CN114320996A - Energy-saving type special-shaped opening ring and centrifugal pump gap sealing structure - Google Patents
Energy-saving type special-shaped opening ring and centrifugal pump gap sealing structure Download PDFInfo
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Abstract
An energy-saving clearance sealing structure for a special-shaped opening ring and a centrifugal pump is characterized in that the outer side surface of the special-shaped opening ring is a cylindrical surface, the inner side surface of the special-shaped opening ring is formed by smoothly transitionally enclosing a main cylindrical surface and at least one auxiliary cambered surface, the central axis corresponding to the main cylindrical surface and the central axis corresponding to the auxiliary cambered surface are eccentrically arranged, and the distance from the vertex of the auxiliary cambered surface to the central axis of the main cylindrical surface is greater than the radius of the main cylindrical surface; the centrifugal pump gap sealing structure comprises a pump shell and an impeller arranged in the pump shell, wherein an irregular opening ring is arranged between the inner circular surface of the pump shell and the outer circular surface of the front end of the impeller, a main cylindrical surface of the inner side surface of the irregular opening ring and the outer circular surface of the front end of the impeller form a main gap sealing structure, an auxiliary arc surface of the inner side surface of the irregular opening ring and the outer circular surface of the front end of the impeller form an auxiliary gap seal, and the position of the auxiliary gap seal is located between two connection parts of the auxiliary arc surface and the main cylindrical surface. The invention can improve the rate of finished products of the pump, reduce the production cost and ensure the high-efficiency operation of the pump.
Description
Technical Field
The invention belongs to the technical field of sealing of fluid machinery, and particularly relates to an energy-saving special-shaped opening ring and a centrifugal pump gap sealing structure.
Background
As a technical means for preventing two or more parts rotating with each other from rubbing or biting each other, a gap is left between the two mutually rotating parts. This structure is a form of sealing structure-clearance seal for centrifugal pumps. The sealing principle is as follows: a narrow channel is formed between the impeller (movable part) and the pump body (static part), and when the medium returns to the low-pressure area of the impeller inlet from the high-pressure area of the impeller outlet along the channel, the flow resistance of the medium is increased, so that the purposes of reducing medium leakage and ensuring the efficiency of the centrifugal pump are achieved, the energy consumption is reduced, and the centrifugal pump is environment-friendly and energy-saving. In order to increase the effect of reducing the amount of leakage, the inner and outer surfaces of this passage are sometimes designed to have various shapes. In order to protect the main parts on the pump from being worn and to facilitate replacement or repair after the moving and static parts are worn, a mouth ring is also arranged. Can restore the choma after the choma wearing and tearing, also can change to resume normal requirement clearance, guarantee the high efficiency operation of pump, the design of this kind of choma makes the pump very convenient when the maintenance, has reduced the replacement cost.
Typically, in an ideal case, the clearance between the impeller and the mouth ring has a value: 0.25-0.5 mm, high-pressure water ejected from the impeller outlet due to the existence of the gap flows back to a low-pressure area in the suction chamber of the water pump from the gap, so that the backflow leakage of the medium is caused, and the efficiency of the water pump is reduced. The greater this return loss, the more the efficiency of the water pump is reduced, greatly causing a waste of energy. In order to improve the efficiency of the water pump, the smaller the gap is, the better the gap is, but the smaller the gap is, the precision of parts and the precision of assembly are improved, which increases the difficulty of processing and assembly, thereby increasing the processing cost, and also causing energy waste and environmental pollution; and the coaxiality of the impeller and the mouth ring is difficult to ensure, and the impeller is easy to rub or be occluded with the mouth ring when rotating.
When an impeller is rubbed or occluded with a port ring in a rotating process due to machining or assembly errors, the port ring with a larger gap with the impeller is replaced, and after the port ring with the larger gap is replaced, medium backflow and leakage can be caused, so that the efficiency of the pump is further reduced, and in severe cases, the efficiency can not meet the national standard requirements and cannot leave a factory or be scrapped.
