CN111173442A - Novel two-stage boosting hydraulic impactor - Google Patents
Novel two-stage boosting hydraulic impactor Download PDFInfo
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- CN111173442A CN111173442A CN202010084675.4A CN202010084675A CN111173442A CN 111173442 A CN111173442 A CN 111173442A CN 202010084675 A CN202010084675 A CN 202010084675A CN 111173442 A CN111173442 A CN 111173442A
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- 238000011010 flushing procedure Methods 0.000 claims abstract description 16
- 239000012530 fluid Substances 0.000 claims abstract description 4
- 239000011148 porous material Substances 0.000 claims abstract 2
- 230000029058 respiratory gaseous exchange Effects 0.000 claims description 6
- 238000007789 sealing Methods 0.000 claims description 5
- 239000000956 alloy Substances 0.000 claims 1
- 229910045601 alloy Inorganic materials 0.000 claims 1
- 208000006011 Stroke Diseases 0.000 abstract description 15
- 238000005553 drilling Methods 0.000 abstract description 11
- 238000000034 method Methods 0.000 abstract description 11
- 230000008569 process Effects 0.000 abstract description 6
- 230000001133 acceleration Effects 0.000 abstract description 3
- 239000007788 liquid Substances 0.000 description 15
- 230000009471 action Effects 0.000 description 9
- 239000011435 rock Substances 0.000 description 6
- 238000010586 diagram Methods 0.000 description 5
- 238000002347 injection Methods 0.000 description 5
- 239000007924 injection Substances 0.000 description 5
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 5
- 238000005299 abrasion Methods 0.000 description 2
- 230000007547 defect Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000003754 machining Methods 0.000 description 2
- 230000001360 synchronised effect Effects 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000008030 elimination Effects 0.000 description 1
- 238000003379 elimination reaction Methods 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 239000012535 impurity Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000000843 powder Substances 0.000 description 1
- 238000004080 punching Methods 0.000 description 1
- 238000010008 shearing Methods 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
- 239000002002 slurry Substances 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 230000008719 thickening Effects 0.000 description 1
- 238000005406 washing Methods 0.000 description 1
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- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21B—EARTH OR ROCK 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
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- Engineering & Computer Science (AREA)
- Life Sciences & Earth Sciences (AREA)
- Geology (AREA)
- Mining & Mineral Resources (AREA)
- Mechanical Engineering (AREA)
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- Environmental & Geological Engineering (AREA)
- Fluid Mechanics (AREA)
- General Life Sciences & Earth Sciences (AREA)
- Geochemistry & Mineralogy (AREA)
- Earth Drilling (AREA)
- Pipe Accessories (AREA)
Abstract
The invention discloses a novel two-stage boosting hydraulic impactor, which comprises an outer pipe, an anvil and a hammer, wherein a nozzle seat is arranged in the outer pipe, the lower end of the nozzle seat is inserted into a tail hole of the hammer arranged in the outer pipe, a pipe valve capable of sliding up and down along the nozzle seat is sleeved in the middle of the nozzle seat, an axial pore passage is formed in the pipe valve to communicate a first pressure area above the pipe valve and a second pressure area below the pipe valve, the sectional area of the lower end surface of the pipe valve in the second pressure area is larger than that of the upper end surface of the pipe valve in the first pressure area, a jet hole is formed in the middle of the nozzle seat and faces a flushing fluid channel in the middle of the hammer, and a third pressure area is formed between the tail hole of the hammer; the side wall of the nozzle seat is provided with a side inlet communicated with the jet hole. The hammer can obtain two times of boosting force in the descending process of the impact hammer, namely pressure energy is obtained in the valve closing acceleration stage, and secondary boosting force is obtained in the free stroke stage in addition to inertia force, so that the impact kinetic energy is higher, the striking capability is improved, and the drilling efficiency is improved.
Description
Technical Field
The invention relates to an impactor for geological exploration, which is suitable for a hydraulic impact rotary drilling method.
Background
In geological drilling operation, the impact rotary drilling method is an effective method for drilling hard rock layers, namely, an impactor is connected to the upper part of a drill bit or the upper part of a core barrel, the impactor generates impact force by hydraulic pressure and transmits the impact force to the drill bit, the drill bit is additionally provided with axial impact force while rotating and crushing rock, namely, the rotary drilling and the axial impact are combined, the drill bit is enabled to crush the rock under the action of the impact force and the rotary shearing force, the drilling speed can be greatly improved, and the method has the advantages of being anti-inclination effect, prolonging the service life of the drill bit and the like. The method can be widely applied to drilling of hard rock stratum, stratum with easy hole deviation and stratum with strong abrasiveness.
