CN110578706A - Super-separation type impeller of spiral axial-flow oil-gas mixed transportation pump - Google Patents
Super-separation type impeller of spiral axial-flow oil-gas mixed transportation pump Download PDFInfo
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- CN110578706A CN110578706A CN201910873627.0A CN201910873627A CN110578706A CN 110578706 A CN110578706 A CN 110578706A CN 201910873627 A CN201910873627 A CN 201910873627A CN 110578706 A CN110578706 A CN 110578706A
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- gas
- hub
- blade
- phase
- impeller
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/18—Rotors
- F04D29/181—Axial flow rotors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D31/00—Pumping liquids and elastic fluids at the same time
Abstract
The invention relates to an ultra-separation type impeller of a spiral axial-flow oil-gas mixed transportation pump, which belongs to the technical field of oil-gas mixed transportation in oil exploitation and comprises a hub and blades; the blades are arranged on the outer ring wall of the hub, and the hub is a conical hub; the maximum thickness of the adjacent surface of the blade and the hub is smaller than that of the blade at the rim. The gas-liquid separation phenomenon and the gas aggregation phenomenon during two-phase flow are improved by adjusting the thickening ratio coefficient xi. The gas-liquid separation is delayed to the tail edge as far as possible, the phase state separation phenomenon in the impeller is optimized, the blade distortion can be reduced to a certain degree, the whole channel is in a gradually reducing shape when the outer diameter of the rim is fixed, and the reduction of the speed of the shaft surface caused by gas compression and flow reduction can be avoided when a two-phase medium is conveyed.
Description
Technical Field
The invention relates to the technical field of oil and gas mixed transportation in oil exploitation, in particular to a super-separation type impeller of a spiral axial-flow oil and gas mixed transportation pump.
Background
with the continuous progress and development of the current society, the requirements on oil field exploitation and transportation technology in industrial application are higher and higher, and the design and application of the multiphase booster pump are emphasized as the core of oil-gas mixed transportation technology. The multiphase pump with wider application is a spiral axial flow multiphase mixed transportation pump, and the spiral axial flow multiphase mixed transportation pump has the advantages that an impeller structure is provided with a long square channel and has a larger flow channel curvature radius, and the impeller adopts an open or semi-open structure and can convey sand-containing media. The gas-liquid two-phase flow is easily affected by a plurality of external factors, and the relative motion and the complex interface effect exist between the phases, so that the students can hardly find out the evolution mechanism of the two-phase flow, and one of the difficulties of improving the working efficiency of the vane type oil-gas mixed transportation pump is to reduce the phase-state separation and enhance the mixing of the gas phase and the liquid phase in the impeller.
The oil-gas mixed transportation pump is a high-efficiency and economic core device of an oil field development mode, is a multiphase transportation device integrating the performances of a conventional liquid phase pump and a gas compressor, and has great influence on the performance of the pump by taking an impeller as a core overflowing part of the oil-gas mixed transportation pump.
disclosure of Invention
The invention aims to provide an over-separating impeller of a spiral axial-flow oil-gas mixed transportation pump with reasonable design aiming at the defects and shortcomings of the prior art, gas-liquid separation is delayed to the tail edge as far as possible, the phase separation phenomenon in the impeller is optimized, the blade distortion can be reduced to a certain extent, the whole channel is gradually reduced when the outer diameter of the rim is fixed, and the reduction of the axial surface speed caused by gas compression and flow reduction can be avoided when two-phase media are transported.
In order to achieve the purpose, the invention adopts the following technical scheme: it comprises a hub and a blade; the blades are arranged on the outer ring wall of the hub, and the hub is a conical hub; the maximum thickness of the adjacent surface of the blade and the hub is smaller than that of the blade at the rim.