In the actual use process, the leakage at the position of the orifice ring is reduced under an ideal condition, the aim of improving the pump efficiency is fulfilled, and in order to achieve the aim, the adopted means is to try to increase the resistance of the flow of a medium, so that the orifice ring is designed into a complex structural shape. This complex construction requires good pump alignment. High precision in machining and assembling the parts of the pump is required to achieve good centering. Especially for the radial labyrinth seal's choma structure, the machining precision is higher, and in case the part is out of tolerance, the degree of difficulty of correcting is very big, and the part can only be scrapped.
On the other hand, as the machining and assembling precision of pump parts is improved, the maintenance difficulty in the out-of-tolerance state is increased, or the parts are scrapped, the factors increase the production cost of products, and the pump parts are not beneficial to energy conservation and market competition.
Disclosure of Invention
The invention aims to provide an energy-saving special-shaped opening ring and a gap sealing structure of a centrifugal pump, which can prevent an impeller and the opening ring from being rubbed and occluded and solve the problem that the efficiency of the pump is reduced due to overlarge gap caused by eccentricity of the existing opening ring structure; the problem that the existing mouth ring is complex in structure and high in processing, assembling and maintaining difficulty can be solved; the efficiency of the pump is not reduced while the machining and assembling precision is reduced and the maintenance difficulty is reduced to the maximum extent, so that the aims of reducing energy consumption, saving energy and protecting environment are fulfilled.
In order to achieve the purpose, the invention adopts the technical scheme that: the utility model provides an energy-saving dysmorphism choma, the lateral surface of dysmorphism choma is the face of cylinder, and the medial surface of dysmorphism choma is enclosed by main face of cylinder and at least one supplementary cambered surface smooth transition and closes and form, and the central axis that main face of cylinder corresponds and the central axis that supplementary cambered surface corresponds are eccentric settings, and the distance of supplementary cambered surface summit to main face of cylinder central axis is greater than the radius of main face of cylinder.
Alternatively, the auxiliary arc surface is a cylindrical surface.
Alternatively, the auxiliary arc surfaces are two conical surfaces arranged at intervals, and the two conical surfaces are arranged in opposite directions.
Furthermore, the two conical surfaces are oppositely arranged along the radial direction of the special-shaped opening ring.
The invention adopts another technical scheme that: the utility model provides a centrifugal pump clearance seal structure, includes the pump casing and sets up the impeller in the pump casing, is equipped with the choma that is fixed in on the pump casing between the outer face of cylinder of inner circle face and impeller front end in the pump casing, the choma is preceding dysmorphism choma, the main face of cylinder of dysmorphism choma medial surface and the outer face of cylinder formation main clearance seal structure of impeller front end, the supplementary cambered surface of dysmorphism choma medial surface and the outer face of cylinder formation auxiliary clearance of impeller front end are sealed, and two of the position that auxiliary clearance is sealed are located auxiliary cambered surface and main face of cylinder meet between the department.
As an alternative to the centrifugal pump clearance seal structure, the centrifugal pump is a single stage, single suction centrifugal pump.
Furthermore, the special-shaped opening ring is arranged between the inner circular surface of the pump cover of the single-stage single-suction centrifugal pump and the outer circular surface of the rear end of the impeller, and the special-shaped opening ring is fixed on the pump cover.
As a second option for the centrifugal pump clearance seal structure, the centrifugal pump is a single-stage double suction centrifugal pump.
As a third option for the centrifugal pump clearance seal structure, the centrifugal pump is a multistage centrifugal pump.
The beneficial effects of the invention include the following: 1. the clearance sealing structure can ensure the efficiency of the pump to the maximum extent, and the efficiency of the pump is not reduced after a new opening ring is replaced in order to avoid or prevent the friction and the occlusion between the impeller and the opening ring.
2. According to the invention, after the main-auxiliary combined gap sealing structure is formed by optimizing the structure of the mouth ring, the pump cannot be scrapped due to the fact that the efficiency of the pump cannot meet the national standard requirement caused by machining errors, so that waste is avoided, and the production cost is reduced to the maximum extent.
3. The optimized special-shaped opening ring can allow the eccentricity and the error of the pump, can reduce the machining precision requirement of pump parts, reduces the machining cost, reduces the production cost of the pump and improves the market competitiveness.