The impact rotary drilling technology is an effective means for improving the drilling speed of hard rock, but the traditional positive-acting impactor is also the time when the impact energy is counteracted by a spring to the maximum at the moment when a hammer strikes an anvil. The traditional double-acting impactor also reduces the striking speed of the impact hammer and the impact energy of the impact hammer due to the action of the water cushion. When the impact hammer enters the free stroke stage, the upper part of the impact hammer is dragged by the negative pressure sucked by the jet flow, so that the striking speed of the impact hammer is reduced, and the impact energy is reduced. The impactors all have low energy utilization rate of the impact rotary drilling technology due to respective defects. In addition, the three impactors have a common disadvantage that the hammer loses the main acting force in the free stroke stage except for gravity, the impact is completely based on inertia, and under the action of corresponding resistance, the speed of the hammer striking the anvil is not the maximum speed of the hammer, namely the impact energy is reduced, and even the hammer cannot strike the anvil and returns to the upper side.
In view of the above, the present invention is particularly proposed.
Disclosure of Invention
Aiming at the problems of the existing hydraulic impactor, the invention aims to provide a novel two-stage boosting hydraulic impactor which can provide secondary thrust at the tail section of an impact stroke of an impact hammer, overcome the influence of resistance, improve the impact speed and further improve the impact kinetic energy.
The technical scheme of the novel two-stage boosting hydraulic impactor is as follows: a novel two-stage boosting hydraulic impactor comprises an outer tube, a anvil and a hammer, wherein a nozzle seat is arranged in the outer tube, the lower end of the nozzle seat is inserted into a tail hole of the hammer arranged in the outer tube, the middle part of the nozzle seat is sleeved with a pipe valve which can slide up and down along the nozzle seat, an axial duct on the pipe valve is communicated with a first pressure area above the pipe valve and a second pressure area below the pipe valve, the sectional area of the lower end surface of the pipe valve in the second pressure area is larger than that of the upper end surface of the pipe valve in the first pressure area, the middle part of the nozzle seat is provided with an injection hole facing to a flushing liquid channel in the middle part of the impact hammer, a third pressure area is arranged between the tail hole of the impact hammer and the nozzle seat, the side wall of the nozzle seat is provided with a side inlet communicated with the injection hole, the position of the side inlet meets the requirement that the side inlet is covered and closed when the pipe valve is positioned at a lower dead point, when the pipe valve is at the top dead center, the lower end of the pipe valve can not close the side inlet, and when the impact hammer is at the top dead center, the upper end surface of the impact hammer corresponds to the lower end of the pipe valve and can cover and close the nozzle seat side inlet.
Furthermore, an inner cylinder is installed in the outer pipe, the nozzle seat and the valve sleeve are installed in the inner cylinder, and a locking position on the valve sleeve is formed in the inner cylinder through a shoulder part.
Further, an inner cylinder is arranged between the outer pipe and the pipe valve, the outer diameter of the lower portion of the pipe valve is larger than the outer diameter of the upper portion of the pipe valve, correspondingly, the inner diameter of the lower portion of the inner cylinder is larger than the inner diameter of the upper portion of the pipe valve, a breathing hole is formed in the side wall of the top portion, close to the larger portion of the inner diameter, of the inner cylinder and communicated with a channel between the inner cylinder and the outer pipe, and.
Furthermore, the lower end of the inner cylinder is further connected with an inner cylinder lower joint, a seal is arranged between the inner cylinder lower joint and the upper end part of the impact hammer, the inner diameter of the part of the outer pipe, where the inner cylinder and the inner cylinder lower joint are installed, is larger than that of the lower half part, a shoulder is formed on the inner wall, the lower end part of the inner cylinder lower joint abuts against the shoulder to realize the positioning of the inner cylinder and the inner cylinder lower joint in the outer pipe, and the upper end part of the inner cylinder is compressed by the lower end face of the upper joint which is connected to the upper end of.
