1. A three-dimensional vibration hydroscillator is characterized in that: the turbine structure comprises a pipe body (1), wherein an eccentric turbine (3) is arranged in the pipe body (1), a sliding sleeve structure capable of rotating relatively is formed between the outer wall of the eccentric turbine (3) and the inner wall of the pipe body (1), an inclined hole (35) which is through along the axial direction is formed in the turbine body (30) of the eccentric turbine (3), an included angle (a) is formed between the inclined hole (35) and the axis of the pipe body (1), an inner sleeve (39) is arranged on the inner wall of the inclined hole (35), and a turbine blade (31) is fixedly arranged in the inner sleeve (39);

still be equipped with in body (1) and decide valve block (4), decide downstream that valve block (4) are located eccentric turbine (3), and eccentric turbine (3) and decide valve block (4) contact are equipped with on deciding valve block (4) along body (1) axial through's discharge orifice (41), and discharge orifice (41) are eccentric hole.

2. A three-dimensional vibratory hydroscillator as defined in claim 1 wherein: the turbine blade (31) is a plurality of helical blades arranged along the circumference of the inner wall of the inner sleeve (39), and the centers of the helical blades are connected with each other through a connecting column (36).

3. A three-dimensional vibratory hydroscillator as defined in claim 1 wherein: a limiting step (13) is further arranged at one end, close to the downstream, of the pipe body (1), and the fixed valve plate (4) is fixedly arranged on the limiting step (13);

the size of the through-flow section between the inclined hole (35) and the overflowing hole (41) of the eccentric turbine (3) changes periodically along with the rotation of the eccentric turbine (3).

4. A three-dimensional vibratory hydroscillator as claimed in any one of claims 1 to 3 wherein: the end of the inclined hole (35) of the eccentric turbine (3) close to the upstream is concentric with the pipe body (1), and the end close to the downstream is eccentric with the pipe body (1).

5. The three-dimensional vibratory hydroscillator of claim 4 wherein: the inner sleeve (39) is axially divided into a helical section (37) and a linear section (38);

the spiral section (37) is internally provided with turbine blades (31), and the spiral section (37) is positioned at one end of the inner sleeve (39) close to the upstream; the straight line section (38) is positioned at one end close to the downstream, and the turbine blade (31) is not arranged in the straight line section (38).

6. The three-dimensional vibratory hydroscillator of claim 4 wherein: a guide shell (2) is fixedly arranged at the upstream of the eccentric turbine (3), a guide hole (21) is arranged in the guide shell (2), the guide hole (21) is of an inverted cone structure, the inner diameter of one end close to the upstream is larger, the inner diameter of one end close to the downstream is smaller, and the downstream end face of the guide shell (2) is in contact with the end face of the eccentric turbine (3);

the downstream end of the diversion hole (21) is concentric with the inclined hole (35) at the downstream end.

7. A three-dimensional vibratory hydroscillator as defined in claim 6 wherein: an end face sealing ring (34) is arranged between the downstream end face of the guide cylinder (2) and the end face of the eccentric turbine (3);

an outer wall bearing (32) is arranged between the outer wall of the eccentric turbine (3) and the inner wall of the pipe body (1), and at least two groups of outer wall bearings (32) are arranged along the axial direction;

an end face bearing (33) is arranged between the end face of the eccentric turbine (3) and the end face of the fixed valve plate (4).

8. A method for processing a three-dimensional vibratory hydroscillator as defined in any of claims 1-7, comprising the steps of:

s1, machining and molding the turbine blade (31);

s2, welding the turbine blades (31) together through connecting columns (36) to form a turbine blade assembly;

s3, finishing the outer contour shape of the turbine blade assembly;

s4, fixing the turbine blade assembly in the inner sleeve (39);

s5, processing an inclined hole (35) on the turbine body (30);

the axis of the inclined hole (35) and the axis of the turbine body (30) form an included angle (a);

the axis of the inclined hole (35) intersects the axis of the turbine body (30) at a position near the upstream end of the turbine body (30);

s6, fixedly arranging the inner sleeve (39) in the inclined hole (35);

the eccentric turbine (3) is processed through the steps.

9. A method of processing as claimed in claim 8, wherein: the inner sleeve (39) is axially divided into a helical section (37) and a linear section (38);

the spiral section (37) is internally provided with turbine blades (31), and the spiral section (37) is positioned at one end of the inner sleeve (39) close to the upstream; the straight line section (38) is positioned at one end close to the downstream, and the turbine blade (31) is not arranged in the straight line section (38);

the turbine blade (31) is adjacent the upstream end of the turbine body (30).

