CN108131100B - Hydraulic oscillator - Google Patents
Hydraulic oscillator Download PDFInfo
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- CN108131100B CN108131100B CN201711487903.7A CN201711487903A CN108131100B CN 108131100 B CN108131100 B CN 108131100B CN 201711487903 A CN201711487903 A CN 201711487903A CN 108131100 B CN108131100 B CN 108131100B
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- liquid guide
- valve shaft
- valve
- flow passage
- guide holes
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- 239000007788 liquid Substances 0.000 claims abstract description 100
- 239000012530 fluid Substances 0.000 claims description 57
- 239000011324 bead Substances 0.000 claims 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 abstract description 20
- 239000002184 metal Substances 0.000 abstract description 5
- 238000012423 maintenance Methods 0.000 abstract description 3
- 238000004519 manufacturing process Methods 0.000 abstract description 3
- 230000015572 biosynthetic process Effects 0.000 abstract 1
- 238000005553 drilling Methods 0.000 description 48
- 230000000694 effects Effects 0.000 description 10
- 210000002445 nipple Anatomy 0.000 description 4
- 230000000737 periodic effect Effects 0.000 description 4
- 238000011144 upstream manufacturing Methods 0.000 description 4
- 238000013461 design Methods 0.000 description 3
- 230000009977 dual effect Effects 0.000 description 3
- 230000010355 oscillation Effects 0.000 description 3
- 239000011435 rock Substances 0.000 description 3
- 230000003068 static effect Effects 0.000 description 3
- 238000004891 communication Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 238000009751 slip forming Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000008094 contradictory effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000000605 extraction Methods 0.000 description 1
- 230000001788 irregular Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 239000011148 porous material Substances 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 230000001360 synchronised effect 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
- E21B7/00—Special methods or apparatus for drilling
- E21B7/24—Drilling using vibrating or oscillating means, e.g. out-of-balance masses
Abstract
The invention relates to a hydraulic oscillator, which comprises a shell, a mandrel, a piston, a spring and a valve shaft assembly, wherein the valve shaft assembly comprises a valve shaft fixedly connected with the shell and a valve sleeve rotatably sleeved on the valve shaft, the valve shaft is provided with an axial flow channel, a backflow flow channel communicated with the axial flow channel and a plurality of first liquid guide holes communicated with the axial flow channel and annularly arranged along the circumferential direction of the valve shaft, the valve sleeve is provided with a plurality of second liquid guide holes annularly arranged along the circumferential direction of the valve sleeve and capable of being communicated with the first liquid guide holes, a turning flow channel is formed when the first liquid guide holes and the second liquid guide holes are communicated, and a severe water hammer phenomenon is formed in the shell through periodical formation and disconnection of the turning flow channel to form oscillating force; an annular flow passage communicated with the backflow flow passage is formed between the valve sleeve and the shell. The valve shaft assembly is an all-metal part, the whole hydraulic oscillator is free of rubber parts, the service life is long, and the equipment production and maintenance cost is low.
Description
Technical Field
The invention belongs to the technical field of oil extraction equipment, and particularly relates to a hydraulic oscillator.
Background
With development of various large oil fields, the number of application of complex structure wells such as high-inclination wells, horizontal wells, multi-branch horizontal wells and the like is increased, wellbores are irregular, well inclination angles are large, friction between a drill string and a well wall in a sliding drilling mode is large, so that the transmission efficiency of drilling pressure is low, and the drilling speed and the extension capacity are severely restricted.