4. The optimized special-shaped opening ring can correct parts caused by machining errors, reduces waste caused by part scrapping, reduces production cost and improves market competitiveness.
5. The special-shaped opening ring ensures reasonable clearance of the pump, does not shorten the service life of the pump because of replacing the opening ring with larger clearance, and prolongs the use, replacement and maintenance period of the pump.
6. The energy-saving special-shaped opening ring and the gap sealing structure of the centrifugal pump can improve the yield of the pump, reduce the production cost, prolong the service life, ensure the pump to operate at a high-efficiency point, reduce the replacement and maintenance frequency and times, reduce the waste, save energy and protect environment.
Drawings
Fig. 1 is a schematic view of a first structural form of the energy-saving special-shaped mouth ring.
Fig. 2 is a partially enlarged view of a portion a in fig. 1.
Fig. 3 is a schematic view of a second structural form of the energy-saving type special-shaped opening ring.
Fig. 4 is a partially enlarged view of fig. 3 at B.
Fig. 5 is a partially enlarged view of C in fig. 3.
Fig. 6 is a cross-sectional view taken along line D-D of fig. 3.
Fig. 7 is a side partial sectional view of a conventional centrifugal pump.
Fig. 8 is a cross-sectional view E-E of fig. 7.
Fig. 9 shows the impeller offset Δ = δ0Schematic diagram of the impeller and the seal position of the gap between the orifice ring of the conventional centrifugal pump;
FIG. 10 shows the impeller offset Δ > δ0Schematic diagram of the impeller and the seal position of the gap between the orifice ring of the conventional centrifugal pump;
FIG. 11 is a schematic view of the gap between the impeller and the contoured ring of the centrifugal pump after the contoured ring has been replaced in the presence of FIG. 9;
FIG. 12 is a schematic view of the gap between the impeller and the contoured ring of the centrifugal pump after the contoured ring has been replaced in the presence of FIG. 10;
FIG. 13 is a schematic view of the gap between the impeller and the special-shaped opening ring of the centrifugal pump after the special-shaped opening ring is replaced under the condition of other eccentric positions of the impeller;
FIG. 14 is a schematic view of a dual auxiliary gap seal structure formed after replacement of a contoured split ring;
the labels in the figure are: 100. a special-shaped opening ring 101, a main cylindrical surface 102, an auxiliary cylindrical surface 103 and an auxiliary conical surface;
1. suction chamber, 2, impeller nut, 3, guide plate, 4, impeller, 5, seal gap, 6, mouth ring, 7, set screw, 8, pump shell, 9, impeller outlet channel, 10, impeller suction inlet channel, 11, volute chamber, 12, impeller nut sealing gasket, 13, pump transmission shaft, 14, impeller transmission key, 15, front chamber space channel, 16, pump shell front inner wall, 17, impeller front cover plate, 18, impeller front end outer cylindrical surface, 19, original mouth ring inner cylindrical surface, 20, conical surface large diameter end, 21, conical surface small diameter end.
Detailed Description
The present invention will be described in further detail with reference to the following drawings and examples, but the invention is not limited thereto.
As shown in fig. 7, in the conventional centrifugal pump, comprising a pump housing 8 and an impeller 4 disposed in the pump housing 8, a straight-tube type or straight-cone type suction chamber 1 is provided at the front end of the pump housing 8, and a baffle 3 is provided in the suction chamber 1 so that a medium smoothly enters an impeller suction passage 10 of the pump housing 8; the impeller suction passage 10 communicates with the suction chamber 1 in the front of the pump housing 8; be equipped with in the pump casing 8 and be used for going out the volute chamber 11 of water, still be equipped with the choma 6 of fastening on pump casing 8 by holding screw 7, on the axial, choma 6 is located between suction chamber 1 and the volute chamber 11 of pump casing 8, and radially, the outer cylinder face of choma 6 and the inner wall fastening connection of pump casing 8, the interior cylinder face of choma 6 and the outer cylinder face 18 clearance fit of impeller front end form seal clearance 5.
