CN205172798U - Turbodrill cavity motor with balanced hub of axial force - Google Patents
Turbodrill cavity motor with balanced hub of axial force Download PDFInfo
- Publication number
- CN205172798U CN205172798U CN201520928363.1U CN201520928363U CN205172798U CN 205172798 U CN205172798 U CN 205172798U CN 201520928363 U CN201520928363 U CN 201520928363U CN 205172798 U CN205172798 U CN 205172798U
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- balance hub
- bearing
- turbine
- overcoat
- hub
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- 238000000034 method Methods 0.000 claims description 12
- 238000005553 drilling Methods 0.000 claims description 10
- 230000004323 axial length Effects 0.000 claims description 9
- 230000033558 biomineral tissue development Effects 0.000 claims description 3
- 230000003068 static effect Effects 0.000 claims description 3
- 108700041286 delta Proteins 0.000 claims 2
- 125000004122 cyclic group Chemical group 0.000 abstract 2
- 239000012224 working solution Substances 0.000 description 15
- 239000012530 fluid Substances 0.000 description 4
- 238000010586 diagram Methods 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- 239000011159 matrix material Substances 0.000 description 1
- 230000002028 premature Effects 0.000 description 1
- 239000011435 rock Substances 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
Classifications
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/20—Hydro energy
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- Turbine Rotor Nozzle Sealing (AREA)
Abstract
The utility model provides a turbodrill cavity motor with balanced hub of axial force, belongs to shaft boring machine technical field, and it is equipped with lock nut, balanced hub, turbine motor main shaft, upward holds up radially that positive axial holds, turbine rotor, turbine stator and radially hold up positive axial to hold down, lock nut joins in marriage the dress in the upper end of turbine motor main shaft, and lock nut is hollow structure with the turbine motor main shaft, balanced hub, upward hold up radially that positive axial holds, the turbine rotor and radially hold up down positive axial hold from last to down in proper order the suit on the turbine motor main shaft, the balanced hub overcoat inner wall and the lock nut up end of balanced hub form the pressure balance chamber, form cyclic annular gap between balanced hub overcoat and balanced hub endotheca, on radially hold up positive axial to hold between bearing endotheca and bearing overcoat to form the bearing fit clearance, the hollow structure of bearing fit clearance, cyclic annular gap, pressure balance chamber, lock nut and turbine motor main shaft link up. The utility model provides a turbine motor main shaft axial force and the unbalanced problem of weight on bit.
Description
Technical field
The utility model relates to a kind of probing turbodrill, and especially a kind of turbodrill hollow motor with axial force balance hub, belongs to drilling equipment technical field.
Background technique
TURBODRILLING TECHNIQUE WITH TREMENDOUS TECHNICAL can reduce energy consumption, reduce costs, and has good economic and social profit, is one of drilling project field cutting edge technology.Turbodrill is commercial Application a kind of mud motor the earliest, and its working principle is the rotating machinery energy hydrodynamic pressure energy of working solution being changed into output shaft, drives drill bit rotational with broken downhole formation rock.
Turbodrill take turbine motor as power section, with turbine motor main shaft for supporting part, turbine motor main shaft is provided with thrust bearing group, and during drillng operation, turbine motor main shaft will bear axial force and the pressure of the drill.In prior art, when turbodrill is in running order, the working solution with certain pressure enters turbine motor active chamber by turbodrill upper end, drive the rotor of turbine motor and turbine motor spindle operation by hydraudynamic drive, the axial force that now turbine motor main shaft is subject to comprises the downward axial force that working solution is caused by the downward axial force that produces during turbine motor rotor, turbine motor main shaft top and bottom pressure reduction.For large scale turbodrill, the downward axial force be subject to due to turbine motor main bearing is usually much larger than the pressure of the drill, there is unbalanced problem in the axial force that turbine motor main bearing is subject to and the pressure of the drill, very easily causes the thrust bearing group premature failure on turbine motor main shaft.
Model utility content
The purpose of this utility model is the drawback for prior art, a kind of turbodrill hollow motor with axial force balance hub is provided, to solve the axial force and the unbalanced problem of the pressure of the drill that large scale turbodrill turbine motor main bearing is subject to, extend the operating life of turbodrill.