The NOV hydraulic oscillator consists of a power part, a valve shaft assembly and an oscillation nipple, wherein the power part is a 2:1 single screw motor, a valve plate is fixed at the lower end of a motor rotor, and when drilling fluid passes through the power part, the rotor is driven to rotate, and the valve plate moves back and forth along with the tail end of the rotor on a plane due to the movement characteristic of the single screw. The valve shaft assembly is connected with the power part, the main parts are a wear-resistant sleeve and a fixed valve plate, the movable valve plate is tightly matched with the fixed valve plate, and the two valve plates are staggered and overlapped due to rotation of the rotor, so that the effective flow area of the valve shaft assembly is also periodically changed due to periodic relative movement. When the two valves are in minimum coincidence, the effective flow area of the drilling fluid passing through the tool is minimum, and the largest water hammer pressure wave is generated; when the two valves are completely overlapped, the effective flow area of the drilling fluid passing through the tool is maximum, and the generated pressure drop is minimum; the periodic variation in effective flow area results in a synchronous periodic variation in pressure upstream. The power part makes the periodic variation of the upstream pressure act on the piston of the oscillating nipple, and the formed acting force continuously presses the spring therein to form vibration. By periodically changing the fluid pressure, the spring acting inside the oscillating nipple causes the piston of the nipple to reciprocate axially under the dual action of the pressure and the spring, causing other drill strings connected to the tool to reciprocate axially due to the large and small pressure. The hydraulic oscillators enable adjacent drilling tools to longitudinally reciprocate in the well bore, static friction of the drilling tools at the bottom of the well is changed into dynamic friction, friction resistance is greatly reduced, the tool can effectively reduce the phenomenon of drilling tool dragging caused by the well bore track, and effective weight-on-bit of the drilling tools acting on rock is ensured, so that mechanical drilling speed and extensibility are improved.
However, the NOV hydraulic oscillator successfully applied in commercialization also has the outstanding technical contradiction problem that the stator of the single-head screw motor with the power part of 2:1 is rubber, belongs to vulnerable parts, has shorter service life, and the service life of a tool is drastically reduced when higher water hammer frequency is obtained by increasing the rotating speed of a rotor; in addition, when the ratio of the maximum effective flow area to the minimum flow area of the valve shaft assembly is larger by adjusting parameters so as to obtain stronger water hammer force, the hydraulic pressure drop consumed by the tool is increased sharply, the water horsepower of the drill bit is reduced remarkably, the mechanical drilling speed is not increased, and the mechanical drilling speed is reduced.
Disclosure of Invention
The embodiment of the invention relates to a hydraulic oscillator, which can at least solve part of defects in the prior art.
The embodiment of the invention relates to a hydraulic oscillator, which comprises a shell, a mandrel, a piston, a spring and a valve shaft assembly, wherein the mandrel stretches into the shell and is in spline connection with the shell through a spline sleeve, the piston is fixedly connected with the mandrel, the spring is sleeved on the mandrel and is clamped between the piston and the spline sleeve, the valve shaft assembly comprises a valve shaft fixedly connected with the shell and a valve sleeve rotatably sleeved on the valve shaft, the valve shaft is provided with an axial flow channel, a backflow flow channel communicated with the axial flow channel and a plurality of first liquid guide holes communicated with the axial flow channel and circumferentially and annularly arranged along the valve shaft, the valve sleeve is provided with a plurality of second liquid guide holes circumferentially arranged along the valve shaft and communicated with the first liquid guide holes, and when the first liquid guide holes are communicated with the second liquid guide holes, a folding flow channel is formed; an annular flow passage communicated with the backflow flow passage is formed between the valve sleeve and the shell.
As one embodiment, an included angle is formed between the axis of each first liquid guiding hole and the radial line of the valve shaft corresponding to the inlet end of the first liquid guiding hole, and each first liquid guiding Kong Zucheng is a first cyclone liquid guiding channel.
As one embodiment, an included angle is formed between the axis of each second liquid guiding hole and the radial line of the valve sleeve corresponding to the inlet end of the second liquid guiding hole, and the rotation direction of each second liquid guiding Kong Zucheng is opposite to that of the first spiral-flow type liquid guiding channel.
As one embodiment, the number of the first liquid guide holes and the number of the second liquid guide holes are 3-8.
As one embodiment, the turning angle of the turning flow channel is 30-90 degrees.
