 A CN111550433 A CN 111550433A
- Authority
- CN
- China
- Prior art keywords
- sealing ring
- guide vanes
- centrifugal pump
- impeller
- ring
- 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
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
- F04D29/08—Sealings
- F04D29/086—Sealings especially adapted for liquid pumps
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention provides a sealing ring with guide vanes in a centrifugal pump, which comprises a volute, an impeller and a sealing ring, wherein the sealing ring is positioned between the volute and the impeller and is arranged on the impeller; and a plurality of guide vanes are uniformly distributed on the outer ring of the sealing ring. The cross section of the sealing ring is trapezoidal, and the end face with large area of the sealing ring faces the impeller. The guide vane is an airfoil guide vane, a plurality of guide vanes are uniformly distributed on the inclined plane of the sealing ring, and the tail part of the airfoil guide vane is flush with the end face with small area of the sealing ring. The invention adopts the wing type guide vane to induce the fluid to generate the flow opposite to the leakage direction to prevent the fluid from flowing out from the clearance between the volute and the impeller, thereby reducing the volume loss and improving the volume efficiency of the centrifugal pump.
Description
Technical Field
The invention relates to the field of centrifugal pumps, in particular to a sealing ring with guide vanes in a centrifugal pump.
Background
The centrifugal pump is a vane type fluid machine, and the working principle of the centrifugal pump is that a prime mover drives an impeller to rotate so as to do work on fluid, and the mechanical energy of the prime mover is converted into the kinetic energy and the pressure energy of the fluid, so that the fluid is conveyed. The leakage of flow during operation in such vane pumps is inevitable and will cause energy loss in the centrifugal pump. In general, the energy loss of a centrifugal pump is mainly classified into three types, i.e., flow loss, volume loss, and disk friction loss. Wherein volume loss
Losses refer to flow losses caused by fluid leakage between the impeller rotation and the housing, the amount of leakage being related to the pressure differential acting across the gap and the gap configuration. This loss of energy will severely reduce the efficiency of the pump and therefore a sealing means is provided to prevent leakage of flow. At present, two sealing modes are used between the volute and the impeller, namely a smaller range leakage gap is arranged; and secondly, a complex sealing structure, such as a labyrinth type seal, is arranged to enlarge a sealing surface. However, a small clearance causes severe wear and reduced stability, and an excessively complicated seal structure is not favorable for production and assembly.
At present, in order to solve the problems of flow leakage of a centrifugal pump at an impeller and a volute and difficulty in machining and assembling caused by small gaps and complex structures, a non-contact sealing structure which ensures good sealing performance under a larger gap and a texture arranged on a sealing surface are provided to prevent fluid leakage. However, the texture is damaged under the scouring action of particles for a long time, the original effect is lost, once the texture is damaged, a new opening ring needs to be replaced, meanwhile, the particles enter the gap to easily reduce the gap between the upper opening ring and the lower opening ring, even the impeller and the pump body are seized, the centrifugal pump is damaged, and the maintenance difficulty and the maintenance cost are increased.
Disclosure of Invention
Aiming at the defects in the prior art, the invention provides the sealing ring with the guide vanes in the centrifugal pump, and the wing-shaped guide vanes are adopted to induce fluid to generate flow opposite to the leakage direction so as to prevent the fluid from flowing out from the gap between the volute and the impeller, so that the volume loss is reduced, and the volume efficiency of the centrifugal pump is improved.
The present invention achieves the above-described object by the following technical means.
A sealing ring with guide vanes in a centrifugal pump comprises a volute, an impeller and a sealing ring, wherein the sealing ring is positioned between the volute and the impeller and is arranged on the impeller; and a plurality of guide vanes are uniformly distributed on the outer ring of the sealing ring.
Further, the cross section of the sealing ring is trapezoidal, and the end face with the large area of the sealing ring faces the impeller.