The utility model above-mentioned purpose is achieved through the following technical solutions:
With a turbodrill hollow motor for axial force balance hub, comprise upper connection, locking nut, balance hub, turbine motor main shaft, upper radial alignment bearing, turbine rotor, turbine stator, turbine motor housing, lower radial alignment bearing and lower contact; Described locking nut and turbine motor main shaft are hollow structure, and locking nut is fitted in the upper end of turbine motor main shaft; Described balance hub, upper radial alignment bearing, turbine rotor and lower radial alignment bearing are sleeved on the outside of turbine motor main shaft from top to bottom successively; Described balance hub is made up of balance hub overcoat and balance hub inner sleeve, the outer set upper side of described balance hub is provided with end cap, mineralization pressure counter balance pocket between balance hub outer casing inner wall and locking nut upper-end surface, balance hub overcoat and balance hub inner sleeve are assembled with gap fiting mode, between balance hub overcoat and balance hub inner sleeve, form annular slot; Described radial alignment bearing is made up of bearing inner sleeve and bearing outside, forms bearing fit gap between bearing inner sleeve and bearing outside; The hollow structure of described bearing fit gap, annular slot, pressure balance chamber, locking nut and turbine motor main shaft is through in a series arrangement.
The above-mentioned turbodrill hollow motor with axial force balance hub, described balance hub inner sleeve, upper radial alignment bearing inner sleeve, turbine rotor and lower radial alignment bearing inner sleeve are compressed by the shaft shoulder end face of locking nut and turbine motor main shaft bottom, become the entirety rotated with turbine rotor; Described balance hub overcoat, upper radial alignment bearing overcoat, turbine stator and lower radial alignment bearing overcoat are compressed by upper connection, lower contact and turbine motor housing end face, become a static entirety.
The above-mentioned turbodrill hollow motor with axial force balance hub, is enclosed within end cap outside described balance hub and is provided with shoulder hole, and the in-core pipe assembly of getting in described shoulder hole and wire line coring drilling process matches.
The above-mentioned turbodrill hollow motor with axial force balance hub, described balance hub outer casing internal diameter is D1, and balance hub inner sleeve external diameter is D2, the annular slot width formed between balance hub overcoat and balance hub inner sleeve
Δ 1=(D1-D2)/2, and 0.20mm≤Δ 1≤1.00mm, the axial length L 1 >=200mm of balance hub overcoat, the axial length L 2 >=150mm of balance hub inner sleeve.
The above-mentioned turbodrill hollow motor with axial force balance hub, axial length L 3 >=the 60mm of described radial alignment bearing, the matching gap Δ 2=(D3-D4 of the outer diameter D 4 of the internal diameter D3 of the bearing outside of upper radial alignment bearing and the bearing inner sleeve of upper radial alignment bearing)/2, and 0.20mm≤Δ 2≤1.00mm.
The above-mentioned turbodrill hollow motor with axial force balance hub, diameter of bore D3 >=Φ 20mm of described motor spindle hollow structure.
The utility model is provided with axial force balance hub in probing turbodrill hollow motor, this axial force balance hub is made up of balance hub overcoat and balance hub inner sleeve, balance hub overcoat and balance hub inner sleeve are assembled with gap fiting mode, annular slot is defined between balance hub overcoat and balance hub inner sleeve, simultaneously between balance hub outer casing inner wall and locking nut upper-end surface, define pressure balance chamber, the endoporus of the bearing fit gap of annular slot and upper radial alignment bearing, pressure balance chamber, locking nut and turbine motor main shaft is through.Therefore, when drilling turbodrill hollow motor and being in running order, when the working solution with certain pressure enters turbine motor active chamber by turbodrill upper end, a small amount of working solution is by upper radial alignment bearing lower end surface, pressure balance chamber is entered by the bearing fit gap of upper radial alignment bearing, the annular slot between balance hub overcoat and balance hub inner sleeve, arrive lower contact by the endoporus of locking nut and turbine motor main shaft again, converge with the working solution by turbine motor active chamber (turbine stator leaf grating gap and turbine rotor leaf grating gap).According to hydromechanical expenditure and pressure principle, in above-mentioned working procedure, flow through the bearing fit gap of radial alignment bearing, annular slot between balance hub overcoat and balance hub inner sleeve, a small amount of working fluid pressure of entering pressure balance chamber can be subject to very large loss, therefore passed to the axial pressure meeting significantly reduction of turbine motor main shaft by locking nut upper-end surface, the downward axial force caused because of turbine motor main shaft top and bottom pressure reduction is very little.Prove through test: compared with the prior art, certain adopts the turbodrill of axial force balance hub, and the axial force that its turbine motor main shaft is subject to can reduce more than 68%.
