CN114962320B - Self-lubricating cooling circulation system for shaftless-driven deep sea mining mixed transportation pump - Google Patents
Self-lubricating cooling circulation system for shaftless-driven deep sea mining mixed transportation pump Download PDFInfo
- Publication number
- CN114962320B CN114962320B CN202210432934.7A CN202210432934A CN114962320B CN 114962320 B CN114962320 B CN 114962320B CN 202210432934 A CN202210432934 A CN 202210432934A CN 114962320 B CN114962320 B CN 114962320B
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- channel
- bearing
- guide vane
- pump
- fluid
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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
- F04D29/06—Lubrication
- F04D29/061—Lubrication especially adapted for liquid pumps
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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
- F04D13/00—Pumping installations or systems
- F04D13/02—Units comprising pumps and their driving means
- F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
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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
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/046—Bearings
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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
- F04D29/58—Cooling; Heating; Diminishing heat transfer
- F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
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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
- F04D29/70—Suction grids; Strainers; Dust separation; Cleaning
- F04D29/708—Suction grids; Strainers; Dust separation; Cleaning specially for liquid pumps
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Control Of Non-Positive-Displacement Pumps (AREA)
Abstract
The invention discloses a self-lubricating cooling circulation system for a shaftless-driven deep sea mining mixed transportation pump, which comprises a pump body and a guide vane channel positioned in the pump body, wherein a shell is arranged in the pump body and positioned at the top end of the guide vane channel, a motor is arranged in the shell, two sides of the motor are respectively provided with a first bearing and a second bearing which are matched with the motor, a thrust disc is arranged on one side, away from the first bearing, of the first bearing, a channel I is arranged at the position of the thrust disc, and a channel II connected with the channel I is arranged at the position of the opening of the guide vane outlet of the guide vane channel in the pump body. The beneficial effects are that: the fluid sequentially flows through the first bearing gap, the motor stator and rotor gap, the second upper bearing gap and the pump cavity before reaching the impeller, and when the pressure of the cavity is higher than the pressure of the outlet of the impeller, the fluid is led into the impeller flow passage area, so that cooling and lubrication circulation is realized.
Description
Technical Field
The invention relates to the technical field of deep sea mining mixed transportation pumps, in particular to a self-lubricating cooling circulation system for a shaftless driving deep sea mining mixed transportation pump.
Background
In the process of collecting and transporting particles in the deep sea, the motor and the stator and the rotor can generate heat rapidly by high-speed rotation driving, so that the service life is prolonged, the safety is improved, the energy consumption is reduced, and the heat is dissipated;
the bearing needs continuous lubrication, the traditional mining pump bearing is a sliding bearing, is arranged in each stage of space guide vane, has poor lubrication condition, and is difficult to realize external forced lubrication on land;
in a traditional space guide vane type mixing and conveying pump, dynamic sealing is difficult to implement between hydraulic stages, potential safety hazards are easy to generate when conveyed small particles enter a dynamic gap and a static gap, and gap sealing is an important technical challenge.
For the problems in the related art, no effective solution has been proposed at present.
Disclosure of Invention
Aiming at the problems in the related art, the invention provides a self-lubricating cooling circulation system for a shaftless-driven deep sea mining mixed transportation pump, so as to overcome the technical problems in the prior art.
For this purpose, the invention adopts the following specific technical scheme:
a self-lubricating cooling circulation system for shaftless drive deep sea mining mixed transportation pump, includes the pump body and is located the guide vane passageway in the pump body, just be located in the pump body the top of guide vane passageway is equipped with the casing, be equipped with the motor in the casing, the both sides of motor are equipped with respectively rather than matched with bearing one and bearing two, bearing one with one side that bearing two kept away from each other all is equipped with thrust disk, the casing is located thrust disk department has seted up passageway one, just be located in the pump body the guide vane exit opening of guide vane passageway be equipped with passageway two that the passageway is connected, be equipped with rather than matched filter on the passageway two.
Preferably, the thrust disc 7 is provided with a through hole 11, a plurality of evenly distributed channels three 12 are formed in the thrust disc 7, two ends of the channels three 12 extend to the through hole 11 and the outer wall of the thrust disc 7 respectively, a moving lift can be generated in the channels three 12, the moving lift is represented by Hi, the cooling and lubricating conditions are that P2 is larger than P1, p2=p0+hi- Δh, the expression of Hi is adopted, P1 is the pressure of an impeller outlet, only P2 is larger than P1, lubrication can be performed normally, D is the outer diameter of the thrust disc through hole, and n is the rotating speed.