Furthermore, the guide vanes are wing-shaped guide vanes, a plurality of guide vanes are uniformly distributed on the inclined plane of the sealing ring, and the tail parts of the wing-shaped guide vanes are flush with the end surface with small area of the sealing ring.
Furthermore, an included angle alpha between a chord of the guide vane and the circumferential direction of the guide vane is 10-20 degrees.
Further, the inner hole radius R of the sealing ring is the sum of the inlet radius of the impeller and the thickness of a front cover plate of the impeller.
Further, the sealing ring has a small area and a small end face thickness e1Is 0.06 times of the radius R of the inner hole of the sealing ring; the end face thickness e of the sealing ring with large area2Is e13-5 times of the total weight of the product.
Further, the thickness b of the trapezoidal cross section of the sealing ring is 0.25-0.35 times of the radius R of the inner hole of the sealing ring.
Furthermore, the thickness h of the guide vane is 0.05-0.08 times of the radius R of the inner hole of the sealing ring.
Further, the airfoil guide vanes are NACA airfoil guide vanes, and the number of the airfoil guide vanes is 8-15.
The invention has the beneficial effects that:
1. the sealing ring with the guide vane in the centrifugal pump is a circular ring with an inclined plane and a sealing ring of an airfoil guide vane, and when the impeller of the centrifugal pump rotates, the sealing ring is driven to rotate. When fluid enters a gap between the volute and the sealing ring along the inclined plane, the inflow speed and the leakage pressure are reduced under the action of the centrifugal force of the inclined plane, and then the directional flow is generated under the induction of the airfoil guide vane, wherein the induction direction is directed to a gap inlet along the inclined plane and is opposite to the direction of the fluid entering the gap in the radial direction. The induced fluid collides with the leaked fluid, an annular flow field with larger pressure along the outer diameter of the circular ring is formed at the inlet of the gap, the fluid leakage is prevented, and good sealing performance under larger gaps is ensured.
2. Compared with the traditional sealing method that the sealing ring with the guide vanes is in a complex structure and reduces the leakage gap, the sealing ring with the guide vanes in the centrifugal pump adopts the NACA airfoil guide vanes, induces the leakage fluid to move reversely to discharge the gap and collide with the subsequent fluid at the gap inlet to form a high-pressure annular flow area, can ensure the good sealing performance of the centrifugal pump under a larger gap, and has the advantages of convenient implementation, simple replacement and the like, thereby reducing the maintenance cost of the centrifugal pump.
3. The sealing ring with the guide vanes in the centrifugal pump adopts a mode that the guide vanes are arranged at a certain angle with the radial direction, namely the sealing surface is arranged in the radial direction and the axial direction, the sealing mode not only increases the sealing surface, but also improves the sealing performance through the wing-shaped guide vanes. Compared with the traditional sealing mode, the sealing device with the guide vanes can ensure good sealing performance under the condition of large clearance, and meanwhile, the sealing ring is not easy to damage, so that the service life of the sealing ring is prolonged.
Drawings
Fig. 1 is a schematic perspective view of a seal ring with guide vanes in a centrifugal pump according to the present invention.
Fig. 2 is a front view of fig. 1.
Fig. 3 is a view of the guide vane of fig. 2 expanded along a slant surface.
Fig. 4 is a radial cross-section through the ring 1 in fig. 1.
Fig. 5 is a schematic view showing the installation of a seal ring having guide vanes in the centrifugal pump according to the present invention.
Fig. 6 is an enlarged view of a portion a of fig. 5.
In the figure:
1-a sealing ring; 2-guide vanes; 3-a volute; 4-impeller.
Detailed Description
The invention will be further described with reference to the following figures and specific examples, but the scope of the invention is not limited thereto.