As one embodiment, the second liquid guiding hole has a larger pore diameter than the first liquid guiding hole.
As one of the embodiments, the backflow passage includes a plurality of backflow holes annularly disposed along the valve shaft, each of the backflow holes being disposed obliquely downward from the annular flow passage side toward the axial flow passage side.
As one embodiment, the inner wall of the valve shaft is in a stepped shaft structure, and the large-diameter section of the inner wall is positioned on one side of the valve shaft, which is close to the piston.
As one of the embodiments, the outer wall of the valve shaft is of a step shaft structure, the small diameter section of the outer wall is located on one side, close to the piston, of the valve shaft, the small diameter section of the outer wall is connected with a locking nut in a threaded mode, and the valve sleeve is sleeved on the small diameter section of the outer wall and is clamped on the step surface of the locking nut and the outer wall of the valve shaft.
As one of the embodiments, the bottom of the housing is connected with a lower joint in a threaded manner, a shoulder is machined on the inner wall of the housing below the piston, the top end of the lock nut is abutted with the shoulder, and the bottom end of the valve shaft is abutted with the lower joint.
The embodiment of the invention has at least the following beneficial effects:
when drilling fluid flows into the valve shaft from the drill rod, most of the fluid is sprayed out from the first fluid guide hole and flows out from the second fluid guide holes, and the drilling fluid can continuously impact the valve sleeve (the hole wall of each second fluid guide hole) due to the action of the above-mentioned turning flow channel for turning the fluid, so that the flowing speed of the drilling fluid in the turning flow channel is unchanged, but the direction is changed severely; according to the principle of conservation of momentum, when drilling fluid flows through each turning flow channel, the momentum of the drilling fluid changes, the reaction force of the drilling fluid generates momentum moment, and the valve sleeve is impacted by the high-speed drilling fluid and acquires energy from the drilling fluid with a certain speed and direction to rotate. Along with the rotation of the valve sleeve, the effective flow areas of the first liquid guide holes of the valve shaft and the second liquid guide holes of the valve sleeve are gradually reduced until the valve sleeve rotates for a certain angle, and all the second liquid guide holes of the valve sleeve are completely staggered with all the first liquid guide holes of the valve shaft, so that all the folded flow passages are closed; due to the inertia effect, the valve sleeve continues to rotate, and the effective flow areas of the first liquid guide holes of the valve shaft and the second liquid guide holes of the valve sleeve are gradually increased, so that the valve sleeve continues to be impacted and rotated by high-speed drilling fluid. Thus, the effective flow area between the valve sleeve and the valve shaft periodically changes from large to small and then from small to large, so that water hammer waves are continuously formed, the hydraulic pressure of the drilling fluid at the upstream periodically changes and acts on the piston, and the formed acting force continuously presses the spring in the shell to form vibration. By periodically varying the fluid pressure within the housing, the piston reciprocates axially under the dual action of the periodically varying pressure and the spring force, causing other drill strings connected to the drilling tool to reciprocate axially. The hydraulic oscillators enable adjacent drilling tools to longitudinally reciprocate in the well bore, static friction of the drilling tools at the bottom of the well is changed into dynamic friction, friction resistance is greatly reduced, the phenomenon that the drilling tools drag due to the well bore track can be effectively reduced, effective weight on bit of the drilling tools acts on rock is guaranteed, and therefore mechanical drilling speed and extensibility are improved.
In the invention, the valve shaft assembly is all metal parts, namely the valve shaft, the valve sleeve and the like are all metal parts, so that the hydraulic oscillator has no rubber parts, long service life and lower equipment production and maintenance cost.
The hydraulic oscillator has the water impact frequency which depends on the number of each liquid guide hole and the rotation rate of the valve sleeve; through reasonable design, the water hammer frequency range is 10-50Hz, and the rotation speed of the valve sleeve can reach 3000r/min, which cannot be realized by a single screw motor.