Preferably, an impeller front pump cavity is arranged in the pump body and positioned on one side of the second bearing, and a channel IV extending into the guide vane channel is arranged in the impeller front pump cavity.
Preferably, in order to calculate the drop pressure of each flow channel conveniently, the pressure change of each flow channel is marked.
Preferably, the pressure loss of the fluid through the conduit:λ=75/Re (metal tube).
Preferably, the pressure of the fluid after leaking from the gap of the previous hydraulic stage changes:
preferably, the fluid is forced to convect through the single phase fluid in the motor tube at a heat flow rate of: phi=ha (t) w -t f )。
Preferably, the heat transferred to the fluid by the motor is:
the beneficial effects of the invention are as follows: according to the hydraulic stage forward pressurization principle, high-pressure fluid is led out near the downstream guide vane outlet, filtered and returned to the second channel at the outer edge of the impeller at the upstream stage, then the drainage fluid sequentially flows through the first bearing gap, the first motor stator and rotor gap, the second upper bearing gap and reaches the pump cavity before the impeller under the driving of pressure difference, and when the pressure of the cavity is higher than the pressure of the impeller outlet, the drainage fluid enters the impeller flow channel area to realize cooling and lubrication circulation.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings that are needed in the embodiments will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.
FIG. 1 is a schematic structural view of a self-lubricating cooling circulation system for a shaftless driven deep sea mining pump in accordance with an embodiment of the present invention;
FIG. 2 is a schematic illustration of the structure of a thrust disc in a self-lubricating cooling circulation system for a shaftless driven deep sea mining pump in accordance with an embodiment of the present invention;
FIG. 3 is a flow chart of drainage in a self-lubricating cooling circulation system for a shaftless driven deep sea mining pump in accordance with an embodiment of the present invention;
FIG. 4 is a partial pressure diagram of a self-lubricating cooling circulation system for a shaftless driven deep sea mining pump in accordance with an embodiment of the present invention;
fig. 5 is a flow chart of a self-lubricating cooling circulation system for a shaftless driven deep sea mining hybrid pump in accordance with an embodiment of the present invention.
In the figure:
1. a pump body; 2. a guide vane passage; 3. a housing; 4. a motor; 5. a first bearing; 6. a second bearing; 7. a thrust plate; 8. a first channel; 9. a second channel; 10. a filter; 11. a through hole; 12. a third channel; 13. a front pump chamber of the impeller; 14. and a fourth channel.
Detailed Description
For the purpose of further illustrating the various embodiments, the present invention provides the accompanying drawings, which are a part of the disclosure of the present invention, and which are mainly used to illustrate the embodiments and, together with the description, serve to explain the principles of the embodiments, and with reference to these descriptions, one skilled in the art will recognize other possible implementations and advantages of the present invention, wherein elements are not drawn to scale, and like reference numerals are generally used to designate like elements.
According to an embodiment of the invention, a self-lubricating cooling circulation system for a shaftless driven deep sea mining mixing pump is provided.
Embodiment one;
as shown in fig. 1-5, the self-lubricating cooling circulation system for a shaftless-driven deep sea mining mixed transportation pump according to the embodiment of the invention comprises a pump body 1 and a guide vane channel 2 positioned in the pump body 1, wherein a shell 3 is arranged at the top end of the guide vane channel 2 in the pump body 1, a motor 4 is arranged in the shell 3, a matched bearing I5 and a bearing II 6 matched with the motor 4 are respectively arranged at two sides of the motor 4, a thrust disc 7 is arranged at one side, away from the bearing I5, of the bearing II 6, a channel I8 is arranged at the position of the thrust disc 7, a channel II 9 connected with the channel I8 is arranged in the pump body 1 and positioned at the opening of the guide vane outlet of the guide vane channel 2, and a filter 10 matched with the channel II 9 is arranged on the channel II.
