CN109025804B - Turbine type axial impactor - Google Patents
Turbine type axial impactor Download PDFInfo
- Publication number
- CN109025804B CN109025804B CN201811179645.0A CN201811179645A CN109025804B CN 109025804 B CN109025804 B CN 109025804B CN 201811179645 A CN201811179645 A CN 201811179645A CN 109025804 B CN109025804 B CN 109025804B
- Authority
- CN
- China
- Prior art keywords
- overflowing
- turbine
- joint
- turbine rotor
- impact
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 239000012530 fluid Substances 0.000 claims abstract description 20
- 230000005540 biological transmission Effects 0.000 claims abstract description 15
- 239000007788 liquid Substances 0.000 claims description 28
- 230000001681 protective Effects 0.000 claims description 3
- 230000000694 effects Effects 0.000 abstract description 4
- 238000005553 drilling Methods 0.000 description 13
- 230000001965 increased Effects 0.000 description 7
- 238000000034 method Methods 0.000 description 5
- 239000011435 rock Substances 0.000 description 5
- 210000002445 Nipples Anatomy 0.000 description 2
- 230000000875 corresponding Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 230000000737 periodic Effects 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 230000003139 buffering Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 239000007789 gas Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000003345 natural gas Substances 0.000 description 1
- 239000003129 oil well Substances 0.000 description 1
- 239000003209 petroleum derivative Substances 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 230000000087 stabilizing Effects 0.000 description 1
Classifications
-
- E—FIXED CONSTRUCTIONS
- E21—EARTH DRILLING; MINING
- E21B—EARTH DRILLING, e.g. DEEP DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B4/00—Drives for drilling, used in the borehole
- E21B4/06—Down-hole impacting means, e.g. hammers
- E21B4/14—Fluid operated hammers
Abstract
The invention relates to a turbine type axial impactor, wherein the upper end of a main short circuit of the turbine type axial impactor is connected with a double female joint, the lower end of the main short circuit is connected with an impact joint through a hexagonal sleeve, a hollow cavity of the impact joint is positioned in the main short circuit, an overflowing cover head of an overflowing cover plate is seated at the upper port of the hollow cavity of the impact joint, an overflowing channel of the overflowing cover plate is inserted into the hollow cavity, a piston hammer is of a three-section type hollow cylindrical structure and positioned in an annular space between the hollow cavity and the overflowing channel, a transmission cylinder of a turbine rotor is inserted into the overflowing channel, an annular table in the turbine rotor is seated on the overflowing cover head of the overflowing cover plate, the upper end of the turbine rotor is connected with a jet stator, and the jet stator is pressed at the lower port of the double female joint; the inside of the jet flow stator is provided with oblique perforation holes, and when fluid passes through the oblique perforation holes, the jet flow hits turbine blades of the turbine rotor, so that the turbine rotor rotates. The invention can generate good longitudinal vibration on the drill bit, and the speed-up effect is very obvious.
Description
The technical field is as follows:
the invention relates to a downhole hydraulic impact tool used in the petroleum and natural gas drilling process, in particular to a turbine type axial impactor.
Background art:
with the progress of exploration and development technology, the depth of oil and gas wells is continuously increased, and the number of deep wells and ultra-deep wells is increased. The hardness of deep stratum rock is high, and the drillability grade value is high, and the drilling difficulty is increased, the mechanical drilling speed is slowed down, and the drilling cost is increased. The drilling difficulty of hard stratum becomes more and more prominent, the efficient rock breaking technology is more important, the quality of the rock breaking efficiency directly determines the speed and the cost of drilling, and the economic benefit of drilling engineering is determined. It can be known from laboratory experiments and field practice that when certain periodic impact force acts on the drill bit, the rock breaking efficiency of the drill bit is remarkably increased, so that the mechanical drilling speed is improved.
The axial impactor is used as a power tool for assisting in breaking rock underground, receives more and more attention from the industry because extra energy does not need to be provided, and gradually becomes an indispensable technical means for accelerating the speed of a deep well. Although various impactors are proved to improve the drilling efficiency in field tests, the impactors have the defects of short service life, easy influence of the performance of drilling fluid and the like, so that the impactors are not widely applied to the operation of drilling machines.