The oscillating force of the hydraulic oscillator depends on the flow rate of drilling fluid, the intermittent time of flowing and the like, and the hydraulic oscillator has the advantages of simple structure, small consumed hydraulic pressure drop, stronger water hammer phenomenon, larger generated water hammer pressure and larger formed oscillating force, and is an contradictory problem which cannot be overcome by the hydraulic oscillator driven by a single screw motor by adjusting parameters of a valve shaft assembly.
Drawings
In order to more clearly illustrate the embodiments of the invention or the technical solutions in the prior art, the drawings that are required in the embodiments or the description of the prior art will be briefly described, it being obvious that the drawings in the following description are only some embodiments of the invention, and that other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.
Fig. 1 is a schematic structural diagram of a hydraulic oscillator according to an embodiment of the present invention;
FIG. 2 is a schematic illustration of a mounting structure of a valve shaft assembly within a housing according to an embodiment of the present invention;
FIG. 3 is a schematic illustration of a valve shaft assembly according to an embodiment of the present invention;
fig. 4-11 are cross-sectional views taken along A-A in fig. 3, wherein,
fig. 4-9 show schematic diagrams of different numbers of first liquid guide holes and second liquid guide holes;
FIGS. 10 and 11 illustrate a schematic representation of the change in effective flow area of a valve shaft assembly.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
As shown in fig. 1, the embodiment of the invention provides a hydraulic oscillator, which comprises a shell 3, a mandrel 1, a piston 5, a spring 4 and a valve shaft assembly 6; the mandrel 1 extends into the shell 3 and is in spline connection with the shell 3 through the spline housing 2, so that the mandrel 1 can drive the shell 3 to rotate and can slide up and down relative to the shell 3; the piston 5, the spring 4 and the valve shaft assembly 6 are all accommodated in the housing 3, wherein the piston 5 is fixedly connected with the mandrel 1, and is generally fixed in a threaded connection manner, the spring 4 is sleeved on the mandrel 1 and is clamped between the piston 5 and the spline housing 2, and in this embodiment, the spring 4 adopts a disc spring set. Typically, the housing 3, the spindle 1, the piston 5 and the spring 4 are all coaxially arranged; the mandrel 1 and the piston 5 are hollow and can be used for liquid circulation.
As shown in fig. 2 to 11, the valve shaft assembly 6 includes a valve shaft 602 fixedly connected to the housing 3, and a valve sleeve 603 rotatably sleeved on the valve shaft 602, the valve shaft 602 has an axial flow passage, a backflow flow passage communicated with the axial flow passage, and a plurality of first liquid guide holes 6021 communicated with the axial flow passage and circumferentially and annularly arranged along the valve shaft 602, the valve sleeve 603 has a plurality of second liquid guide holes 6031 circumferentially and annularly arranged along the valve shaft and capable of being communicated with each of the first liquid guide holes 6021, and the first liquid guide holes 6021 and the second liquid guide holes 6031 form a diversion flow passage when being communicated; an annular flow passage 606 for communicating with the return flow passage is formed between the valve housing 603 and the housing 3. The valve shaft 602 is a hollow structure penetrating up and down, so that drilling fluid can conveniently enter the shaft cavity of the valve shaft 602 and flow into the upper part of the valve shaft 602 to be in contact with the piston 5; the valve sleeve 603 is sleeved on the valve shaft 602 and can rotate relative to the valve shaft 602, and generally, the valve sleeve 603 and the valve shaft 602 are in a tightly sleeved structure, i.e. the inner diameter of the valve sleeve 603 is basically the same as the outer diameter of the valve shaft 602; the above-mentioned turning flow channel is that the liquid flows through the turning flow channel, specifically, the liquid turns during the process of flowing from the first liquid guiding hole 6021 into the second liquid guiding hole 6031. The liquid flowing out of the second pilot holes 6031 of the valve housing 603 enters the annular flow passage 606 and then enters the axial flow passage through the return flow passage.