When the pump works, the pump transmission shaft 13 drives the impeller 4 to do circular motion to generate centrifugal force, and the low-pressure medium in the suction chamber 1 is conveyed into the volute chamber 11 to generate high pressure under the action of the centrifugal force of the impeller, so that the conversion from mechanical energy to pressure energy is realized, and the medium is pumped from a low position to a high position.
Since the volute 11 of the pump housing 8 is in communication with the suction chamber 1, the high pressure water discharged from the impeller outlet passage 9 into the volute will return to the suction chamber 1 again along the front chamber space passage 15 formed by the front inner wall 16 of the pump housing and the front cover plate 17 of the impeller, creating a leak. For this purpose, a mouth ring structure is provided, a sealing gap 5 is formed by the clearance fit of the inner cylindrical surface of the mouth ring 6 and the outer cylindrical surface 18 of the front end of the impeller, and the gap value delta of the sealing gap 5 is the conventional condition0And the diameter is not less than 0.25-0.5 mm, so that the normal work of the centrifugal pump can be met.
Conventionally, as shown in fig. 8, the center of the impeller 4 and the center of the pump housing 8 coincide with each other, and the eccentricity Δ thereof is 0, and at this time, four gap values δ of the seal gap in the vertical direction and the horizontal direction1、δ2、δ3And delta4Are all equal and are in the normal range delta0。
Because the normal clearance range of the seal clearance is small, machining and assembly errors can cause the center of the impeller 4 to deviate from the center of the pump housing 8 by a factor delta in fig. 83For example, the horizontal eccentricity of the impeller 4 and the pump housing 8 may cause δ3=0 or δ3Is less than 0. When the horizontal offset amount is delta = delta0When is delta3=0, the inner cylindrical surface of the mouth ring 6 is meshed with the outer cylindrical surface 18 at the front end of the impeller, the impeller 4 and the mouth ring 6 have the minimum clearance delta as shown in the attached figure 9, and the operation cannot be performed3Position, delta3=0, at mostLarge gap delta1Position, delta1=2δ0。
When the offset amount is delta > delta0When is delta3< 0, the inner cylindrical surface of the mouth ring 6 is blocked and collided with the outer cylindrical surface 18 of the front end of the impeller, as shown in figure 10, the impeller 4 is not rotated, the pump can not work normally, and the positions a and b in figure 10 are blocked parts respectively. In fig. 10, the gap value δ in the eccentric direction between the impeller 4 and the mouth ring 63=δ0- Δ < 0, gap value δ1=δ0+Δ。
If during operation of the centrifugal pump the situation as described in connection with fig. 9 and 10 occurs, the current practice is to replace the orifice ring with a larger inner cylindrical surface radius in order to increase the clearance between the orifice ring and the impeller. For the case shown in fig. 10, the gap between the mouth ring and the impeller needs to be increased by a larger magnitude than in the case of fig. 9. After the gap is increased, the gap between the impeller and the mouth ring is larger, and the leakage of the medium can be caused, so that the efficiency of the pump is influenced.
The energy-saving special-shaped opening ring and the corresponding gap sealing structure can well solve the problems and ensure the working efficiency of the pump.
Example 1: as shown in fig. 1 and 2, the outer side surface of the energy-saving type special-shaped orifice ring 100 provided by the invention is a cylindrical surface, and is matched with the inner wall of a pump housing and is fixedly assembled by fastening screws, the inner side surface of the special-shaped orifice ring 100 is formed by smoothly transitionally enclosing a main cylindrical surface 101 and an auxiliary cylindrical surface 102, the central axis corresponding to the main cylindrical surface 101 and the central axis corresponding to the auxiliary cylindrical surface 102 are eccentrically arranged, and the distance from the auxiliary cylindrical surface 102 to the central axis of the main cylindrical surface 101 is greater than the radius of the main cylindrical surface 101.