Further, the nozzle seat is axially and radially positioned by an upper shoulder which is annularly and convexly arranged inwards at the upper end of the inner cylinder and abuts against a radial convex edge at the upper end of the nozzle seat from the lower part, and the upper edge of the nozzle seat is pressed by the upper joint.
Furthermore, sealing rings are arranged between the upper end of the impact hammer and the nozzle seat and between the upper end of the impact hammer and the lower joint of the inner cylinder.
Further, a convergent nozzle is installed at the injection hole of the nozzle holder.
Furthermore, an annular groove is arranged on the lower end face of the pipe valve and communicated with the hole on the pipe valve.
Further, the nozzle seat surface side hole position is provided with a circle of annular grooves.
Furthermore, the lower end of the outer pipe is connected with a sliding seat sleeve through threads, the anvil is installed in the sliding seat sleeve, and the lower end of the anvil is connected with a lower connector.
Furthermore, an adjusting gasket is arranged between the sliding seat sleeve and the lower joint.
According to the novel two-stage boosting hydraulic impactor with the structure, in the descending accelerating stage when the impact hammer and the valve are closed, the low-pressure area is formed below the impact hammer, the spring resistance of a positive-acting impactor is not generated in the low-pressure area, and the water cushion resistance of a throttling ring of a traditional double-acting impactor is not generated. In the free stroke process of the valve and the impact hammer, the water channel on the side surface of the nozzle seat is not opened instantly but lags a little, so that the second pressure area is still in a high-pressure state to generate secondary boosting force on the tail end surface of the upper part of the impact hammer, the defect that the impact hammer only bears inertia force but does not have main power in the free stroke stage is overcome, the impact speed can be effectively increased, and the impact energy is increased.
Drawings
Fig. 1 is a schematic structural view of the novel two-stage boosting hydraulic impactor, and a schematic view of a state that a jet flow jet and a suction impact hammer start to ascend at the upper limit position of a pipe valve.
FIG. 2 is a schematic diagram of the synchronized acceleration downstroke of the impactor of FIG. 1 after the hammer upstroke and the tubular valve are closed.
Fig. 3 is a schematic view of the impactor of fig. 1 with the hammer and pipe valve separated and the ram in a free stroke stage.
FIG. 4 is a schematic view of another embodiment of a nozzle carrier.
Fig. 5 is a cross-sectional view B-B of fig. 2.
3 fig. 3 6 3 is 3 a 3 sectional 3 view 3 taken 3 along 3 line 3 a 3- 3 a 3 of 3 fig. 3 1 3. 3
In the figure: 1. the device comprises an upper joint, 2, an outer pipe, 3, a nozzle seat, 4, an inner cylinder, 5, a pipe valve, 6, a nozzle, 7, a lower joint of the inner cylinder, 8, a punch hammer, 9, an anvil, 10, a sliding seat sleeve, 11, a gasket, 12 and a lower joint; 13. annular groove, 14, annular groove
a. Flushing liquid passage area, b, first pressure area, c, second pressure area, d, third pressure area, e, breathing hole, f, breathing passage
Detailed Description
The invention is further described below in conjunction with the drawings and the detailed description of the invention to assist in understanding the content of the invention.
Fig. 1 shows a complete structural schematic diagram of the novel two-stage boosting hydraulic impactor, which is a schematic diagram of a state that a pipe valve is already at an upper limit position under hydraulic pressure, jet injection forms entrainment, and a punching hammer starts to ascend. FIG. 2 is a schematic diagram of the upward movement of the hammer in contact with the pipe valve to close the waterway and about to accelerate the downward movement in the same direction. FIG. 3 is a schematic diagram showing the state that the pipe valve is stopped by the upper end face of the lower joint of the inner cylinder, the hammer is separated from the pipe valve, the primary power assistance is stopped, but the drainage channel is not opened, the secondary power assistance of the impact hammer is started, and the impact hammer and the pipe valve deviate from each other. To clearly show the details of the construction of the spool valve portion, FIG. 2 shows the impactor with the upper and lower fittings removed.
The whole structure of the impactor is shown in figure 1, the upper end of an outer pipe 2 formed by a section of steel pipe is connected with an upper connector 1 through threads, and the upper connector 1 is used for being connected with a drill rod. The outer pipe 2 is internally provided with a nozzle holder 3, an inner cylinder 4, an inner cylinder lower joint 7 and a hammer 8. The lower end of the outer pipe 2 is connected with a sliding seat sleeve 10 through threads, an anvil 9 is installed in the sliding seat sleeve 10, the lower end of the anvil is connected with a lower connector 12, and the lower connector 12 is used for being directly connected with a drill bit or being connected with the drill bit through a drill rod.