Embodiment two;
as shown in fig. 1-5, the thrust disc 7 is provided with a through hole 11, a plurality of evenly distributed channels three 12 are provided in the thrust disc 7, two ends of the channels three 12 extend to the through hole 11 and the outer wall of the thrust disc 7 respectively, a moving lift can be generated in the channels three 12, the moving lift is represented by Hi, the cooling and lubrication condition is that P2 is larger than P1, the P2 = p0+ Hi- Δh, the expression of Hi is that the pressure of an impeller outlet is that the P1 is that the P2 is larger than P1, the lubrication can work normally, D is the outer diameter of the thrust disc through hole, n is the rotation speed, a pump cavity 13 before the impeller is arranged in the pump body 1 and positioned at one side of the bearing two 6, and a channel four 14 extending into the guide vane channel 2 is arranged in the pump cavity 13 before the impeller.
Embodiment three;
as shown in fig. 1-5, to facilitate calculation of the drop pressure of each flow channel, the pressure change of each flow channel is labeled, and the pressure loss of the fluid through the pipeline is:λ=75/Re (metal tube), pressure change of fluid after leakage from gap of previous hydraulic stage：/>Heat flow of fluid through forced convection heat transfer of single-phase fluid in motor tube: phi=ha (t) w -t f ). In order to ensure that the drainage fluid smoothly enters the impeller area, the flow resistance of each gap is required to be accurately calculated, a reasoning disc structure is arranged at the front end of the lower bearing when necessary, and a radial flow passage is arranged in the thrust disc. The drainage fluid rotates at a high speed in the radial flow channel to generate auxiliary lift, maintain the circulating pressure, comprehensively consider the geometric dimension of the gap and the heating value of the motor, determine the circulating flow, further correct the flow area of the circulating channel, and the upper bearing and the lower bearing can be angular contact bearings or radial bearings, and if the radial bearings are, the radial dimensions are required to be independently set.
Fourth embodiment;
as shown in fig. 1-the heat transferred to the fluid by the motor is:
p1 is the pressure loss of the fluid after it has passed through the filter:
p2 is the pressure loss of the fluid through the pipe:
p3 is the pressure change of the fluid after leaking from the gap of the previous hydraulic stage:
p4 is the pressure change of the fluid after passing through the thrust disc:
p5 is the pressure change of the fluid through the upper and lower bearing gaps:
p7 is the pressure change of the fluid through the stator-rotor gap:
p7 is the pressure change of the fluid after passing through the suction disc;
therefore, calculation is performed, fluid is pressurized through the thrust disc, the fluid smoothly enters the main runner at the position of the pressure P5> P6 of the pump cavity in front of the impeller, the thrust disc rotates along with the rotor system at a high speed, the fluid can acquire kinetic energy along with the rotation of the thrust disc after passing through the thrust disc, and the kinetic energy is pushed out by the thrust disc at a high speed, so that the pressure is increased.
In summary, by means of the technical scheme of the invention, according to the hydraulic stage forward pressurization principle, high-pressure fluid is led out near the downstream guide vane outlet, filtered and returned to the second channel 9 at the outer edge of the upstream impeller of the stage, and then the drainage fluid sequentially flows through the first bearing 5 gap, the motor stator-rotor gap, the second upper bearing 6 gap and reaches the front pump cavity of the impeller under the driving of pressure difference, and when the cavity pressure is greater than the impeller outlet pressure, the drainage fluid enters the impeller flow channel area to realize cooling and lubrication circulation.
The foregoing description of the preferred embodiments of the invention is not intended to be limiting, but rather is intended to cover all modifications, equivalents, alternatives, and improvements that fall within the spirit and scope of the invention.
Claims (3)
1. A self-lubricating cooling circulation system for a shaftless-driven deep sea mining mixed transportation pump is characterized by comprising a pump body (1) and a guide vane channel (2) positioned in the pump body (1), wherein a shell (3) is arranged at the top end of the guide vane channel (2) in the pump body (1), a motor (4) is arranged in the shell (3), a first bearing (5) and a second bearing (6) which are matched with the motor (4) are respectively arranged at two sides of the motor (4), thrust discs (7) are respectively arranged at one side, far away from each other, of the first bearing (5) and the second bearing (6), a channel (8) is arranged at the position of the first thrust disc (7), a channel two (9) which is connected with the channel one (8) is arranged in the pump body (1) and positioned at the guide vane outlet of the guide vane channel (2), a filter (10) which is matched with the channel two (9) is arranged on the channel two, through holes (11) are respectively arranged on the thrust discs (7), a plurality of through holes (12) are uniformly distributed in the thrust discs (7), a plurality of through holes (12) are respectively arranged at the two ends of the thrust discs (12) which are respectively extended to the three through holes (12), an impeller front pump cavity (13) is arranged in the pump body (1) and positioned on one side of the second bearing (6), and a channel IV (14) extending into the guide vane channel (2) is arranged in the impeller front pump cavity (13).