10. A method of processing as claimed in claim 8, wherein: a plurality of welding holes (301) are formed in the wall of the inner sleeve (39), the positions of the welding holes (301) correspond to the outer edge positions of the turbine blades (31), and the turbine blades (31) are welded and connected through the welding holes (301).

Background

At present, the drilling of an oil field is developed into a directional well and a horizontal well from a vertical well, a drilling tool is usually tightly attached to a lower side well wall, the friction of the drilling tool on the well wall is overlarge, the drilling efficiency is influenced, and the drilling pressure is difficult to transfer to a drill bit. In order to overcome the defect, the static friction of the drilling tool is changed into dynamic friction by adopting a hydraulic oscillator in the prior art so as to reduce the friction resistance. The conventional hydraulic oscillator generally has three structures, namely 1, a screw motor structure, wherein a screw drives a moving plate to rotate, so that the through-flow section of a hole between the moving plate and a static plate is periodically changed, and vibration is generated. The method has the problems that the pressure consumption is high and generally reaches 3-4 MPa, the service life is generally less than 500 hours, and the price of a screw motor is very high, for example, the structure is similar to that in Chinese patent document CN 205778542U. 2. The jet structure utilizes the vortex cavity to generate vibration and utilizes the periodic variation of a pressure medium to generate high-frequency vibration, but the pressure loss of the scheme is only 0.2-0.3 Mpa, the frequency is high, and the frequency cannot be controlled. Such as the structure in chinese patent document CN 104963624A. 3. The turbine structure is configured to generate vibration by periodically changing a flow cross section of a hole between the rotor and the stator by rotating the rotor by the turbine rotor. The problem that this scheme exists is that, the structure is comparatively complicated, and rotating member is too much, and is with high costs, and the loss is higher, and turbine rotor rotational speed is higher, makes the output frequency of instrument higher, and is difficult to control, and life is also shorter. For example, the structures described in chinese patent documents CN104895517A and CN 104405287A, CN 211648054U. However, various schemes in the prior art have the problems of complex structure and high processing cost, and the existing tools are difficult to completely meet the construction requirements along with the increase of the length of the well.

Disclosure of Invention

The invention aims to solve the technical problem of providing a three-dimensional vibration hydraulic oscillator, which can overcome the problem of underground pressure supporting by a simplified structure, realize three-dimensional vibration of radial vibration and axial vibration by lower pressure consumption and reduce the use cost.

Another technical problem to be solved by the present invention is to provide a method for processing a three-dimensional vibratory hydroscillator, which can conveniently and precisely prepare an eccentric turbine as a core component in the three-dimensional vibratory hydroscillator.

In order to solve the technical problems, the technical scheme adopted by the invention is as follows: a three-dimensional vibration hydraulic oscillator comprises a pipe body, wherein an eccentric turbine is arranged in the pipe body, a sliding sleeving structure capable of rotating relatively is formed between the outer wall of the eccentric turbine and the inner wall of the pipe body, an inclined hole penetrating along the axial direction is formed in the turbine body of the eccentric turbine, an included angle is formed between the inclined hole and the axis of the pipe body, an inner sleeve is arranged on the inner wall of the inclined hole, and a turbine blade is fixedly arranged in the inner sleeve;

the fixed valve plate is arranged in the pipe body and is positioned at the downstream of the eccentric turbine, the eccentric turbine is in contact with the fixed valve plate, and the fixed valve plate is provided with a through hole which is axially communicated with the pipe body and is an eccentric hole.

In a preferred embodiment, the turbine blade is a plurality of helical blades arranged along the circumference of the inner wall of the inner sleeve, and the centers of the helical blades are connected with each other through a connecting column.

In the preferred scheme, one end of the pipe body close to the downstream is also provided with a limiting step, and the fixed valve plate is fixedly arranged on the limiting step;

the size of the through-flow section between the inclined hole and the overflowing hole of the eccentric turbine is periodically changed along with the rotation of the eccentric turbine.

In a preferred scheme, one end of the inclined hole of the eccentric turbine close to the upstream is in a concentric structure with the pipe body, and one end of the inclined hole close to the downstream is in an eccentric structure with the pipe body.