In sum, the utility model alleviates the axial force and the unbalanced problem of the pressure of the drill that turbine motor main bearing is subject to effectively, extends the operating life of turbodrill.
Accompanying drawing explanation
Fig. 1 is cross-sectional view of the present utility model;
Fig. 2 is the cross-sectional view of axial force balance hub;
Fig. 3 is I place schematic enlarged-scale view in Fig. 2;
Fig. 4 is A-A cross-sectional view in Fig. 2;
Fig. 5 is upper radial alignment bearing cross-sectional view;
Fig. 6 is J place schematic enlarged-scale view in Fig. 5;
Fig. 7 is the working principle schematic diagram of the utility model in conventional drilling process;
Fig. 8 is the cross-sectional view of the axial force balance hub mated with wire line coring drilling process;
Fig. 9 is the working principle schematic diagram of the utility model in wire line coring drilling process.
In figure, each list of reference numerals is: 1, upper connection, 2, locking nut, 3, turbine motor main shaft, 4, axial force balance hub, 4-1, balance hub overcoat, 4-2, balance hub inner sleeve, 4-3, annular slot, 4-4, shoulder hole, 5, upper radial alignment bearing, 5-1, bearing outside, 5-2, bearing inner sleeve, 5-3, bearing fit gap, 6, turbine stator, 7, turbine rotor, 8, turbine motor housing, 9, lower radial alignment bearing, 10, lower contact, 11, working solution, 12, get in-core pipe assembly;
H, pressure balance chamber.
Embodiment
Below in conjunction with the drawings and specific embodiments, the utility model is described in further detail.
Referring to Fig. 1 to Fig. 6, the turbodrill hollow motor with axial force balance hub described in the utility model comprises upper connection 1, locking nut 2, balance hub 4, turbine motor main shaft 3, upper radial alignment bearing 5, turbine rotor 7, turbine stator 6, turbine motor housing 8, lower radial alignment bearing 9 and lower contact 10; Described locking nut 2 is hollow structure with turbine motor main shaft 3, and locking nut 2 is fitted in the upper end of turbine motor main shaft 3; Described balance hub 4, upper radial alignment bearing 5, turbine rotor 7 and lower radial alignment bearing 9 are sleeved on the outside of turbine motor main shaft 3 from top to bottom successively; Described balance hub 4 is made up of balance hub overcoat 4-1 and balance hub inner sleeve 4-2, described balance hub overcoat 4-1 upper end is provided with end cap, mineralization pressure counter balance pocket H between balance hub outer casing inner wall and locking nut upper-end surface, balance hub overcoat 4-1 and balance hub inner sleeve 4-2 assembles with gap fiting mode, forms annular slot 4-3 between balance hub overcoat 4-1 and balance hub inner sleeve 4-2; Described radial alignment bearing 5 is made up of bearing inner sleeve 5-2 and bearing outside 5-1, forms bearing fit gap 5-3 between bearing inner sleeve 5-2 and bearing outside 5-1; The hollow structure of described bearing fit gap 5-3, annular slot 4-3, pressure balance chamber H, locking nut and turbine motor main shaft is through in a series arrangement; The inner sleeve of described balance hub inner sleeve 4-2, upper radial alignment bearing inner sleeve 5-2, turbine rotor 7 and lower radial alignment bearing 9 is compressed by the shaft shoulder end face of locking nut 2 with turbine motor main shaft 3 bottom, becomes the entirety rotated with turbine rotor; The overcoat of described balance hub overcoat 4-1, upper radial alignment bearing overcoat 5-1, turbine stator 6 and lower radial alignment bearing 9 is compressed with turbine motor housing 8 end face by upper connection 1, lower contact 10, becomes a static entirety.