The invention content is as follows:
the invention aims to provide a turbine type axial impactor which is used for solving the problems of low drilling speed, low tool impact efficiency and the like caused by the fact that the depth of an oil well is increased continuously.
The technical scheme adopted by the invention for solving the technical problems is as follows: the turbine type axial impactor of the turbine type axial impactor comprises a double female connector, a main body short connector, a hexagonal sleeve, an impact connector, a jet flow stator, a turbine rotor, an overflowing cover plate and a piston hammer, wherein the upper end of the main body short connector is connected with the double female connector, the lower end of the main body short connector is connected with the impact connector through the hexagonal sleeve, a hollow cavity of the impact connector is positioned in the main body short connector, an overflowing cover head of the overflowing cover plate is seated at an upper port of the hollow cavity of the impact connector, an overflowing channel of the overflowing cover plate is inserted into the hollow cavity, the piston hammer is of a three-section type hollow cylindrical structure, the piston hammer is positioned in an annular space between the hollow cavity and the overflowing channel, a transmission cylinder of the turbine rotor is inserted into the overflowing channel, an annular platform in the turbine rotor is seated on the overflowing cover head of the overflowing cover plate, the upper end of the turbine; the jet flow stator is internally provided with oblique perforation holes, and when fluid passes through the oblique perforation holes, the jet flow hits turbine blades of the turbine rotor, so that the turbine rotor rotates;
the transmission cylinder is hollow, the transmission cylinder above the annular table is provided with an inflow hole, the transmission cylinder below the annular table is provided with a first circulation hole and a second circulation hole, the overflowing channel is correspondingly provided with a first overflowing hole and a second overflowing hole, and the hollow cavity is correspondingly provided with a first liquid outlet hole and a second liquid outlet hole.
In the scheme, the jet flow stator is clamped at the female buckle of the main body short circuit, and the annular elastic body is arranged between the jet flow stator and the double female joint so as to slow down the impact of the reverse force formed by the jet flow on the double female joint; an oblique clamping groove with an oblique outer contour is formed at the outlet end of the oblique perforation of the jet flow stator and matched with a turbine blade of the turbine rotor; the center of the jet flow stator is provided with a limit groove, and a limit column at the upper end of the turbine rotor is inserted into the limit groove, so that the turbine rotor does not move radially or axially.
The lower edge of the turbine rotor limiting column in the scheme is provided with the protective ring, and the protective ring is used for reducing friction between the turbine rotor and the jet flow stator in the rotating process.
In the above solution, the impact joint has a relief hole at the bottom of the hollow cavity, from which fluid can flow out of the hollow cavity, thereby reducing the pressure in the hollow cavity; a liquid outlet channel is arranged in the middle of the impact joint, a confluence channel is arranged on the impact joint below the liquid outlet channel, and fluid from the first liquid outlet hole and the second liquid outlet hole can flow into the confluence channel from the confluence channel; a steady flow channel is arranged between the pressure reducing hole and the liquid outlet channel, so as to lead the fluid to form a stable state; there is a section of hexagonal to connect outside impact joint, and the hexagonal connects and is identical with the inside of hexagonal cover, and fixed impact connects, and the sharp-pointed department of hexagonal connects has the chamfer, in order to reduce the wearing and tearing in the vibration process.
In the scheme, the outside of the impact joint is provided with a clamping ring groove for placing a half-ring to achieve the effect of fixing the impact joint; the lower end of the clamping ring groove is provided with a T-shaped step for installing an elastic body and buffering the movement of the impact joint.
In the scheme, the jet flow stator has 1-7 oblique perforation holes.
The turbine rotor in the scheme has 1-17 turbine blades and 1-4 inflow holes.
In the scheme, the impact joint is provided with 1-8 liquid outlet channels, 1-6 first liquid outlet holes and 1-6 second liquid outlet holes.
The invention has the following beneficial effects:
1. the turbine rotor and the overflowing cover plate have strong interference effect on drilling fluid flow, can generate pulse impact load, generate good longitudinal vibration on a drill bit, and have very obvious speed increasing effect.
2. The invention mainly opens different chambers through the rotation of the turbine rotor, so that the piston hammer moves, and the sealing performance is not required to be high.
3. The longitudinal vibration frequency and amplitude of the invention are controlled by the size, number and inclination angle of the oblique perforation, which is convenient for adjustment.