Example 2: when the centrifugal pump is in a situation as shown in fig. 9, the special-shaped mouth ring 100 of embodiment 1 is assembled on the pump shell 8 of the centrifugal pump to replace the original mouth ring 6, and after replacement, as shown in fig. 11, the position c in the figure is the position where the outer cylindrical surface at the front end of the original impeller and the inner cylindrical surface of the mouth ring are engaged and rubbed, after the special-shaped mouth ring of the invention is replaced, a main gap sealing structure is formed between the main cylindrical surface 101 of the special-shaped mouth ring 100 and the outer cylindrical surface 18 at the front end of the impeller, and the main gap sealing structure and the normal sealing structure are combinedThe sealing structures of the ring and the impeller of the gauge are the same; because the auxiliary cylindrical surface 102 of the special-shaped orifice ring 100 is expanded outward compared with the contour line of the main cylindrical surface 101, an auxiliary gap seal can be formed between the connecting positions d and e of the auxiliary cylindrical surface 102 and the main cylindrical surface 101 and the outer cylindrical surface 18 at the front end of the impeller, and the auxiliary gap seal is larger than the gap at the same position in fig. 9, especially the gap corresponding to the original position c. Assuming that the maximum distance of the auxiliary cylindrical surface 102 of the shaped orifice ring 100 from the contour line of the main cylindrical surface 101 is δ', the distance between the auxiliary cylindrical surface 102 of the shaped orifice ring 100 and the outer cylindrical surface 18 of the front end of the impeller at the position c is set to δ min after the replacement of the shaped orifice ring 100, since δ in fig. 93=0, therefore, after the special-shaped mouth ring 100 is replaced in fig. 11, the clearance between the impeller 4 and the special-shaped mouth ring 100 is δ3= δ min = δ', maximum gap δ across it1=2δ0And the radius, eccentricity, arc length and the like of the auxiliary cylindrical surface 102 leave a gap at the positions d and e to ensure the running of the impeller 4, so that the impeller 4 and the special-shaped mouth ring 100 at the positions d and e and the part between the positions d and e can not be engaged and rubbed. Through production test verification, the gap sealing structure after the special-shaped opening ring shown in figure 1 is replaced can ensure the original efficiency value of the pump, and can solve the technical problem shown in figure 9.
Example 3: when the centrifugal pump is in the condition shown in fig. 10, the positions a and b in the figure are the positions where the outer cylindrical surface at the front end of the original impeller and the inner cylindrical surface of the mouth ring are blocked; the special-shaped orifice ring 100 of the embodiment 1 is assembled on a pump shell 8 of the centrifugal pump to replace the original orifice ring 6, and after replacement, as shown in fig. 12, a main gap sealing structure is formed between a main cylindrical surface of the special-shaped orifice ring 100 and an outer cylindrical surface 18 at the front end of an impeller, and the main gap sealing structure is the same as a conventional orifice ring-impeller sealing structure; the arc surface from the point f to the point g on the special-shaped opening ring 100 is an auxiliary cylindrical surface 102 of the special-shaped opening ring 100, the auxiliary cylindrical surface 102 expands outwards compared with the contour line of the main cylindrical surface 101 corresponding to the position, and can form auxiliary gap sealing with the outer cylindrical surface 18 at the front end of the impeller, the original blocking positions a and b are located in the auxiliary gap sealing, the blocking state of the impeller 4 is relieved, and the point f and the point g are reserved with a gap for ensuring the running of the impeller through the design of the radius, the eccentricity, the arc length and the like of the auxiliary cylindrical surface 102, so that the problem of the figure 10 is solved. As can be seen from the enlarged portion of fig. 12, the inner cylindrical surface 19 of the original bellmouth ring is on the left side of the outer cylindrical surface 18 of the front end of the impeller, and the auxiliary cylindrical surface 102 of the replaced special-shaped bellmouth ring 100 is on the right side of the outer cylindrical surface 18 of the front end of the impeller, so that the requirement of impeller rotation is met.
Example 4: the present embodiment is different from embodiment 2 in that the eccentric position may be different due to uncertainty of the out-of-tolerance of parts due to machining and assembling errors, and the auxiliary gap seal of the present embodiment may be in any position according to the eccentric position. As shown in fig. 13, when the vertical eccentricity occurs, the auxiliary gap seal is formed between the point h and the point i after the change of the shape ring.