As shown in fig. 1 and 5, the centrifugal pump of the present invention has a seal ring with guide vanes therein, the centrifugal pump includes a volute 3, an impeller 4 and a seal ring 1, the seal ring 1 is located between the volute 3 and the impeller 4, and the seal ring 1 is mounted on the impeller 4; and a plurality of guide vanes 2 are uniformly distributed on the outer ring of the sealing ring 1. The central axis of the seal ring 1 is collinear with the central axis of the impeller 4 when installed. The cross section of the sealing ring 1 is trapezoidal, namely the area of one end face of the sealing ring 1 is larger than that of the other end face of the sealing ring 1. As shown in fig. 6, the area of the end surface on the left side is smaller than the area of the end surface on the right side. The right side end face of the sealing ring 1 faces the impeller 4. The sealing ring 1 and the impeller 4 are fixed on the impeller 4 in an interference fit manner. An installation gap of 0.6-1.0mm is kept between the outer side wall surface of the airfoil guide vane 2 and the wall surface of the volute 3, and non-contact installation is adopted.
As shown in fig. 1 and 2, the cross section of the sealing ring 1 is trapezoidal, a certain angle is formed between a trapezoidal inclined plane and the axial direction, 8-15 airfoil guide vanes 2 are uniformly and fixedly arranged on the inclined plane along the circumferential direction, the airfoil guide vanes 2 protrude outwards along the vertical direction of the inclined plane, and the tail parts of the airfoil guide vanes 2 are flush with the excircle of the end surface of the sealing ring 1.
As shown in fig. 1, fig. 2, fig. 3 and fig. 6, the inner hole radius R of the sealing ring 1 is determined according to the size of the impeller 4 of the centrifugal pump, and the inner hole radius R of the sealing ring 1 is the sum of the inlet radius of the impeller 4 and the thickness of the front cover plate of the impeller. Thickness e of left end face of sealing ring 11The radius of the inner hole of the sealing ring 1 is 0.06 times of the radius R of the inner hole, and the thickness e of the right end surface of the sealing ring 12Is e13-5 times, the thickness b of the sealing ring 1 in the axial direction is 0.25-0.35 times the radius R of the inner hole of the sealing ring 1. When the centrifugal pump impeller rotates, the sealing ring is driven to rotate, and when leaking fluid enters a gap between the volute and the sealing ring along the inclined plane, the inflow speed and the leaking pressure are reduced under the action of the centrifugal force of the inclined plane, so that the fluid leakage is prevented.
Referring to fig. 3, the airfoil guide vane 2 is an airfoil, and is an NACA airfoil, the chord length L along the inclined guide vane 2 is 0.4R, and the blade installation angle α is 10 ° to 20 °, that is, the included angle α between the chord of the vane and the circumferential direction of the vane is.
Referring to fig. 3, the thickness h of the airfoil guide vane along the vertical direction of the inclined plane is 0.05-0.10 times of the radius R of the inner hole of the sealing ring 1. The invention selects the NACA4415 airfoil type guide vane, because the NACA4415 airfoil type guide vane 2 has the characteristics of narrow length and large outlet pressure, namely large leakage pressure. Because the ratio of the length of the working surface of the wing profile to the length of the back surface of the wing profile is larger, larger conveying pressure opposite to the leakage direction can be generated along the direction of the inclined surface, so that induced fluid collides with the leakage fluid, an annular flow field with larger pressure along the outer diameter of the circular ring is formed at the inlet of the gap, the fluid leakage is prevented, and the centrifugal pump has good sealing performance under the larger gap.
The present invention is not limited to the above-described embodiments, and any obvious improvements, substitutions or modifications can be made by those skilled in the art without departing from the spirit of the present invention.
Claims (9)
1. A sealing ring with guide vanes in a centrifugal pump comprises a volute (3) and an impeller (4), and is characterized by further comprising a sealing ring (1), wherein the sealing ring (1) is located between the volute (3) and the impeller (4), and the sealing ring (1) is installed on the impeller (4); a plurality of guide vanes (2) are uniformly distributed on the outer ring of the sealing ring (1).