4. The invention has no buffer reset devices such as springs and the like, reduces energy loss, improves the utilization efficiency of hydraulic impact power and solves the problem of low impact efficiency.
5. The invention has simple structure, easy realization and lower cost, and is convenient for popularization and application in the oilfield field.
Fourthly, explanation of the attached drawings:
FIG. 1 is a schematic structural view of the present invention;
FIG. 2 is an external view of the impact joint of the present invention;
FIG. 3 is a cross-sectional view A-A of FIG. 2;
FIG. 4 is an external view of the cover plate of the present invention;
FIG. 5 is a cross-sectional view of the flow-through cover plate of the present invention;
FIG. 6 is a schematic structural view of a hexagonal sleeve according to the present invention;
FIG. 7 is a schematic view of the construction of the movable hammer of the present invention;
FIG. 8 is a cross-sectional view of a fluidic stator of the present invention;
FIG. 9 is a top view of the fluidic stator of the present invention;
FIG. 10 is an external view of a turbine rotor of the present invention;
FIG. 11 is a sectional view taken along line F-F of FIG. 10;
FIG. 12 is a view showing the upward movement of the movable hammer in the present invention;
FIG. 13 is a cross-sectional view A-A of FIG. 12;
FIG. 14 is a cross-sectional view B-B of FIG. 12;
FIG. 15 is a view of the present invention with the movable hammer in an upward position;
FIG. 16 is a cross-sectional view A-A of FIG. 15;
FIG. 17 is a cross-sectional view B-B of FIG. 16;
FIG. 18 is a view showing a state in which the movable hammer moves downward in the present invention;
FIG. 19 is a cross-sectional view A-A of FIG. 18;
FIG. 20 is a cross-sectional view taken along line B-B of FIG. 18;
FIG. 21 is a view of the present invention with the movable hammer held in a down position;
FIG. 22 is a cross-sectional view taken along line A-A of FIG. 21;
fig. 23 is a cross-sectional view B-B of fig. 21.
In the figure, 1, a double female joint, 2, a main body short joint, 3, a hexagonal sleeve, 4, an impact joint, 5, a jet flow stator, 6, a turbine rotor, 7, an overflowing cover plate, 8, a piston hammer, 9, an elastic body I, 10, a half-split ring, 11, an elastic body II, 12, a hexagonal joint, 13, a T-shaped step, 14, a clamping ring groove, 15, a liquid outlet channel, 16, a second liquid outlet hole, 17, a first liquid outlet hole, 18, a hollow cavity, 19, a pressure reducing hole, 20, a confluence channel, 21, a flow stabilizing channel, 22, an overflowing cover head, 23, an overflowing channel, 24, a first overflowing hole, 25, a second overflowing hole, 26, an inclined perforating hole, 27 limiting groove, 28, 29, a limiting column, 30, a protecting ring, 31, an inflow hole, 32, a ring platform, 33, a transmission cylinder, 34, a first circulating hole, 35, a second circulating hole, 36, a turbine blade, 37, a rotor channel, 38, a first cavity, a second circulating hole, a second circulating, 39. A second chamber.
Detailed Description
The invention is further described below with reference to the accompanying drawings:
as shown in fig. 1, the turbine type axial impactor of the turbine type axial impactor comprises a double female joint 1, a main short circuit 2, a hexagonal sleeve 3, an impact joint 4, a jet stator 5, a turbine rotor 6, an overflowing cover plate 7 and a piston hammer 8, wherein the upper end of the main short circuit 2 is connected with the double female joint 1, the lower end of the main short circuit 2 is connected with the impact joint 4 through the hexagonal sleeve 3, a hollow cavity 18 of the impact joint 4 is positioned in the main short circuit 2, an overflowing cover head 22 of the overflowing cover plate 7 is seated at an upper port of the hollow cavity 18 of the impact joint 4, and an overflowing channel 23 of the overflowing cover plate 7 is inserted into the hollow cavity 18, so that the piston hammer 8 only moves in the hollow cavity 18; the piston hammer 8 is positioned in an annular space between the hollow cavity 18 and the overflowing channel 23, a transmission cylinder 33 of the turbine rotor 6 is inserted into the overflowing channel 23, an annular table 32 in the turbine rotor 6 is seated on the overflowing cover head 22 of the overflowing cover plate 7, and the upper end of the turbine rotor 6 is connected with the jet flow stator 5.