In the preferred embodiment shown in fig. 1, 2 and 3, an inner cylinder 4 is also coaxially mounted on the upper half of the outer tube 2, the lower end of the inner cylinder 4 is connected with an inner cylinder lower joint 7 through threads, and the inner cylinder 4 and the inner cylinder lower joint 7 form a tandem inner sleeve structure mounted in the outer tube 2. The inner diameter of the part of the outer pipe 2, where the inner cylinder 4 and the inner cylinder lower joint 7 are installed, is larger, a shoulder is formed on the inner wall, the lower end part of the inner cylinder lower joint 7 abuts against the shoulder to position the inner cylinder 4 and the inner cylinder lower joint 7 in the outer pipe 2, the upper end part of the inner cylinder 4 is pressed by the lower end face of the upper joint 1 which is connected to the upper end of the outer pipe 2 through threads, and the inner cylinder 4 and the inner cylinder lower joint 7 are installed and fixed in the outer pipe 1. This approach facilitates segmented tooling and quick assembly.
The upper end of the outer pipe 2 is provided with a nozzle holder 3, the upper convex shoulder which is convex towards the inside at the upper end of the inner cylinder 4 is abutted against the convex edge at the upper end of the nozzle holder from the lower part to carry out axial and radial positioning, and the upper edge is pressed by the upper joint 1 to realize fixed installation. The nozzle holder 3 has a smaller diameter at its lower part and forms an annular gap with the inner cylinder 4, in which gap a pipe valve 5 is mounted. The upper end of the inner cylinder 4 is provided with a lower shoulder which protrudes inwards in an annular shape to form an upper stroke stop point of the pipe valve 5, the upper end surface of the inner cylinder lower joint 7 which protrudes inwards on the inner wall of the inner cylinder 4 is provided with a lower stroke stop point of the pipe valve 5 to limit the sliding stroke of the pipe valve 5, and the pipe valve 5 can only slide in the range between the upper stop point and the lower stop point.
An annular gap is arranged between the nozzle holder 3 and the inner cylinder 4 above the pipe valve 5 to form a first pressure area b, and the first pressure area b is communicated with a flushing liquid channel area a in the middle of the nozzle holder through a side hole of the nozzle holder 3. The external diameter of the lower part of the pipe valve 5 is larger than that of the upper part, so that the sectional area of the lower end surface of the pipe valve 5 is larger than that of the upper end surface. Correspondingly, the lower part of the inner diameter of the inner cylinder 4 is larger than the upper part, so that an annular movement space is formed between the pipe valve 5 and the inner cylinder 4, and the movement space is downwards communicated to a flushing liquid area between the impact hammer 8 and the outer pipe 2 through a breathing hole e on the side wall of the inner cylinder 4 and an annular gap between the inner cylinder 4 and the outer pipe 2. The pipe valve 5 is also in the shape of a circular pipe and is mounted in the annular gap between the nozzle holder 3 and the inner cylinder 4 and can slide up and down. The pipe valve 5 is provided with an axial hole which is communicated with a first pressure area b at the upper end of the pipe valve and a second pressure area c below the pipe valve to form a washing liquid channel.
O-shaped ring sealing structures are adopted between the pipe valve 5 and the inner cylinder 4 and between the pipe valve and the nozzle seat 3, the O-shaped rings play a sealing role and are mainly used as quick-wear parts to be conveniently replaced, and abrasion caused by direct friction between the pipe valve and the nozzle seat and the inner cylinder is avoided. Of course, it is also advantageous to reduce the machining accuracy.