Referring to Fig. 7, when turbodrill hollow motor is in running order, before the working solution 11 with certain pressure enters turbine motor active chamber by turbodrill upper end, a small amount of working solution is by upper radial alignment bearing 5 lower end surface, pressure balance chamber H is entered by the bearing fit gap 5-3 of upper radial alignment bearing 5, the annular slot 4-3 between balance hub overcoat 4-1 and balance hub inner sleeve 4-2, arrive lower contact 10 by the endoporus of locking nut 2 and turbine motor main shaft 3 again, converge with the working solution by turbine motor active chamber.According to hydromechanical expenditure and pressure principle, in above-mentioned working procedure, flow through the bearing fit gap 5-3 of radial alignment bearing 5, annular slot 4-3 between balance hub overcoat 4-1 and balance hub inner sleeve 4-2, enter a small amount of working fluid pressure of pressure balance chamber H and can be subject to very large loss, therefore passed to the axial pressure meeting significantly reduction of turbine motor main shaft 3 by locking nut 2 upper-end surface, the downward axial force caused because of turbine motor main shaft 3 top and bottom pressure reduction is very little.Such as: a kind of integral shroud external diameter of turbine rotor 7 is 220mm, turbine rotor 7 matrix external diameter is the turbodrill of 158mm, when adopting prior art, the axial force that turbine motor main shaft 3 is subject to is 288.10kN, wherein working solution is 92.03kN by the downward axial force produced during turbine motor turbine rotor, the Yin Mada pressure drop of turbine motor main shaft 3 top and bottom (
=10MPa) the downward axial force that produces is 196.07kN.To above-mentioned turbodrill configuration axial force balance hub 4, make the bearing outside 5-1 internal diameter D3=158.3mm of radial alignment bearing 5 on it, the outer diameter D 4=158mm of bearing inner sleeve 5-2, the axial length L 3=100mm of upper radial alignment bearing 5, the internal diameter D5=158.35mm of balance hub overcoat 4-1, the outer diameter D 2=158mm of balance hub inner sleeve 4-2, the axial length L 1=400mm of balance hub overcoat 4-1, the axial length L 2=300mm of balance hub inner sleeve 4-2; By the axial force balance effect of axial force balance hub 4, the working fluid pressure that turbine motor main shaft 3 upper/lower terminal of this turbodrill bears is very small, can ignore, the axial force that now turbine motor main shaft 3 is subject to only comprises the downward axial force of working solution 11 by producing during turbine motor turbine rotor, and size is 92.03kN; As can be seen here, compared with the prior art, adopt the turbodrill of axial force balance hub, the axial force that its turbine motor main shaft is subject to can reduce more than 68%.
Referring to Fig. 8, Fig. 9, described in the utility model with in the turbodrill hollow motor of axial force balance hub, another embodiment of described balance hub 4 is the structure of mating with wire line coring drilling process, this embodiment is provided with shoulder hole 4-4 on the end cap of balance hub overcoat 4-1, described shoulder hole 4-4 gets in-core pipe assembly 12 for assembling in wire line coring drilling process, its working principle is: when drill turbodrill hollow motor carry out wire line coring creep into time, before the working solution 11 with certain pressure enters turbine motor active chamber by turbodrill upper end, a small amount of working solution is by upper radial alignment bearing 5 lower end surface, by the bearing fit gap 5-3 of upper radial alignment bearing 5, annular slot 4-3 between balance hub overcoat 4-1 and balance hub inner sleeve 4-2 enters pressure balance chamber H, lower contact 10 is arrived with the gap of getting in-core pipe assembly 12 again by the endoporus of locking nut 2 and turbine motor main shaft 3, converge with the working solution by turbine motor active chamber.According to hydromechanical expenditure and pressure principle, in above-mentioned working procedure, flow through the bearing fit gap 5-3 of radial alignment bearing 5, annular slot 4-3 between balance hub overcoat 4-1 and balance hub inner sleeve 4-2, enter a small amount of working fluid pressure of pressure balance chamber H and can be subject to very large loss, the axial pressure being passed to turbine motor main shaft 3 by locking nut 2 upper-end surface can significantly reduce, and therefore the pressure reduction downward axial force that causes in turbine motor main shaft 3 top and bottom is very little.
Claims (6)
1. the turbodrill hollow motor with axial force balance hub, it is characterized in that, the described turbodrill hollow motor with axial force balance hub comprises upper connection (1), locking nut (2), balance hub (4), turbine motor main shaft (3), upper radial alignment bearing (5), turbine rotor (7), turbine stator (6), turbine motor housing (8), lower radial alignment bearing (9) and lower contact (10); Described locking nut (2) and turbine motor main shaft (3) are hollow structure, and locking nut (2) is fitted in the upper end of turbine motor main shaft (3); Described balance hub (4), upper radial alignment bearing (5), turbine rotor (7) and lower radial alignment bearing (9) are sleeved on the outside of turbine motor main shaft (3) from top to bottom successively; Described balance hub (4) is made up of balance hub overcoat (4-1) and balance hub inner sleeve (4-2), described balance hub overcoat (4-1) upper end is provided with end cap, mineralization pressure counter balance pocket (H) between balance hub outer casing inner wall and locking nut upper-end surface, balance hub overcoat (4-1) and balance hub inner sleeve (4-2), with gap fiting mode assembling, form annular slot (4-3) between balance hub overcoat (4-1) and balance hub inner sleeve (4-2); Described radial alignment bearing (5) is made up of bearing inner sleeve (5-2) and bearing outside (5-1), forms bearing fit gap (5-3) between bearing inner sleeve (5-2) and bearing outside (5-1); The hollow structure of described bearing fit gap (5-3), annular slot (4-3), pressure balance chamber (H), locking nut and turbine motor main shaft is through in a series arrangement.