The jet flow stator 5 is clamped at the female buckle of the main body short circuit 2, an annular elastic body is arranged between the jet flow stator 5 and the double female joint 1, and the impact of the reverse force formed by jet flow on the double female joint 1 is relieved; as shown in fig. 8 and 9, the outlet end of the oblique perforation 26 of the jet stator 5 is provided with an oblique clamping groove 28 with an oblique outer contour, so as to be matched with a turbine blade 36 of the turbine rotor 6; and a limit groove 27 is provided in the cylindrical table of the jet stator 5 so that the turbine rotor 6 does not move radially or axially.
As shown in fig. 4 and 5, an overflow channel 23 is formed in the overflow cover plate 7, and the inner diameter of the overflow channel 23 matches with the outer diameter of a transmission cylinder 33 of the turbine rotor 6, so that the transmission cylinder 33 can rotate in the overflow channel 23, and an annular table 32 in the turbine rotor 6 is seated on the overflow cover head 22 of the overflow cover plate 7 to limit the axial movement of the overflow cover plate 7; inside the jet stator 5, there are 7 oblique perforations 26, and when the fluid passes through the oblique perforations 26, the jet will hit the turbine blades 36 of the turbine rotor 6, so that the turbine rotor 6 will rotate.
The drive cylinder 33 of the turbine rotor 6 is hollow, forming a rotor channel, which is a flow channel for the fluid; the transmission cylinder 33 is divided into three sections, and the upper end of the transmission cylinder 33 is provided with an inflow hole 31 for allowing the fluid passing through the turbine blades 36 to flow into a rotor channel 37 of the turbine rotor 6; the transfer cylinder 33 has two symmetrical sets of circulation holes (first circulation hole 34 and second circulation hole 35) and the flow cover plate 7 also has two corresponding sets of flow holes (first flow hole 24 and second flow hole 25) that match each other so that the piston hammer 8 moves repeatedly to impact the impact sub 4.
The impact fitting 4 presents a relief orifice 19 at the bottom of the hollow cavity 18, from which fluid can flow out of the hollow cavity 18, thereby reducing the pressure in the hollow cavity 18; in the middle of the impact joint 4 there is a set of outlet channels 15, from which the fluid coming out of the first outlet opening 17 and the second outlet opening 16 can flow into the collecting channel 20; and a steady flow passage 21 is provided between the pressure reducing hole 19 and the liquid outlet passage 15 in order to make the fluid in a stable state. A section of hexagonal joint 12 is arranged outside the impact joint 4 and is used for being matched with the inside of the hexagonal sleeve 3 to fix the impact joint 4, and sharp positions of the hexagonal joint are provided with chamfers so as to reduce abrasion in the vibration process.
When the invention is installed: the hexagonal sleeve 3 is sleeved on the impact joint 4, and the interior of the hexagonal sleeve 3 is matched with the hexagonal joint 12 of the impact joint 4; the half-split ring 10 and the elastic body II 11 are respectively arranged on a clamping ring groove 14 and a T-shaped step 13 of the impact joint 4, the hexagonal sleeve 3 and the main body short joint 2 are arranged together by threads, and the impact joint 4 is fixed; the piston hammer 8 is arranged in the hollow cavity 18 of the impact joint 4, the overflowing cover plate 7 and the turbine rotor 6 are sequentially inserted into the hollow cavity 18, and at the moment, the piston hammer 8 only moves axially in the hollow cavity 18; and matching a limiting groove 27 in the jet flow stator 5 with a limiting column 29 of the turbine rotor 6, installing an elastic body I9 on the turbine rotor 6, and finally screwing the double female connector 1 and the main short circuit 2 by using threads to finish installation.