The lower end of the nozzle seat 3 is inserted into a tail hole of the punch hammer 8, a third pressure area d is formed between the lower end of the punch hammer 8 and the tail end of the punch hammer 8 to form a jet flow entrainment area, and O-shaped rings are arranged between the upper end of the punch hammer 8 and the lower joint 7 of the inner cylinder and between the upper end of the punch hammer and the annular gap of the nozzle seat 3 for sealing and reducing abrasion. The center of the lower end of the nozzle seat 3 is provided with a jet flow jet hole, the jet flow jet hole faces to the center of the impact hammer 8, the nozzle seat 3 is provided with a side inlet which is communicated with the central jet hole, and the side inlet position of the nozzle seat is arranged to meet the following requirements: the pipe valve covers the side inlet of the nozzle holder 3 when the pipe valve 5 is in the bottom dead center position as shown in fig. 3, the pipe valve opens the side inlet of the nozzle holder when the pipe valve 5 is in the top dead center position as shown in fig. 1, and the side inlet of the nozzle holder is covered and closed when the ram 8 and the pipe valve 5 are abutted together as shown in fig. 2 (simultaneous descending process).
The working principle is explained as follows:
as shown in figure 1, flushing liquid (slurry) enters a flushing liquid channel area a of the impactor through an upper connector 1, then enters a first pressure area b through a side hole at the upper end of a nozzle seat 3, and then enters a second pressure area c below a pipe valve through a hole channel on the pipe valve 5, because the area of the lower end face of the pipe valve is larger than that of the upper end, the pipe valve 5 is firstly pushed to the top dead center position, an inlet at the side of a jet hole in the middle of the nozzle seat 3 is opened, the flushing liquid forms high-speed jet through the jet hole of the nozzle 3 and is ejected, the jet forms entrainment negative pressure in a third pressure area d at the upper end of a hammer, and under the action of the negative pressure, the hammer 8 overcomes self weight and upward.
When the hammer 8 moves upwards to the upper limit position to be in contact with the pipe valve 5, namely the position and the state shown in fig. 2, the water path is cut off, so that the flushing liquid cannot move downwards, the pressure of the first pressure area b and the pressure of the second pressure area c are instantly formed into high pressure due to the water shock wave pressure generated by closing the valve, and the hammer 8 and the pipe valve 5 synchronously accelerate downwards under the action of the high pressure, wherein the stage is a first-stage boosting stage.
In the synchronous acceleration descending process of the impact hammer 8 and the pipe valve 5, when the pipe valve 5 is stopped by the upper end surface of the inner cylinder lower joint 7, the impact hammer 8 continuously descends by inertia, the stage is a free stroke stage (as shown in fig. 3), at this time, because the second pressure zone c is not opened to the jet hole channel of the nozzle seat 3, the second pressure zone c is still at high pressure, and except that the impact hammer 8 continuously descends under the action of inertia, the high-pressure flushing liquid at the second pressure zone c generates downward active thrust to the upper end surface of the impact hammer 8, so that the impact hammer 8 is subjected to secondary stress until the anvil 9 is hit, and one impact action is completed. After that, the states of fig. 1 and 2 are repeated, so that the impact action is generated repeatedly.
In the free stroke process, because the second pressure area c is not opened to the injection hole channel of the nozzle seat 3, the entrainment negative pressure shown in fig. 1 can not be generated in the third pressure area d of the tail hole of the punch hammer 8, and the dragging problem of the negative pressure generated by the ejection entrainment in the process of the traditional ejection and suction impactor is overcome. Higher impact energy can be achieved with the secondary boost action and elimination of the "drag" problem described above.
In this embodiment, the structure of assembling the inner casing 4 and the inner casing lower joint 7 in the outer pipe 1 is adopted for the sake of easy processing and assembling, and simultaneously, the breathing hole e is prevented from sucking the flushing liquid containing impurities such as rock powder and the like out of the pipe. The invention can be integrated under the condition of the working principle of the invention.
In order to reduce the local energy loss of the fluid, the upper end of the nozzle holder 3 is in the shape of an inverted cone with a larger diameter, and in order to make the flow of the channel a and the first pressure region B smooth, four side holes as shown in fig. 5 are formed in the section B-B of fig. 2, so that the flushing fluid can smoothly enter the first pressure region B.
Based on the above functions, the nozzle holder 3 can achieve the same effects as the structure shown in fig. 1 to 3, for example, the structure shown in fig. 4. I.e. the through-holes for the flushing liquid are made directly at the circumferential position of the flange at the upper end of the nozzle holder 3 instead of the central hole as shown in fig. 1-3.