Based on the above structure, when the drilling fluid flows into the valve shaft 602 from the drill pipe, most of the fluid is ejected from the first fluid guide hole 6021 and flows out from the second fluid guide hole 6031, and due to the above-mentioned effect of turning the fluid in the turning flow passage, the drilling fluid can continuously impact the valve sleeve 603 (the hole wall of each second fluid guide hole 6031), and the flow speed of the drilling fluid in the turning flow passage is unchanged, but the direction is changed drastically; as known from the principle of conservation of momentum, when drilling fluid flows through each of the turning channels, the momentum thereof changes, and the reaction force thereof generates moment of momentum, so that the valve sleeve 603 receives the impact of the drilling fluid at a high speed and obtains energy from the drilling fluid having a certain speed and direction, thereby rotating. As the valve sleeve 603 rotates, the effective flow areas of the first fluid guide holes 6021 of the valve shaft 602 and the second fluid guide holes 6031 of the valve sleeve 603 gradually decrease until the valve sleeve 603 rotates by a certain angle, and each second fluid guide hole 6031 of the valve sleeve 603 is completely staggered with each first fluid guide hole 6021 of the valve shaft 602, so that each folded flow channel is closed; due to the inertia effect, the valve sleeve 603 continues to rotate, and the effective flow areas of the first fluid guide holes 6021 of the valve shaft 602 and the second fluid guide holes 6031 of the valve sleeve 603 gradually increase, so that the valve sleeve 603 continues to rotate under the impact of high-speed drilling fluid. In this way, as the effective flow area between the valve housing 603 and the valve shaft 602 periodically changes, the effective flow area changes from large to small and then from small to large, so that a water hammer wave is continuously formed, the upstream drilling fluid pressure periodically changes and acts on the piston 5, and the formed acting force continuously presses the spring 4 in the housing 3 to form vibration. By periodically varying the fluid pressure in the housing 3, the piston 5 reciprocates axially under the dual action of the periodically varying pressure and the force of the spring 4, causing other drill strings connected to the drilling tool to reciprocate axially. The hydraulic oscillators enable adjacent drilling tools to longitudinally reciprocate in the well bore, static friction of the drilling tools at the bottom of the well is changed into dynamic friction, friction resistance is greatly reduced, the phenomenon that the drilling tools drag due to the well bore track can be effectively reduced, effective weight on bit of the drilling tools acts on rock is guaranteed, and therefore mechanical drilling speed and extensibility are improved.
In this embodiment, the valve shaft assembly 6 is an all-metal member, that is, the valve shaft 602, the valve sleeve 603, etc. are all metal members, so that the hydraulic oscillator has no rubber member, long service life and low production and maintenance costs.
The hydraulic oscillator has a water hammer frequency which depends on the number of the liquid guide holes and the rotation rate of the valve sleeve 603; by reasonable design, the water hammer frequency range is 10-50Hz, and the rotating speed of the valve sleeve 603 can reach 3000r/min, which cannot be realized by a single screw motor.
The oscillating force of the hydraulic oscillator depends on the flow rate of drilling fluid, the intermittent time of flowing and the like, and the hydraulic oscillator has a simple structure, small consumed hydraulic pressure drop, and can lead the water hammer phenomenon to be more severe, lead the generated water hammer pressure to be larger and lead the oscillating force to be larger by adjusting the parameters of the valve shaft assembly 6, thus being the contradiction problem which can not be overcome by the hydraulic oscillator driven by a single screw motor.