2. the turbodrill hollow motor with axial force balance hub according to claim 1, it is characterized in that, the inner sleeve of described balance hub inner sleeve (4-2), upper radial alignment bearing inner sleeve (5-2), turbine rotor (7) and lower radial alignment bearing (9) is compressed by the shaft shoulder end face of locking nut (2) with turbine motor main shaft (3) bottom, becomes the entirety with turbine rotor rotation; The overcoat of described balance hub overcoat (4-1), upper radial alignment bearing overcoat (5-1), turbine stator (6) and lower radial alignment bearing (9) is compressed with turbine motor housing (8) end face by upper connection (1), lower contact (10), becomes a static entirety.
3. the turbodrill hollow motor with axial force balance hub according to claim 2, it is characterized in that, described balance hub overcoat (4-1) is provided with shoulder hole (4-4) on end cap, and described shoulder hole (4-4) matches with the in-core pipe assembly (12) of getting in wire line coring drilling process.
4. the turbodrill hollow motor with axial force balance hub according to claim 1 or 2 or 3, it is characterized in that, described balance hub overcoat (4-1) internal diameter is D1, balance hub inner sleeve (4-2) external diameter is D2, the width Delta 1=(D1-D2 of the annular slot (4-3) formed between balance hub overcoat (4-1) and balance hub inner sleeve (4-2))/2, and 0.20mm≤Δ 1≤1.00mm, axial length L 1 >=the 200mm of balance hub overcoat (4-1), the axial length L 2 >=150mm of balance hub inner sleeve (4-2).
5. the turbodrill hollow motor with axial force balance hub according to claim 4, it is characterized in that, axial length L 3 >=the 60mm of described radial alignment bearing (5), bearing outside (5-1) the internal diameter D3 of upper radial alignment bearing (5) and the matching gap Δ 2=(D3-D4 of bearing inner sleeve (5-2) outer diameter D 4)/2, and 0.20mm≤Δ 2≤1.00mm.
6. the turbodrill hollow motor with axial force balance hub according to claim 5, is characterized in that, diameter of bore D3 >=Φ 20mm of described motor spindle (3).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520928363.1U CN205172798U (en) | 2015-11-20 | 2015-11-20 | Turbodrill cavity motor with balanced hub of axial force |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520928363.1U CN205172798U (en) | 2015-11-20 | 2015-11-20 | Turbodrill cavity motor with balanced hub of axial force |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN205172798U true CN205172798U (en) | 2016-04-20 |
Family
ID=55736800
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201520928363.1U Expired - Fee Related CN205172798U (en) | 2015-11-20 | 2015-11-20 | Turbodrill cavity motor with balanced hub of axial force |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN205172798U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105275720A (en) * | 2015-11-20 | 2016-01-27 | 北京春仑石油技术开发有限公司 | Turbodrill hollow motor with axial force balance hub |
| CN112324335A (en) * | 2020-10-30 | 2021-02-05 | 中国地质大学（武汉） | Rope core-taking turbine drilling tool for geological exploration of horizontal directional drilling engineering |
| CN115749581A (en) * | 2022-12-09 | 2023-03-07 | 北京探矿工程研究所 | Anti-braking anti-falling large-torque turbine drilling tool |
-
2015
- 2015-11-20 CN CN201520928363.1U patent/CN205172798U/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105275720A (en) * | 2015-11-20 | 2016-01-27 | 北京春仑石油技术开发有限公司 | Turbodrill hollow motor with axial force balance hub |
| CN112324335A (en) * | 2020-10-30 | 2021-02-05 | 中国地质大学（武汉） | Rope core-taking turbine drilling tool for geological exploration of horizontal directional drilling engineering |
| CN115749581A (en) * | 2022-12-09 | 2023-03-07 | 北京探矿工程研究所 | Anti-braking anti-falling large-torque turbine drilling tool |
| CN115749581B (en) * | 2022-12-09 | 2023-09-12 | 北京探矿工程研究所 | Prevent braking and prevent falling big moment of torsion turbine drilling tool |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20160420 |