In the solutions shown in fig. 1 to 3, because the high-speed jet is formed by a tapered jet structure, the tapered jet can be directly machined on the nozzle holder 3 as shown in fig. 4, or a tapered nozzle 6 can be installed on the nozzle holder 3 by a screw thread as shown in fig. 1 to 3, which is not only beneficial for machining, but also can change the nozzle 6 according to different parameter requirements.
In order to realize that the pipe valve 5 does not continuously open when opening the inlet of the nozzle holder 3, but all the nozzles are opened for making the inlet of the nozzle holder 3 instantly, as shown in fig. 1-3, a ring of annular grooves 14 are arranged at the hole position on the surface side of the nozzle holder 3, and flushing liquid can be converged into the side port of the nozzle holder along the annular grooves 14 on the periphery of the nozzle holder, so that the flushing liquid can smoothly reach the upper end of the nozzle 6.
In the accelerating descending stage of the closed valve, the volume of the second pressure area c is gradually reduced, the liquid in the second pressure area c must smoothly flow back to the first pressure area, and the lower end of the pipe valve is provided with an annular groove 13.
As shown in fig. 1, the lower end of the outer tube 2 is connected with the sliding sleeve 10 through a screw thread, the diameter of the lower end is small, the upper end is large, the corresponding anvil 9 is provided with a large upper end and a large lower end, the upper end and the lower end of the anvil are consistent with the inner hole of the sliding sleeve 10, a regular polygon structure (as shown in fig. 6) is arranged between the sliding sleeve and the anvil, and the anvil and the drill bit are driven to rotate through the outer tube 2 and the sliding sleeve by using the traditional torque.
In order to adjust the impact stroke of the impact hammer, an adjusting gasket 11 is arranged between the lower joint 12 and the sliding seat sleeve 10, the hammer stroke of the thickening gasket is increased, the impact power of the impactor is increased, the impact frequency is reduced, otherwise, the hammer stroke is reduced, the impact energy is reduced, and the impact frequency is increased.
The invention solves the problem that the impact energy of the valve type positive-acting impactor is reduced due to the hammer spring at the stage, solves the problem that the impact energy is reduced due to the water cushion generated by the throttling ring of the traditional double-acting impactor, and solves the problem that the jetting and entrainment of the jetting and absorbing impactor generates the 'absorbing force' at the upper end of the impact hammer. Can greatly improve the energy utilization rate and improve the striking energy.
Claims (10)
1. A novel two-stage boosting hydraulic impactor comprises an outer pipe, an anvil and a hammer, wherein a nozzle seat is installed in the outer pipe, the lower end of the nozzle seat is inserted into a tail hole of the hammer installed in the outer pipe, a pipe valve capable of sliding up and down along the nozzle seat is sleeved in the middle of the nozzle seat, an axial pore passage is formed in the pipe valve and is communicated with a first pressure area above the pipe valve and a second pressure area below the pipe valve, the sectional area of the lower end surface of the pipe valve in the second pressure area is larger than that of the upper end surface of the pipe valve in the first pressure area, a jet hole is formed in the middle of the nozzle seat and faces a flushing fluid channel in the middle of the hammer, and a third pressure area is formed between the tail hole of the; the side inlet of the side wall of the nozzle seat is communicated with the jet hole, the position of the side inlet meets the requirement that the side inlet is covered and closed when the pipe valve is positioned at a bottom dead center, the lower end of the pipe valve cannot close the side inlet when the pipe valve is positioned at a top dead center, and the upper end surface of the impact hammer corresponds to the lower end of the pipe valve and can cover and close the side inlet of the nozzle seat when the impact hammer is positioned at the top dead center.
2. The novel two-stage boosting hydraulic impactor as claimed in claim 1, wherein: an inner cylinder is arranged between the outer pipe and the pipe valve, the outer diameter of the lower part of the pipe valve is larger than the outer diameter of the upper part of the pipe valve, correspondingly, the inner diameter of the lower part of the inner cylinder is larger than the inner diameter of the upper part of the pipe valve, a breathing hole is formed in the side wall of the top part close to the larger part of the inner diameter and communicated with an annular channel between the inner cylinder and the outer pipe, and the annular channel is communicated.