The parameters of the valve shaft assembly 6 are further optimized:
for the above-mentioned designs of the first fluid guiding hole 6021 and the second fluid guiding hole 6031, there may be various embodiments, for example, the first fluid guiding hole 6021 may be radially opened along the valve shaft 602, and the second fluid guiding hole 6031 is a non-radial hole; in this embodiment, in order to obtain a better oscillation effect, as shown in fig. 4 to 11, preferably, an included angle is formed between the axis of each first liquid guiding hole 6021 and the radial line of the valve shaft 602 corresponding to the inlet end of the first liquid guiding hole 6021, and each first liquid guiding hole 6021 forms a first rotational flow type liquid guiding channel. As a preferred embodiment, the first liquid guiding holes 6021 are uniformly and annularly arranged on the side wall of the valve shaft 602, that is, the included angles between the axes of the first liquid guiding holes 6021 and the radial lines of the valve shaft 602 corresponding to the inlet ends of the first liquid guiding holes 6021 are the same, the circumferential spacing between the inlets of every two adjacent first liquid guiding holes 6021 is the same along the circumferential direction of the inner wall of the valve shaft 602, and the circumferential spacing between the outlets of every two adjacent first liquid guiding holes 6021 is the same along the circumferential direction of the outer wall of the valve shaft 602. Further preferably, an included angle is formed between the axis of each second fluid guiding hole 6031 and the radial line of the valve sleeve 603 corresponding to the inlet end of the second fluid guiding hole 6031, and each second fluid guiding hole 6031 forms a second rotational flow type fluid guiding channel, and the rotation direction of the second rotational flow type fluid guiding channel is opposite to that of the first rotational flow type fluid guiding channel. Likewise, each second pilot hole 6031 is preferably uniformly annularly disposed on the sidewall of the valve housing 603. In the embodiment of fig. 4 to 9, the first cyclone-type liquid guiding channel formed by the first liquid guiding holes 6021 is clockwise, and the second cyclone-type liquid guiding channel formed by the second liquid guiding holes 6031 is anticlockwise; vice versa. By adopting the structure, the steering effect of the steering flow channel formed by the conduction of each first liquid guide hole 6021 and each second liquid guide hole 6031 is good, the drilling fluid sprayed out of the first liquid guide holes 6021 can directly impact the hole wall of the second liquid guide holes 6031 so as to impact the valve sleeve 603 at a high speed, the water hammer phenomenon is more severe, the generated water hammer pressure is larger, and the formed oscillating force is larger.
As a possible embodiment, as shown in fig. 4 to fig. 9, the number of the first liquid guiding holes 6021 and the second liquid guiding holes 6031 is 3 to 8, and the number of the first liquid guiding holes 6021 and the second liquid guiding holes 6031 may be the same or different, preferably, the number of the first liquid guiding holes 6021 and the second liquid guiding holes 6031 are designed to be the same and correspond to each other one by one, when one liquid guiding hole is communicated with one second liquid guiding hole 6031, the other first liquid guiding holes 6021 are communicated with one second liquid guiding hole 6031 one by one, or the number of the first liquid guiding holes 6021 is less than the number of the second liquid guiding holes 6031, so that a better water impact effect can be obtained;
as a possible embodiment, as shown in fig. 4 to 9, the turning angle of the turning flow channel is 30 ° to 90 °, so that the impact effect on the valve sleeve 603 can be satisfied;
as a possible embodiment, as shown in fig. 4 to fig. 9, the aperture of the second liquid guiding hole 6031 is larger than that of the first liquid guiding hole 6021, so that the communication time between the first liquid guiding hole 6021 and the second liquid guiding hole 6031 can be prolonged, and the water hammer effect is better.
As a possible embodiment, as shown in fig. 2 and fig. 3, the height of the first liquid guiding hole 6021 and the height of the second liquid guiding hole 6031 are preferably the same, and the height of the first liquid guiding hole 6021 occupies 1/3-1/2 of the axial flow channel length of the valve shaft 602, so as to ensure the matched communication flow between the two;
as a possible embodiment, as shown in fig. 2 and fig. 3, the inner wall of the valve shaft 602 has a stepped shaft structure, and the large diameter section of the inner wall is located at the side of the valve shaft 602 close to the piston 5, that is, the axial flow path of the valve shaft 602 has a diameter-changing process, and further, the inner tube of the valve shaft 602 has a venturi structure, so that the fluid flow rate around each first liquid guiding hole 6021 can be effectively increased, and the water impact effect and the oscillation effect are better.