As shown in fig. 2 and 3, when the fluid in the hollow cavity 18 cannot flow out from the first liquid outlet hole 17 or the second liquid outlet hole 16, a closed space is formed inside the hollow cavity 18, and the pressure inside the hollow cavity 18 gradually increases with the inflow of the fluid, so that the tool is easily damaged, and therefore, a pressure reducing hole 19 is formed at the bottom of the hollow cavity 18, thereby reducing the pressure inside the hollow cavity. The snap ring groove 14 is used for mounting the half-split ring 10, thereby fixing the impact joint 4. The T-shaped step 13 is for mounting the elastic body ii 11, and for alleviating the position shift of the impact joint 4 caused by the periodic impact force of the piston hammer 8.
The hexagonal socket 3 shown in fig. 6 has a regular hexagon inside, which is just matched with the hexagon of the hexagonal socket 12 of the impact joint 4, and is used for fixing the impact joint 4. The outside of hexagonal cover 3 is a set of screw thread, and is identical with the internal thread of main part nipple 2 for hexagonal cover 3 and main part nipple 2 link together.
The transfer cover plate 7 in fig. 4 and 5 is mounted inside the piston hammer 8 in fig. 7, and the drive cylinder 33 of the turbine rotor 6 is also mounted inside the transfer channel 23 of the transfer cover plate 7, one ring after the other. Due to the rotation of the turbine rotor 6, the two circulation holes of the turbine rotor 6 and the two corresponding overflowing holes of the overflowing cover plate 7 form a communicating or closed channel at the same time, but due to the layer of piston hammer 8 outside, the channel can be just blocked, so the communication condition of the two channels is also closely related to the motion condition of the piston hammer 8.
The piston hammer 8 shown in fig. 7 is a three-section hollow cylindrical structure, the inner diameter and the outer diameter of the head section and the tail section are consistent, the outer diameter of the middle section is large, the inner diameter of the middle section is small, the piston hammer 8 is installed in the hollow cavity 18 of the impact joint 4 and can move axially, the outer diameter of the middle section of the piston hammer 8 is large, the inner diameter of the middle section of the piston hammer 8 is small, and therefore when the piston hammer 8 moves axially, the internal friction between the piston hammer 8 and the outside hollow cavity 18 and the internal friction between the piston hammer and the inside overflowing cover plate 7 are reduced, and therefore.
For ease of understanding, the following description is made of the working process of the present invention:
1. when the turbine rotor 6 rotates, the first circulation holes 34 of the turbine rotor 6 are staggered from the first overflowing holes 24 of the overflowing cover plate 7, as shown in fig. 12, 13 and 14. A first cavity 38 formed by the movable hammer 8, the overflowing cover plate 7 and the impact joint 4 forms a negative pressure area, the movable hammer 8 moves upwards, and fluid in the first cavity 38 flows out of the first liquid outlet hole 17;
2. when the turbine rotor 6 continues to rotate and the first circulation hole 34 is communicated with the first overflowing hole 24, the piston hammer 8 blocks the passage of the first circulation hole, but the second circulation hole 35 is communicated with the second overflowing hole 25, the fluid flows out of the second liquid outlet hole 16, and the piston hammer 8 keeps an upward state, as shown in fig. 15, 16 and 17;
3. when the turbine rotor 6 rotates again, the second circulation hole 35 is staggered with the second overflowing hole 25, a negative pressure area is formed in the second chamber 39, as shown in fig. 18, 19 and 20, the piston hammer 8 moves downwards, and fluid in the second chamber 39 flows out of the second liquid outlet hole 16;
4. when the turbine rotor 6 rotates again, the second circulation holes 35 are communicated with the second overflowing holes 25, the piston hammers 8 block the passages of the second circulation holes, but the first circulation holes 34 are communicated with the first overflowing holes 24, the fluid flows out of the first liquid outlet holes 17, and the piston hammers 8 keep a descending state, as shown in fig. 21, 22 and 23.
With this cycle, the piston hammer 8 will make a cyclic movement in the hollow chamber 18, repeatedly and periodically striking the impact joint 4.