3. The novel two-stage boosting hydraulic impactor as claimed in claim 2, wherein: the lower end of the inner cylinder is further connected with an inner cylinder lower joint, a seal is arranged between the inner cylinder lower joint and the upper end part of the impact hammer, the inner diameter of the part, where the inner cylinder and the inner cylinder lower joint are installed, of the outer pipe is larger than that of the lower half part, a shoulder is formed on the inner wall, the lower end part of the inner cylinder lower joint abuts against the shoulder to achieve the positioning of the inner cylinder and the inner cylinder lower joint in the outer pipe, and the upper end part of the inner cylinder is compressed by the lower end face of an upper joint which is connected to the upper.
4. The novel two-stage boosting hydraulic impactor as claimed in claim 2, wherein: the nozzle seat is axially and radially positioned by an upper convex shoulder which is annularly and convexly arranged inwards at the upper end of the inner cylinder and abuts against a radial convex edge at the upper end of the nozzle seat from the lower part, and the upper edge of the nozzle seat is pressed by an upper joint.
5. The novel two-stage boosting hydraulic impactor as claimed in claim 1 or 2, wherein: and sealing rings are arranged between the upper end of the impact hammer and the nozzle seat and between the upper end of the impact hammer and the lower joint of the inner cylinder.
6. The novel two-stage boosting hydraulic impactor as claimed in claim 1 or 2, wherein: a tapered alloy nozzle is mounted at the nozzle hole of the nozzle holder by screw threads.
7. The novel two-stage boosting hydraulic impactor as claimed in claim 1 or 2, wherein: the lower end face of the pipe valve is provided with an annular groove which is communicated with the hole end on the pipe valve.
8. The novel two-stage boosting hydraulic impactor as claimed in claim 1 or 2, wherein: and a ring of annular grooves are formed in the surface side hole of the nozzle seat.
9. The novel two-stage boosting hydraulic impactor as claimed in claim 1 or 2, wherein: the lower end of the outer pipe is connected with a sliding seat sleeve through threads, the anvil is installed in the sliding seat sleeve, and the lower end of the anvil is connected with a lower connector.
10. The novel two-stage boosting hydraulic impactor as claimed in claim 9, wherein: an adjusting gasket is arranged between the sliding seat sleeve and the lower joint.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010084675.4A CN111173442B (en) | 2020-02-10 | 2020-02-10 | Novel secondary boosting hydraulic impactor |
| PCT/CN2020/089967 WO2021159621A1 (en) | 2020-02-10 | 2020-05-13 | Novel two-stage boosting hydraulic impactor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010084675.4A CN111173442B (en) | 2020-02-10 | 2020-02-10 | Novel secondary boosting hydraulic impactor |
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| CN111173442A true CN111173442A (en) | 2020-05-19 |
| CN111173442B CN111173442B (en) | 2024-08-27 |
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| CN202010084675.4A Active CN111173442B (en) | 2020-02-10 | 2020-02-10 | Novel secondary boosting hydraulic impactor |
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| CN (1) | CN111173442B (en) |
| WO (1) | WO2021159621A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114352188A (en) * | 2021-12-31 | 2022-04-15 | 核工业北京地质研究院 | Slide valve type valve control mechanism capable of improving working performance of hydraulic impactor |
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|---|---|---|---|---|
| US6237701B1 (en) * | 1997-11-17 | 2001-05-29 | Tempress Technologies, Inc. | Impulsive suction pulse generator for borehole |
| CN1894076A (en) * | 2003-12-19 | 2007-01-10 | 克拉克设备公司 | Impact tool |
| CN108798500A (en) * | 2017-04-28 | 2018-11-13 | 中石化石油工程技术服务有限公司 | A kind of hydraulical impact device for power drilling tool |
| CN212105719U (en) * | 2020-02-10 | 2020-12-08 | 中国地质大学（北京） | Novel two-stage boosting hydraulic impactor |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
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| DE3823900C1 (en) * | 1988-07-14 | 1989-02-16 | Hans Brochier Gmbh & Co, 8500 Nuernberg, De | |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN114352188A (en) * | 2021-12-31 | 2022-04-15 | 核工业北京地质研究院 | Slide valve type valve control mechanism capable of improving working performance of hydraulic impactor |
| CN114352188B (en) * | 2021-12-31 | 2024-01-12 | 核工业北京地质研究院 | Slide valve type valve control mechanism capable of improving working performance of hydraulic impactor |
Also Published As
| Publication number | Publication date |
|---|---|
| CN111173442B (en) | 2024-08-27 |
| WO2021159621A1 (en) | 2021-08-19 |
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