The working principle of the invention is as follows:
The two-phase medium has certain kinetic energy after being rotated to do work by the impeller, then flows out of the outlet edge of the impeller in the working process of the spiral axial flow type oil-gas mixed transportation pump, the two-phase fluid flows in from the direction of the water inlet edge, and flows out of the spiral axial flow type oil-gas mixed transportation pump in the direction of the water outlet edge after being acted by the blades; because the impeller rotates to cause that the pressure gradient is formed on the working surface of the blade and the back surface of the blade and the centrifugal force acts, separation power is provided for gas phase and liquid phase, the separation of the gas phase and the liquid phase is intensified, and the density of the gas phase is far less than that of the liquid phase, so that under the combined action of the centrifugal force and the pressure gradient, the gas phase with low density gradually moves to an adjacent surface area close to the hub, and the liquid phase with high density is gradually thrown to a rim area, so that the separation phenomenon of the gas phase and the liquid phase is formed in an impeller runner;
Introducing a thickening ratio coefficient xi which represents the intensity of the change of the blade thickness from the hub to the rim, and the expression is as follows:
on the basis of meeting the strength requirement of the hub and the process requirement of the wheel rim, the thickening ratio coefficient xi is enabled to be<1, i.e. maximum thickness δ at the adjacent face of the blade to the hubh maxLess than its maximum thickness at the rim
δs maxThe different thickening ratio coefficients correspond to different blade back molded lines, the molded lines of the working surfaces of the blades are all consistent, the larger the thickening ratio coefficient is, the more inclined the blades are towards the rim direction, the smaller the thickening ratio coefficient is, the more inclined the blades are towards the adjacent surface direction, and the thickening ratio coefficient is<1, the acting force of the back of the blade on the fluid is opposite to the centrifugal force direction in the radial component force direction, namely, a part of gas-liquid separation power is reduced, so that the gas-liquid separation phenomenon and the gas aggregation phenomenon in a flow channel can be improved, the gas-liquid separation phenomenon can be delayed to a tail edge area by the wing section of the impeller under the condition, the gas-liquid separation phenomenon cannot occur at the middle and rear parts of the impeller to cause the performance reduction of the mixing and conveying pump, and meanwhile, the effect of slowing down the flow channel is achievedthe gas-liquid separation phenomenon can also correspondingly improve the mixing and conveying performance of the mixing and conveying pump; the gas-liquid separation phenomenon and the gas aggregation phenomenon during two-phase flow are improved by adjusting the thickening ratio coefficient xi.
after adopting the structure, the invention has the beneficial effects that: the invention provides an ultra-separation type impeller of a spiral axial-flow oil-gas mixed transportation pump, which delays gas-liquid separation to the tail edge as much as possible, optimizes the phase state separation phenomenon in the impeller, can reduce the blade distortion to a certain extent, has a whole channel in a gradually reducing shape when the outer diameter of a wheel rim is fixed, and can avoid the reduction of the axial surface speed caused by gas compression and flow reduction when two-phase media are transported.
Description of the drawings:
Fig. 1 is a schematic structural view of the present invention.
Fig. 2 is an external view of a blade according to the invention.
Fig. 3 is an internal view of a blade according to the invention.
Fig. 4 is a force analysis diagram of the background art.
FIG. 5 is a force analysis diagram of the present invention.
Description of reference numerals:
The wind turbine blade comprises a hub 1, blades 2, blade back faces 2-1, blade working faces 2-2, a wheel rim 2-3 and adjacent faces 2-4.
The specific implementation mode is as follows:
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 only a part of the embodiments of the present invention, and not all of the embodiments. 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.
As shown in fig. 1 to fig. 3, the following technical solutions are adopted in the present embodiment: it comprises a hub 1 and blades 2; the blades 2 are arranged on the outer ring wall of the hub 1, and the hub 1 is a conical hub; the maximum thickness of the adjacent surfaces 2-4 of the blades 2 and the hub 1 is smaller than that of the maximum thickness of the adjacent surfaces at the wheel rims 2-3.