2. Sealing ring with guide vanes in a centrifugal pump according to claim 1, characterized in that the cross-section of the sealing ring (1) is trapezoidal and the end face of the sealing ring (1) with large area faces the impeller (4).
3. The sealing ring with the guide vanes in the centrifugal pump according to claim 1, wherein the guide vanes (2) are airfoil-shaped guide vanes, a plurality of guide vanes (2) are uniformly distributed on the inclined surface of the sealing ring (1), and the tail parts of the airfoil-shaped guide vanes (2) are flush with the end surface of the sealing ring (1) with a small area.
4. Sealing ring with guide vanes in a centrifugal pump according to claim 1, characterized in that the angle α between the chord of the guide vane (2) and the circumferential direction of the guide vane is 10 ° -20 °.
5. The sealing ring with guide vanes in the centrifugal pump according to claim 1, characterized in that the inner hole radius R of the sealing ring (1) is the sum of the inlet radius of the impeller (4) and the thickness of the front cover plate of the impeller.
6. Seal ring with guide vanes in a centrifugal pump according to claim 5, characterized in that the seal ring (1) has a small area end surface thickness e1Is 0.06 times of the radius R of the inner hole of the sealing ring (1); the end face thickness e of the sealing ring (1) with large area2Is e13-5 times of the total weight of the product.
7. Sealing ring with guide vanes in a centrifugal pump according to claim 5, characterized in that the trapezoidal cross-sectional thickness b of the sealing ring (1) is 0.25-0.35 times the inner bore radius R of the sealing ring (1).
8. Sealing ring with guide vanes in a centrifugal pump according to claim 5, characterized in that the thickness h of the guide vanes (2) is 0.05-0.08 times the radius R of the inner bore of the sealing ring (1).
9. The seal ring with guide vanes in a centrifugal pump according to claim 3, wherein said airfoil guide vanes are NACA airfoil guide vanes, and the number of said airfoil guide vanes is 8-15.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010412372.0A CN111550433A (en) | 2020-05-15 | 2020-05-15 | Sealing ring with guide vanes in centrifugal pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010412372.0A CN111550433A (en) | 2020-05-15 | 2020-05-15 | Sealing ring with guide vanes in centrifugal pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN111550433A true CN111550433A (en) | 2020-08-18 |
Family
ID=72001965
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010412372.0A Pending CN111550433A (en) | 2020-05-15 | 2020-05-15 | Sealing ring with guide vanes in centrifugal pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN111550433A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114738300A (en) * | 2022-04-20 | 2022-07-12 | 江苏毅合捷汽车科技股份有限公司 | Two-stage centrifugal air compressor |
| CN114837966A (en) * | 2022-04-20 | 2022-08-02 | 江苏毅合捷汽车科技股份有限公司 | Centrifugal air compressor and control method thereof |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2644403A (en) * | 1952-03-05 | 1953-07-07 | Ingersoll Rand Co | Device for preventing clogging in centrifugal pumps |
| GB1431189A (en) * | 1972-05-15 | 1976-04-07 | Ahlstroem Oy | Pumps |
| JPS55128695A (en) * | 1979-03-26 | 1980-10-04 | Hitachi Ltd | Centrifugal pump |
| SU1273648A1 (en) * | 1985-07-05 | 1986-11-30 | Всесоюзный Научно-Исследовательский Институт Горной Механики Им.М.М.Федорова | Sealing for neck of centrifugal pump impeller |
| SU1483100A1 (en) * | 1987-10-26 | 1989-05-30 | Уральский филиал Всесоюзного теплотехнического научно-исследовательского института им.Ф.Э.Дзержинского | Seal for centrifugal pump impeller |