Claims (8)
1. A turbine axial impactor, comprising: the turbine type axial impactor comprises a double female joint (1), a main body short circuit (2), a hexagonal sleeve (3), an impact joint (4), a jet flow stator (5), a turbine rotor (6), an overflowing cover plate (7) and a piston hammer (8), wherein the upper end of the main body short circuit (2) is connected with the double female joint (1), the lower end of the main body short circuit is connected with the impact joint (4) through the hexagonal sleeve (3), a hollow cavity (18) of the impact joint (4) is positioned in the main body short circuit (2), an overflowing cover head (22) of the overflowing cover plate (7) is seated at an upper port of the hollow cavity (18) of the impact joint (4), an overflowing channel (23) of the overflowing cover plate (7) is inserted into the hollow cavity (18), the piston hammer (8) is of a three-section hollow cylindrical structure, the piston hammer (8) is positioned in an annular space between the overflowing cavity (18) and the overflowing channel (23), a transmission cylinder (33) of the turbine rotor (6) is inserted into, an annular table (32) in the turbine rotor (6) is seated on an overflowing cover head (22) of the overflowing cover plate (7), the upper end of the turbine rotor (6) is connected with a jet flow stator (5), and the jet flow stator (5) is pressed at the lower port of the double female connector (1); the jet flow stator (5) is internally provided with oblique perforation holes (26), and when fluid passes through the oblique perforation holes (26), the jet flow hits turbine blades (36) of the turbine rotor (6), so that the turbine rotor (6) rotates;
the transmission cylinder (33) is hollow, the transmission cylinder above the annular table (32) is provided with an inflow hole (31), the transmission cylinder below the annular table (32) is provided with a first circulation hole (34) and a second circulation hole (35), the overflowing channel (23) is correspondingly provided with a first overflowing hole (24) and a second overflowing hole (25), and the hollow cavity (18) is correspondingly provided with a first liquid outlet hole (17) and a second liquid outlet hole (16).
2. The turbine axial impactor of claim 1, wherein: the jet flow stator (5) is clamped at a female buckle of the main body short circuit (2), and an annular elastic body is arranged between the jet flow stator (5) and the double female joint (1); an outlet end of an oblique perforation (26) of the jet flow stator (5) is provided with an oblique clamping groove (28) with an inclined outer profile, and the oblique clamping groove (28) is matched with a turbine blade (36) of the turbine rotor (6); a limiting groove (27) is formed in the center of the jet flow stator (5), and a limiting column (29) at the upper end of the turbine rotor (6) is inserted into the limiting groove (27).
3. The turbine axial impactor of claim 2, wherein: the lower edge of the limiting column (29) is provided with a protective ring (30).
4. The turbine axial impactor of claim 3, wherein: the bottom of the hollow cavity (18) of the impact joint (4) is provided with a pressure reducing hole (19), the middle part of the impact joint (4) is provided with a liquid outlet channel (15), and the impact joint below the liquid outlet channel (15) is provided with a confluence channel (20); a steady flow channel (21) is arranged between the pressure reducing hole (19) and the liquid outlet channel (15); a section of hexagonal joint (12) is arranged outside the impact joint (4), the hexagonal joint (12) is matched with the inside of the hexagonal sleeve (3), the impact joint (4) is fixed, and a sharp part of the hexagonal joint (12) is provided with a chamfer.
5. The turbine axial impactor of claim 4, wherein: the outside of the impact joint (4) is provided with a clamping ring groove (14), and the lower end of the clamping ring groove (14) is provided with a T-shaped step (13).
6. The turbine axial impactor of claim 5, wherein: the jet flow stator (5) is provided with 1-7 oblique perforation holes (26).
7. The turbine axial impactor of claim 6, wherein: the turbine rotor (6) is provided with 1-17 turbine blades (36) and 1-4 inflow holes (31).