the working principle of the specific embodiment is as follows:
the two-phase medium has certain kinetic energy after rotating to do work through the impeller, then flows out of the outlet edge of the impeller in the working process of the spiral axial flow type oil-gas mixed transportation pump, the two-phase fluid flows in from the direction of the water inlet edge, and flows out of the water outlet edge after the two-phase fluid works through the blade 2 (mainly works through the working surface 2-2 of the blade); because the impeller rotates to cause the pressure gradient formation on the working surface 2-2 of the blade and the back surface 2-1 of the blade and the action of centrifugal force, the separation power is provided for gas phase and liquid phase, the separation of the gas phase and the liquid phase is intensified, and the density of the gas phase is far less than that of the liquid phase, so that under the combined action of the centrifugal force and the pressure gradient, the gas phase with low density gradually moves to the area 2-4 close to the adjacent surface of the hub 1, and the liquid phase with high density is gradually thrown to the area 2-3 of the wheel rim, so that the separation phenomenon of the gas phase and the liquid phase is formed in a runner of the impeller;
Typically, during thickening of the blade 2, the maximum thickness δ of the adjacent faces 2-4 of the blade 2 and the hub 1 ish maxThe thickness is greatest at the adjacent face 2-4 of the hub 1, as determined by the strength conditions, and varies linearly from the adjacent face 2-4 to the rim 2-3, generally thinner than at the hub 1. The thickening rule of the blade 2 can be any airfoil profile thickness variation rule for thickening, wherein 791 the airfoil profile is most commonly applied to a multiphase mixing pump.
In order to explore the influence of the linear change rule of the maximum thickness from the hub to the rim on the external characteristic and the mixed transmission characteristic of the multiphase mixed transmission pump, a thickening ratio coefficient xi is introduced, the coefficient represents the intensity of the change of the thickness of the blade from the hub to the rim, and the expression is as follows:
on the basis of meeting the strength requirement of the hub 1 and the process requirement of the wheel rim 2-3, the thickening ratio coefficient xi is enabled to be<1, i.e. the maximum thickness delta at the adjacent faces 2-4 of the blade 2 and the hub 1h maxLess than its maximum thickness delta at the rim 2-3s maxDifferent thickening ratio systemThe number of the molded lines of the back surfaces of the blades is different, the molded lines of the working surfaces of the blades are all the same, the larger the thickening ratio coefficient is, the more the blades incline towards the 2-3 direction of the wheel rim, the smaller the thickening ratio coefficient is, the more the blades incline towards the 2-4 direction of the adjacent surfaces, and the thickening ratio coefficient is<1, the acting force of the back 2-1 of the blade on the fluid is opposite to the centrifugal force direction in the radial component force direction, which is equivalent to the reduction of a part of gas-liquid separation power, so that the gas-liquid separation phenomenon and the gas aggregation phenomenon in a flow channel can be improved, the wing section of the impeller under the condition can well delay the gas-liquid separation phenomenon to a tail edge area, the gas-liquid separation phenomenon can not occur at the middle rear part of the impeller to cause the performance reduction of the mixed delivery pump, and simultaneously, the mixed delivery performance of the mixed delivery pump can be correspondingly improved due to the slowing of the gas-liquid separation phenomenon in the flow channel; the gas-liquid separation phenomenon and the gas aggregation phenomenon during two-phase flow are improved by adjusting the thickening ratio coefficient xi.
Referring to fig. 4 and 5, the existing model (fig. 4, the coefficient of thickening ratio thereof) with the thickness at the adjacent surface 2-4 of the hub 1 larger than the maximum thickness at the rim 2-3 is shown>1) Model with thickness at the adjacent face 2-4 of the hub 1 less than its maximum thickness at the rim 2-3 (see fig. 5 for its thickening ratio coefficient)<1) And (3) carrying out simplified blade stress analysis: in the figure, FtRepresenting the force exerted by the blade back on the fluid particles in a direction perpendicular to the blade back, where FtxRepresents Fta component force in a radial direction. FcRepresenting the centrifugal force to which the fluid particles are subjected when the impeller is rotating, the direction being from the hub side to the rim side. FpRepresenting the differential pressure force directed from the rim side to the hub side to which the fluid particles are subjected, the two-phase fluid is primarily subjected to the above forces in the flow regime.