Example 5: due to machining and assembling errors and uncertainty of part out-of-tolerance, eccentric positions may be different, and axial deflection may occur at the same time, two auxiliary arc surfaces and a main cylindrical surface 101 are arranged on the inner side of the replaced special-shaped opening ring 100, the central axis corresponding to the main cylindrical surface 101 and the central axis corresponding to the auxiliary arc surfaces are eccentrically arranged, and the distance from the auxiliary arc surfaces to the central axis of the main cylindrical surface 101 is greater than the radius of the main cylindrical surface 101. Further, the auxiliary arc surface in this embodiment is an auxiliary conical surface 103, and the two conical surfaces are oppositely arranged along the radial direction of the shaped mouth ring, and the directions of the two conical surfaces are opposite, as shown in fig. 3-6.
Example 6: when the centrifugal pump runs and the conditions as described in embodiment 5 occur, the front end and the rear end of the impeller are occluded, rubbed and collided, and the special-shaped mouth ring with the structure described in embodiment 5 needs to be replaced to form double auxiliary gap sealing. As shown in fig. 14, on one side of the shaped mouth ring 100, the large diameter end 20 of the cone surface is at the front end of the mouth ring, the small diameter end 21 of the cone surface is at the rear end of the mouth ring, and on the opposite side, the large diameter end 20 of the cone surface of the other cone surface is at the rear end of the mouth ring, and the small diameter end 21 of the cone surface is at the front end of the mouth ring, so that two sections of auxiliary gap seals are respectively formed on the left side and the right side of the mouth ring, wherein the auxiliary gap on the left side is sealed at the front end of the mouth ring, and the auxiliary gap on the right side is sealed at the rear end of the mouth ring. Delta1’And delta1Front gaps sealed respectively for left auxiliary gapsAnd back clearance, δ3’And delta3Respectively, a front gap and a rear gap of the right auxiliary gap seal. In fig. 14, a main clearance seal structure is formed between the main cylindrical surface of the mouth ring and the outer cylindrical surface of the front end of the impeller, which is the same as the conventional mouth ring-impeller seal structure.
In the above embodiments, the centrifugal pumps are all single-stage single-suction centrifugal pumps, and the front end of the impeller is provided with the orifice ring, but it is understood by the skilled person that the present invention can also be applied to single-stage single-suction double-orifice ring centrifugal pumps, and the orifice rings are also provided at the impeller and the pump cover, or the skilled person can also understand that the present invention can also be applied to single-stage double-suction centrifugal pumps and multistage centrifugal pumps.
The above embodiments are only intended to illustrate the technical solution of the present invention and not to limit the same, and it should be understood by those of ordinary skill in the art that the specific embodiments of the present invention can be modified or substituted with equivalents with reference to the above embodiments, and any modifications or equivalents without departing from the spirit and scope of the present invention are within the scope of the claims to be appended.
Claims (9)
1. The utility model provides an energy-saving dysmorphism choma which characterized in that: the outer side face of the special-shaped opening ring is a cylindrical face, the inner side face of the special-shaped opening ring is formed by surrounding a main cylindrical face and at least one auxiliary arc face in a smooth transition mode, the central axis corresponding to the main cylindrical face and the central axis corresponding to the auxiliary arc face are arranged in an eccentric mode, and the distance from the vertex of the auxiliary arc face to the central axis of the main cylindrical face is larger than the radius of the main cylindrical face.
2. The energy-saving special-shaped mouth ring as claimed in claim 1, wherein: the auxiliary cambered surface is a cylindrical surface.
3. The energy-saving special-shaped mouth ring as claimed in claim 1, wherein: the auxiliary cambered surface is two conical surfaces arranged at intervals, and the two conical surfaces are arranged in opposite directions.
4. The energy-saving special-shaped mouth ring as claimed in claim 3, wherein: the two conical surfaces are oppositely arranged along the radial direction of the special-shaped opening ring.
5. The utility model provides a centrifugal pump clearance seal structure, includes the pump casing and sets up the impeller in the pump casing, is equipped with the choma that is fixed in on the pump casing between the outer face of cylinder of circle in the pump casing and impeller front end, its characterized in that: the mouth ring is the special-shaped mouth ring as claimed in any one of claims 1 to 4, a main cylindrical surface of the inner side surface of the special-shaped mouth ring and an outer cylindrical surface of the front end of the impeller form a main gap sealing structure, an auxiliary arc surface of the inner side surface of the special-shaped mouth ring and the outer cylindrical surface of the front end of the impeller form an auxiliary gap seal, and the position of the auxiliary gap seal is located between two connection positions of the auxiliary arc surface and the main cylindrical surface.