8. The turbine axial impactor of claim 7, wherein: the impact joint (4) is provided with 1-8 liquid outlet channels (15), 1-6 first liquid outlet holes (17) and 1-6 second liquid outlet holes (16).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811179645.0A CN109025804B (en) | 2018-10-10 | 2018-10-10 | Turbine type axial impactor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811179645.0A CN109025804B (en) | 2018-10-10 | 2018-10-10 | Turbine type axial impactor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109025804A CN109025804A (en) | 2018-12-18 |
| CN109025804B true CN109025804B (en) | 2019-12-20 |
Family
ID=64616526
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201811179645.0A Active CN109025804B (en) | 2018-10-10 | 2018-10-10 | Turbine type axial impactor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN109025804B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113550696B (en) * | 2021-07-26 | 2022-07-19 | 中煤科工集团西安研究院有限公司 | Drill bit with axial rock breaking function |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201087695Y (en) * | 2007-10-16 | 2008-07-16 | 长沙黑金刚实业有限公司 | High wind pressure downhole air hammer |
| CN102953678A (en) * | 2011-08-23 | 2013-03-06 | 宜昌市五环钻机具有限责任公司 | Valveless single cylinder blind hole channel down-hole hammer |
| CN103821452B (en) * | 2014-03-11 | 2016-01-20 | 东北石油大学 | A kind of frequency low-amplitude axial impact device |
| AU2015101848A4 (en) * | 2014-12-26 | 2016-02-18 | Yichang Wuhuan Rock Drilling Tools Co., Ltd | Down-the-Hole Impactor |
| CN105239922A (en) * | 2015-10-08 | 2016-01-13 | 西南石油大学 | Local reciprocating type hydraulic-impact well drilling speed increasing tool |
| CN106703686B (en) * | 2017-03-08 | 2018-10-30 | 中国石油天然气集团公司 | Pulsing jet formula impact of collision device |
-
2018
- 2018-10-10 CN CN201811179645.0A patent/CN109025804B/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| CN109025804A (en) | 2018-12-18 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102191915B (en) | Resonant pulse vibrating drilling device | |
| CN104265160B (en) | Hydraulic oscillation axial impact device | |
| CN103628815B (en) | A kind of nearly drill bit reverses, Oscillatory Coupling impactor | |
| CN203701951U (en) | Torsion impact generator | |
| CN109025805B (en) | Pulse jet hydraulic impactor | |
| CN109025827B (en) | Hydraulic torsional pulse impactor for drilling speed increase | |
| CN103899250A (en) | Device for improving oil and gas well drilling speed | |
| CN107605396B (en) | A kind of shunt penetrates suction hydraulic impacter | |
| CN104499941A (en) | Device for converting longitudinal vibration of drill stem into torsional impact of drill bit | |
| CN206129207U (en) | Novel oscillatory surge ware based on turbine and cam | |
| CN109025804B (en) | Turbine type axial impactor | |
| CN108222873B (en) | Composite vibration impactor | |
| CN203271584U (en) | Well-drilling water-pressure torsional impact device | |
| CN200989164Y (en) | Pulsation pumping pressure drilling device for lowering underwell differential pressure | |
| CN204326969U (en) | Method of longitudinal vibration of drilling string is converted into the device of drill bit torsional pulse | |
| CN203594356U (en) | Near-bit torsion and oscillation coupling impactor | |
| CN108643824B (en) | Hydraulic vibration-damping impact drilling tool | |
| CN111877979B (en) | Ratchet type hydraulic impactor | |
| CN105840098B (en) | Hydraulic impacter | |
| AU2020104043A4 (en) | Turbine-type axial impactor 2 | |
| CN112627720A (en) | High-efficiency injection-suction type hydraulic impactor | |
| CN106761386B (en) | A kind of drilling well auxiliary rock tool | |
| CN207795050U (en) | A kind of frequency low-amplitude complex vibration impactor | |
| RU181505U1 (en) | SLIDING EXPANDER | |
| CN215830423U (en) | Combined impact tool |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| CB03 | Change of inventor or designer information | ||
| CB03 | Change of inventor or designer information |
Inventor after: Li Wei Inventor after: Sun Wenfeng Inventor after: Ling Xin Inventor after: Li Siqi Inventor after: Li Yuwei Inventor after: Li Jianbing Inventor after: Gai Jingming Inventor before: Li Wei Inventor before: Ling Xin Inventor before: Li Siqi Inventor before: Li Yuwei Inventor before: Li Jianbing Inventor before: Gai Jingming |
|
| CB03 | Change of inventor or designer information | ||
| CB03 | Change of inventor or designer information |
Inventor after: Sun Wenfeng Inventor after: Li Wei Inventor after: Ling Xin Inventor after: Li Siqi Inventor after: Li Yuwei Inventor after: Li Jianbing Inventor after: Gai Jingming Inventor before: Li Wei Inventor before: Sun Wenfeng Inventor before: Ling Xin Inventor before: Li Siqi Inventor before: Li Yuwei Inventor before: Li Jianbing Inventor before: Gai Jingming |
|
| GR01 | Patent grant | ||
| GR01 | Patent grant |