| KR101797096B1 (en) * | 2017-05-26 | 2017-11-15 | 덕지산업 주식회사 | Centrifugal pump with reduced leakage loss between casing and impeller |
| CN108869379A (en) * | 2018-05-02 | 2018-11-23 | 江苏大学 | A kind of centrifugal pump seal ring with axial diversion blade |
-
2020
- 2020-05-15 CN CN202010412372.0A patent/CN111550433A/en active Pending
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2644403A (en) * | 1952-03-05 | 1953-07-07 | Ingersoll Rand Co | Device for preventing clogging in centrifugal pumps |
| GB1431189A (en) * | 1972-05-15 | 1976-04-07 | Ahlstroem Oy | Pumps |
| JPS55128695A (en) * | 1979-03-26 | 1980-10-04 | Hitachi Ltd | Centrifugal pump |
| SU1273648A1 (en) * | 1985-07-05 | 1986-11-30 | Всесоюзный Научно-Исследовательский Институт Горной Механики Им.М.М.Федорова | Sealing for neck of centrifugal pump impeller |
| SU1483100A1 (en) * | 1987-10-26 | 1989-05-30 | Уральский филиал Всесоюзного теплотехнического научно-исследовательского института им.Ф.Э.Дзержинского | Seal for centrifugal pump impeller |
| KR101797096B1 (en) * | 2017-05-26 | 2017-11-15 | 덕지산업 주식회사 | Centrifugal pump with reduced leakage loss between casing and impeller |
| CN108869379A (en) * | 2018-05-02 | 2018-11-23 | 江苏大学 | A kind of centrifugal pump seal ring with axial diversion blade |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114738300A (en) * | 2022-04-20 | 2022-07-12 | 江苏毅合捷汽车科技股份有限公司 | Two-stage centrifugal air compressor |
| CN114837966A (en) * | 2022-04-20 | 2022-08-02 | 江苏毅合捷汽车科技股份有限公司 | Centrifugal air compressor and control method thereof |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN111550433A (en) | Sealing ring with guide vanes in centrifugal pump | |
| CN108869379B (en) | Centrifugal pump sealing ring with axial guide vanes | |
| CN106870243A (en) | A kind of multi-state multistage turbine | |
| CN212003608U (en) | Small-flow high-lift multistage centrifugal pump | |
| US7210904B2 (en) | Runner blade for low specific speed Francis turbine | |
| CN106949087B (en) | Shaft seal type nuclear main pump impeller structure with back vanes | |
| US9470101B2 (en) | Turbomachine | |
| CN108869384B (en) | Radial sealing ring of centrifugal pump with cylindrical guide vanes | |
| KR101393054B1 (en) | Adapter for preventing cavitaion and centrifugal pump having adapter | |
| CN110469539B (en) | Impeller, centrifugal pump and air conditioner | |
| CN211900990U (en) | Impeller for multistage centrifugal pump and multistage centrifugal pump | |
| CN108331784B (en) | Centrifugal pump open impeller structure | |
| CN215672848U (en) | Self-balancing multistage centrifugal pump with efficient throttling seal | |
| CN113550795B (en) | Gas turbine suitable for all territories | |
| JP2001073993A (en) | Centrifugal fluid machinery | |
| CN114017347A (en) | Sectional type multistage centrifugal pump without balancing device | |
| CN210178579U (en) | Small-flow high-pressure sectional type multistage pump | |
| CN108825549B (en) | Radial sealing ring of centrifugal pump with wing type guide vanes | |
| CN111878450A (en) | Sealing mechanism, axial flow compressor and gas turbine | |
| CN216477868U (en) | Sectional type multistage centrifugal pump without balancing device | |
| CN111828370B (en) | Radial sealing opening ring of centrifugal pump | |
| CN210949168U (en) | Energy-saving pump body structure | |
| CN108757546B (en) | Radial sealing ring of centrifugal pump with flat guide vane | |
| CN220581275U (en) | Secondary rectification centrifugal pump structure | |
| CN211343369U (en) | Small vortex submersible electric pump |
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 | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20200818 |
|
| RJ01 | Rejection of invention patent application after publication |