6. A centrifugal pump gap seal structure according to claim 5, wherein: the centrifugal pump is a single-stage single-suction centrifugal pump.
7. A centrifugal pump gap seal structure according to claim 6, wherein: the special-shaped opening ring is arranged between the inner circle surface of the pump cover of the single-stage single-suction centrifugal pump and the outer circle surface of the rear end of the impeller, and the special-shaped opening ring is fixed on the pump cover.
8. A centrifugal pump gap seal structure according to claim 5, wherein: the centrifugal pump is a single-stage double-suction centrifugal pump.
9. A centrifugal pump gap seal structure according to claim 5, wherein: the centrifugal pump is a multistage centrifugal pump.
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Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH11257287A (en) * | 1998-03-13 | 1999-09-21 | Teral Kyokuto Inc | Wear ring structure of centrifugal pump |
| JP2002257081A (en) * | 2001-02-26 | 2002-09-11 | Terada Pump Seisakusho:Kk | Leak preventing device for volute pump |
| CN201288673Y (en) * | 2008-09-25 | 2009-08-12 | 上海凯士比泵有限公司 | Inclination type intermediate section multi-stage centrifugal pump |
| CN203702015U (en) * | 2013-08-30 | 2014-07-09 | 宝山钢铁股份有限公司 | Gas sealconnecting structure for oil well pipe |
| JP2015197052A (en) * | 2014-03-31 | 2015-11-09 | 三菱重工業株式会社 | Centrifugal compressor, supercharger, and method of manufacturing centrifugal compressor |
| CN105485049A (en) * | 2015-12-30 | 2016-04-13 | 浙江理工大学 | Steady-flow centrifugal pump and design method thereof |
| CN106930968A (en) * | 2015-12-30 | 2017-07-07 | 苏尔寿管理有限公司 | For the multistage horizontal centrifugal pump and its repair method of trandfer fluid |
| CN111677686A (en) * | 2020-06-03 | 2020-09-18 | 黄河水利委员会黄河水利科学研究院 | Wear-resistant mouth ring of centrifugal water pump and preparation method thereof |
-
2021
- 2021-11-25 CN CN202111413718.XA patent/CN114320996B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH11257287A (en) * | 1998-03-13 | 1999-09-21 | Teral Kyokuto Inc | Wear ring structure of centrifugal pump |
| JP2002257081A (en) * | 2001-02-26 | 2002-09-11 | Terada Pump Seisakusho:Kk | Leak preventing device for volute pump |
| CN201288673Y (en) * | 2008-09-25 | 2009-08-12 | 上海凯士比泵有限公司 | Inclination type intermediate section multi-stage centrifugal pump |
| CN203702015U (en) * | 2013-08-30 | 2014-07-09 | 宝山钢铁股份有限公司 | Gas sealconnecting structure for oil well pipe |
| JP2015197052A (en) * | 2014-03-31 | 2015-11-09 | 三菱重工業株式会社 | Centrifugal compressor, supercharger, and method of manufacturing centrifugal compressor |
| CN105485049A (en) * | 2015-12-30 | 2016-04-13 | 浙江理工大学 | Steady-flow centrifugal pump and design method thereof |
| CN106930968A (en) * | 2015-12-30 | 2017-07-07 | 苏尔寿管理有限公司 | For the multistage horizontal centrifugal pump and its repair method of trandfer fluid |
| CN111677686A (en) * | 2020-06-03 | 2020-09-18 | 黄河水利委员会黄河水利科学研究院 | Wear-resistant mouth ring of centrifugal water pump and preparation method thereof |
Non-Patent Citations (1)
| Title |
|---|
| 高波;王震;杨丽;杜文强;李长军;: "叶轮口环间隙对离心泵性能及流动特性的影响", 排灌机械工程学报, no. 01, 31 January 2017 (2017-01-31), pages 13 - 17 * |
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