2. A self-lubricating cooling circulation system for a shaftless driven deep sea mining pump according to claim 1, whichCharacterized in that the pressure loss of the fluid through the pipe:where λ is the along-the-path friction coefficient, ρ is the fluid density, ν is the average velocity in the tube, l is the tube length, and d is the tube diameter.
3. A self-lubricating cooling circulation system for a shaftless driven deep sea mining pump according to claim 2, wherein the fluid is forced convected heat transfer through single phase fluid in the motor tube: phi=ha (t) w -t f ) Wherein phi is the heat transfer rate, h is the heat transfer coefficient, t w Is the wall temperature, t f Is the fluid temperature.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210432934.7A CN114962320B (en) | 2022-04-22 | 2022-04-22 | Self-lubricating cooling circulation system for shaftless-driven deep sea mining mixed transportation pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210432934.7A CN114962320B (en) | 2022-04-22 | 2022-04-22 | Self-lubricating cooling circulation system for shaftless-driven deep sea mining mixed transportation pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN114962320A CN114962320A (en) | 2022-08-30 |
| CN114962320B true CN114962320B (en) | 2023-09-22 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202210432934.7A Active CN114962320B (en) | 2022-04-22 | 2022-04-22 | Self-lubricating cooling circulation system for shaftless-driven deep sea mining mixed transportation pump |
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| CN (1) | CN114962320B (en) |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1257165A (en) * | 1998-12-17 | 2000-06-21 | 沈阳机电研究设计院 | Combined motor pump |
| JP2002130191A (en) * | 2000-10-24 | 2002-05-09 | Ebara Corp | Submerged motor pump |
| CN102003396A (en) * | 2010-12-14 | 2011-04-06 | 四川润德机电技术有限公司 | Self-cooling guide vane downdraft type submersible pump |
| DE102011117183A1 (en) * | 2011-10-28 | 2012-08-02 | Ruhrpumpen Gmbh | Conveying element e.g. magnetic drive pump has connecting bore which is correspondingly connected with through-hole of shaft |
| CN103261705A (en) * | 2010-08-25 | 2013-08-21 | 麦格纳动力系有限公司 | Electric water pump with stator cooling |
| CN107387424A (en) * | 2017-07-28 | 2017-11-24 | 江苏大学 | A kind of canned motor pump with forcing functions lubricating function |
| CN209494720U (en) * | 2018-11-21 | 2019-10-15 | 兴城市水泵制造有限公司 | Directly drive shaftless blade electric pump |
| CN112460031A (en) * | 2019-11-28 | 2021-03-09 | 江苏大学 | Impeller built-in high-speed centrifugal pump |
-
2022
- 2022-04-22 CN CN202210432934.7A patent/CN114962320B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1257165A (en) * | 1998-12-17 | 2000-06-21 | 沈阳机电研究设计院 | Combined motor pump |
| JP2002130191A (en) * | 2000-10-24 | 2002-05-09 | Ebara Corp | Submerged motor pump |
| CN103261705A (en) * | 2010-08-25 | 2013-08-21 | 麦格纳动力系有限公司 | Electric water pump with stator cooling |
| CN102003396A (en) * | 2010-12-14 | 2011-04-06 | 四川润德机电技术有限公司 | Self-cooling guide vane downdraft type submersible pump |
| DE102011117183A1 (en) * | 2011-10-28 | 2012-08-02 | Ruhrpumpen Gmbh | Conveying element e.g. magnetic drive pump has connecting bore which is correspondingly connected with through-hole of shaft |
| CN107387424A (en) * | 2017-07-28 | 2017-11-24 | 江苏大学 | A kind of canned motor pump with forcing functions lubricating function |
| CN209494720U (en) * | 2018-11-21 | 2019-10-15 | 兴城市水泵制造有限公司 | Directly drive shaftless blade electric pump |
| CN112460031A (en) * | 2019-11-28 | 2021-03-09 | 江苏大学 | Impeller built-in high-speed centrifugal pump |
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| Publication number | Publication date |
|---|---|
| CN114962320A (en) | 2022-08-30 |
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