Continuing with the structure of the hydraulic oscillator, as shown in fig. 2 and 3, the return channel includes a plurality of return holes 605 annularly disposed along the circumference of the valve shaft 602, each return hole 605 is disposed obliquely downward from the annular flow channel 606 to the axial flow channel, and the drilling fluid thrown out through the valve sleeve 603 can quickly return to the axial flow channel. In this embodiment, the number of the reflow holes 605 is 3 to 6, preferably 4.
Continuing the structure of the hydraulic oscillator, as shown in fig. 2 and 3, the outer wall of the valve shaft 602 is in a stepped shaft structure, the small diameter section of the outer wall is positioned on one side of the valve shaft 602 close to the piston 5, the small diameter section of the outer wall is screwed with the locking nut 601, and the valve sleeve 603 is sleeved on the small diameter section of the outer wall and is clamped on the stepped surface of the outer wall of the locking nut 601 and the valve shaft 602. The valve sleeve 603 can be sleeved with the valve shaft 602 through a plurality of annular bearings, so that the relative rotation between the two is smooth. Further, as shown in fig. 2, the bottom of the housing 3 is screwed with a lower joint, a shoulder is machined on the inner wall of the housing 3 below the piston 5, the top end of the lock nut 601 abuts against the shoulder, and the bottom end of the valve shaft 602 abuts against the lower joint. The lock nut 601 is provided with a seal ring, and can be in sealing contact with the inside of the housing 3.
The foregoing description of the preferred embodiments of the invention is not intended to be limiting, but rather is intended to cover all modifications, equivalents, alternatives, and improvements that fall within the spirit and scope of the invention.
Claims (6)
1. The utility model provides a hydraulic oscillator, includes casing, dabber, piston, spring and valve shaft assembly, the dabber stretch into in the casing and through the spline housing with casing spline connection, the piston with the dabber links firmly, the spring housing is located the dabber is just pressed from both sides and is located the piston with between the spline housing, its characterized in that:
the valve shaft assembly comprises a valve shaft fixedly connected with the shell and a valve sleeve rotatably sleeved on the valve shaft, the valve shaft is provided with an axial flow passage, a backflow flow passage communicated with the axial flow passage and a plurality of first liquid guide holes communicated with the axial flow passage and annularly arranged along the circumferential direction of the valve shaft, the valve sleeve is provided with a plurality of second liquid guide holes annularly arranged along the circumferential direction of the valve sleeve and communicated with the first liquid guide holes, and a diversion flow passage is formed when the first liquid guide holes and the second liquid guide holes are communicated; an annular flow passage communicated with the backflow flow passage is formed between the valve sleeve and the shell;
an included angle is formed between the axis of each first liquid guide hole and the radial line of the valve shaft corresponding to the inlet end of the first liquid guide hole, and each first liquid guide Kong Zucheng is a first spiral-flow type liquid guide channel;
an included angle is formed between the axis of each second liquid guide hole and the radial line of the valve sleeve corresponding to the inlet end of the second liquid guide hole, each second liquid guide Kong Zucheng is a second rotational flow type liquid guide channel, and the rotation direction of the second rotational flow type liquid guide channel is opposite to that of the first rotational flow type liquid guide channel;
the valve shaft inner tube is in a venturi structure so as to increase the fluid flow rate around each first liquid guide hole;
the backflow flow passage comprises a plurality of backflow holes which are annularly arranged along the circumferential direction of the valve shaft, and each backflow hole is obliquely arranged downwards from the side of the annular flow passage to the side of the axial flow passage.
2. The hydraulic oscillator of claim 1, wherein: the number of the first liquid guide holes and the number of the second liquid guide holes are 3-8.