as can be seen from fig. 4 and 5, the centrifugal force is directed from the hub side to the rim side, the force and the pressure difference force are separation power causing separation of two phases, when the difference between the two forces is larger, the fluid particles will be subjected to the combined action of the centrifugal force and the pressure difference force, so that the gas phase with small density will move towards the hub side, the liquid phase with large density will move towards the rim side, and the liquid phase with large density will continue to apply a squeezing force to the gas phase with small density, so that the gas phase gradually gathers at the hub, and when serious, the gas blockage phenomenon will be caused, and the performance of the multiphase pump will be reduced. When the thickening ratio coefficient xi is larger than 1, the acting force of the back surface of the blade on the fluid is consistent with the direction of the centrifugal force in the radial component direction, which is equivalent to applying a power to the separation of two phases. When the thickening ratio coefficient xi is less than 1, the direction is opposite, the acting force of the back of the blade on the fluid is opposite to the centrifugal force direction in the radial component force direction, which is equivalent to cutting down a part of gas-liquid separation power, so that the gas-liquid separation phenomenon and the gas aggregation phenomenon in the flow channel can be improved, the gas-liquid separation phenomenon can be delayed to the tail edge region well by the wing section of the impeller, the gas-liquid separation phenomenon can not occur at the middle rear part of the impeller to cause the performance reduction of the mixed delivery pump, and simultaneously, the mixed delivery performance of the mixed delivery pump can be correspondingly improved due to the fact that the gas-liquid separation phenomenon in the flow channel is slowed down, so that the wing section is defined.
After adopting above-mentioned structure, this embodiment's beneficial effect is as follows:
1. Introducing a thickening ratio coefficient, and adjusting the inclination of the back of the blade by adjusting the thickening ratio coefficient value so as to correspondingly change the force acting on the fluid point;
2. Compared with the stress analysis of the blades with the thickening ratio coefficient more than 1 on fluid particles in the prior art, the scheme with the thickening ratio coefficient less than 1 can reduce part of gas-liquid separation power, effectively improve the gas-liquid separation and gas aggregation phenomena in a flow channel, and further improve the performance of the mixed transportation pump;
3. the impeller can delay the gas-liquid separation phenomenon in the flow channel to the impeller ultra-separation wing section at the tail edge, solves the problem that gas-liquid phases are gathered at the middle rear part of the flow channel, and can effectively improve the mixed transportation characteristic of the mixed transportation pump.
Although the present invention has been described in detail with reference to the foregoing embodiments, it will be apparent to those skilled in the art that various changes in the embodiments and/or modifications of the invention can be made, and equivalents and modifications of some features of the invention can be made without departing from the spirit and scope of the invention.
Claims (2)
1. The utility model provides a superseparation type impeller of spiral axial-flow type oil-gas multiphase pump which characterized in that: it comprises a hub (1) and blades (2); the blades (2) are arranged on the outer annular wall of the hub (1), and the hub (1) is a conical hub; the maximum thickness of the adjacent surface (2-4) of the blade (2) and the hub (1) is smaller than that of the blade at the rim (2-3).
2. The utility model provides a superseparation type impeller of spiral axial-flow type oil-gas multiphase pump which characterized in that: the working principle is as follows: the two-phase medium has certain kinetic energy after being rotated to do work by the impeller, then flows out of the outlet edge of the impeller in the working process of the spiral axial flow type oil-gas mixed transportation pump, the two-phase fluid flows in from the direction of the water inlet edge, and flows out of the spiral axial flow type oil-gas mixed transportation pump in the direction of the water outlet edge after being acted by the blades; because the impeller rotates to cause that the pressure gradient is formed on the working surface of the blade and the back surface of the blade and the centrifugal force acts, separation power is provided for gas phase and liquid phase, the separation of the gas phase and the liquid phase is intensified, and the density of the gas phase is far less than that of the liquid phase, so that under the combined action of the centrifugal force and the pressure gradient, the gas phase with low density gradually moves to an adjacent surface area close to the hub, and the liquid phase with high density is gradually thrown to a rim area, so that the separation phenomenon of the gas phase and the liquid phase is formed in an impeller runner;