3. The hydraulic oscillator of claim 1, wherein: the turning angle of the turning flow channel is 30-90 degrees.
4. The hydraulic oscillator of claim 1, wherein: the aperture of the second liquid guide hole is larger than that of the first liquid guide hole.
5. The hydraulic oscillator of claim 1, wherein: the valve shaft outer wall is of a step shaft structure, the outer wall small-diameter section is located on one side, close to the piston, of the valve shaft, the locking nut is screwed on the outer wall small-diameter section, and the valve sleeve is sleeved on the outer wall small-diameter section and clamped on the locking nut and the valve shaft outer wall step surface.
6. The hydraulic oscillator of claim 5, wherein: the casing bottom threaded connection has the lower part to connect, in the piston below processing has the circular bead on the casing inner wall, lock nut top with the circular bead butt, the valve shaft bottom with the lower part connects the butt.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711487903.7A CN108131100B (en) | 2017-12-29 | 2017-12-29 | Hydraulic oscillator |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711487903.7A CN108131100B (en) | 2017-12-29 | 2017-12-29 | Hydraulic oscillator |
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| CN108131100A CN108131100A (en) | 2018-06-08 |
| CN108131100B true CN108131100B (en) | 2024-01-30 |
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| CN201711487903.7A Active CN108131100B (en) | 2017-12-29 | 2017-12-29 | Hydraulic oscillator |
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Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111425157B (en) * | 2020-05-02 | 2021-11-19 | 东北石油大学 | Hydraulic oscillation system |
| GB2606562B (en) * | 2021-05-13 | 2023-08-30 | Rotojar Innovations Ltd | Downhole drag reduction apparatus |
| EP4263999A1 (en) * | 2020-12-16 | 2023-10-25 | Rotojar Innovations Limited | Downhole drag reduction apparatus |
| CN113006680B (en) * | 2021-03-19 | 2022-10-28 | 成都欧维恩博石油科技有限公司 | Low-pressure-loss torsion impact drilling tool and rock breaking method |
| CN114293940B (en) * | 2021-12-31 | 2023-07-18 | 杰瑞能源服务有限公司 | Power device and drilling and grinding tool |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104405287A (en) * | 2014-10-19 | 2015-03-11 | 长江大学 | Dual-pulse hydraulic oscillator for well drilling |
| CN105952383A (en) * | 2016-07-04 | 2016-09-21 | 海斯比得（武汉）石油科技有限公司 | Drill bit, drilling tool and partial underbalance drilling method |
| CN106894756A (en) * | 2017-04-13 | 2017-06-27 | 西南石油大学 | A kind of hydraulic blow helicoid hydraulic motor |
| CN107503686A (en) * | 2017-09-05 | 2017-12-22 | 中国石油大学(华东) | A kind of torsion spring type hydroscillator |
| CN207750052U (en) * | 2017-12-29 | 2018-08-21 | 海斯比得（武汉）石油科技有限公司 | Hydroscillator |
Family Cites Families (1)
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| US8181719B2 (en) * | 2009-09-30 | 2012-05-22 | Larry Raymond Bunney | Flow pulsing device for a drilling motor |
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Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104405287A (en) * | 2014-10-19 | 2015-03-11 | 长江大学 | Dual-pulse hydraulic oscillator for well drilling |
| CN105952383A (en) * | 2016-07-04 | 2016-09-21 | 海斯比得（武汉）石油科技有限公司 | Drill bit, drilling tool and partial underbalance drilling method |
| CN106894756A (en) * | 2017-04-13 | 2017-06-27 | 西南石油大学 | A kind of hydraulic blow helicoid hydraulic motor |
| CN107503686A (en) * | 2017-09-05 | 2017-12-22 | 中国石油大学(华东) | A kind of torsion spring type hydroscillator |
| CN207750052U (en) * | 2017-12-29 | 2018-08-21 | 海斯比得（武汉）石油科技有限公司 | Hydroscillator |
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