Introducing a thickening ratio coefficient xi which represents the intensity of the change of the blade thickness from the hub to the rim, and the expression is as follows:
On the basis of meeting the strength requirement of the hub and the process requirement of the wheel rim, the thickening ratio coefficient xi is enabled to be<1, i.e. maximum thickness δ at the adjacent face of the blade to the hubh maxLess than its maximum thickness delta at the rims maxdifferent thickening ratio coefficients correspond to different blade back molded lines, the molded lines of the working surface of the blade are consistent, the larger the thickening ratio coefficient is, the more the blade inclines towards the wheel rim,The smaller the thickening ratio coefficient is, the more the blade is inclined to the direction of the adjacent surface, and the thickening ratio coefficient xi is<1, the acting force of the back of the blade on the fluid is opposite to the centrifugal force direction in the radial component force direction, which is equivalent to the reduction of a part of gas-liquid separation power, so that the gas-liquid separation phenomenon and the gas aggregation phenomenon in a flow channel can be improved, the wing section of the impeller under the condition can well delay the gas-liquid separation phenomenon to a tail edge area, the gas-liquid separation phenomenon can not occur at the middle rear part of the impeller to cause the performance reduction of the mixed delivery pump, and simultaneously, the mixed delivery performance of the mixed delivery pump can be correspondingly improved due to the fact that the gas-liquid separation phenomenon in the flow channel is slowed down; the gas-liquid separation phenomenon and the gas aggregation phenomenon during two-phase flow are improved by adjusting the thickening ratio coefficient xi.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910873627.0A CN110578706A (en) | 2019-09-17 | 2019-09-17 | Super-separation type impeller of spiral axial-flow oil-gas mixed transportation pump |
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| CN201910873627.0A CN110578706A (en) | 2019-09-17 | 2019-09-17 | Super-separation type impeller of spiral axial-flow oil-gas mixed transportation pump |
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| CN110578706A true CN110578706A (en) | 2019-12-17 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN117366008A (en) * | 2023-10-31 | 2024-01-09 | 兰州理工大学 | Multiphase mixed transmission impeller with high light and heavy phase separation resistance |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0468877A1 (en) * | 1990-07-27 | 1992-01-29 | Institut Francais Du Petrole | Apparatus for multiphase pumping or compression and its application |
| JP2000230491A (en) * | 1998-12-08 | 2000-08-22 | Zojirushi Corp | Compact pump unit, electric thermo-pot and method of manufacturing lead screw for screw pump |
| CN103615409A (en) * | 2013-11-29 | 2014-03-05 | 湘潭泵业集团有限公司 | Multi-step segment-type oil-gas multiphase pump |
| US20150159619A1 (en) * | 2012-06-06 | 2015-06-11 | G.A.M. Manshanden Management B.V. | Ship Screw, Pump Screw or Turbine Screw |
| CN206280296U (en) * | 2016-12-06 | 2017-06-27 | 西华大学 | A kind of helico-axial oil and gas multiphase flow impeller of pump |
| CN109162956A (en) * | 2018-09-13 | 2019-01-08 | 清华大学 | A kind of T-type leaf top inhibiting pump internal lobe top tip leakage vortex and the pump with it |
-
2019
- 2019-09-17 CN CN201910873627.0A patent/CN110578706A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0468877A1 (en) * | 1990-07-27 | 1992-01-29 | Institut Francais Du Petrole | Apparatus for multiphase pumping or compression and its application |
| JP2000230491A (en) * | 1998-12-08 | 2000-08-22 | Zojirushi Corp | Compact pump unit, electric thermo-pot and method of manufacturing lead screw for screw pump |
| US20150159619A1 (en) * | 2012-06-06 | 2015-06-11 | G.A.M. Manshanden Management B.V. | Ship Screw, Pump Screw or Turbine Screw |
| CN103615409A (en) * | 2013-11-29 | 2014-03-05 | 湘潭泵业集团有限公司 | Multi-step segment-type oil-gas multiphase pump |
| CN206280296U (en) * | 2016-12-06 | 2017-06-27 | 西华大学 | A kind of helico-axial oil and gas multiphase flow impeller of pump |
| CN109162956A (en) * | 2018-09-13 | 2019-01-08 | 清华大学 | A kind of T-type leaf top inhibiting pump internal lobe top tip leakage vortex and the pump with it |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN117366008A (en) * | 2023-10-31 | 2024-01-09 | 兰州理工大学 | Multiphase mixed transmission impeller with high light and heavy phase separation resistance |
| CN117366008B (en) * | 2023-10-31 | 2024-03-12 | 兰州理工大学 | Multiphase mixed transmission impeller with high light and heavy phase separation resistance |
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Application publication date: 20191217 |
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