In a preferred scheme, the inner sleeve is axially divided into a spiral section and a straight section;

turbine blades are arranged in the spiral section, and the spiral section is positioned at one end of the inner sleeve close to the upstream; the straight line section is positioned at one end close to the downstream, and no turbine blade is arranged in the straight line section.

In the preferred scheme, a guide cylinder is fixedly arranged at the upstream of the eccentric turbine, a guide hole is arranged in the guide cylinder, the guide hole is of an inverted cone structure, the inner diameter of one end close to the upstream is larger, the inner diameter of one end close to the downstream is smaller, and the downstream end surface of the guide cylinder is in contact with the end surface of the eccentric turbine;

the downstream end of the diversion hole is concentric with the inclined hole at the downstream end.

In the preferred scheme, an end face sealing ring is arranged between the downstream end face of the guide cylinder and the end face of the eccentric turbine;

an outer wall bearing is arranged between the outer wall of the eccentric turbine and the inner wall of the pipe body, and at least two groups of outer wall bearings are arranged along the axial direction;

an end face bearing is arranged between the end face of the eccentric turbine and the end face of the fixed valve plate.

A method for manufacturing the three-dimensional vibratory hydroscillator described above, comprising the steps of:

s1, machining and forming the turbine blade;

s2, welding the turbine blades together through connecting columns to form a turbine blade assembly;

s3, finishing the outer contour shape of the turbine blade assembly;

s4, fixing the turbine blade assembly in the inner sleeve;

s5, processing an inclined hole on the turbine body;

the axis of the inclined hole and the axis of the turbine body form an included angle;

the axis of the angled bore intersects the axis of the turbine body at a location proximate the upstream end of the turbine body;

s6, fixing the inner sleeve in the inclined hole;

the eccentric turbine is machined through the steps.

In a preferred scheme, the inner sleeve is axially divided into a spiral section and a straight section;

turbine blades are arranged in the spiral section, and the spiral section is positioned at one end of the inner sleeve close to the upstream; the straight line section is positioned at one end close to the downstream, and no turbine blade is arranged in the straight line section;

the turbine blades are adjacent the upstream end of the turbine body.

In a preferred embodiment, the wall of the inner sleeve is provided with a plurality of welding holes, the positions of the welding holes correspond to the outer edge positions of the turbine blades, and the turbine blades are welded and connected through the welding holes.

The invention provides a three-dimensional vibration hydraulic oscillator, which adopts the scheme of an eccentric turbine, combines an inclined hole of the eccentric turbine and a fixed valve plate with the eccentric hole into a valve group with a variable flow cross section, can generate composite vibration, comprises superimposed radial vibration and axial vibration, is more favorable for the transmission of vibration waves, converts the static friction of a drilling tool in an effect coverage range into dynamic friction, solves the problem of underground pressure supporting, and is more favorable for the transmission of underground drilling pressure. The structure is greatly simplified, the pressure loss is low, a plurality of the fixed valve plates can be connected in series on the drilling tool at intervals, so that the vibration effect is fully transmitted to each section of the drilling tool, and in a further preferable scheme, the fixed valve plates with different eccentric distances can be conveniently replaced to adapt to different geological structures, so that the pressure loss and the vibration effect are in the optimal state. The preparation method provided by the invention can be used for processing the eccentric turbine with a complex structure in a convenient manner, thereby solving the manufacturing problem of the eccentric turbine.

Drawings

The invention is further illustrated by the following examples in conjunction with the accompanying drawings:

fig. 1 is a front sectional view of an eccentric turbine of the present invention.

FIG. 2 is an exploded perspective view of the inner sleeve and turbine blade of the present invention.

Fig. 3 is a front view of the present invention.

Fig. 4 is a sectional view a-a of fig. 3.

Fig. 5 is a sectional view B-B of fig. 4.

Fig. 6 is a schematic diagram of the vibration curve of the present invention.

In the figure: the device comprises a pipe body 1, an outer cone connector 11, an inner cone connector 12, a limiting step 13, a guide cylinder 2, a guide hole 21, an eccentric turbine 3, a turbine blade 31, an outer wall bearing 32, an end face bearing 33, an end face sealing ring 34, an inclined hole 35, a connecting column 36, a spiral section 37, a straight line section 38, an inner sleeve 39, a turbine body 30, a welding hole 301, a fixed valve plate 4, an overflowing hole 41 and an included angle a.

Detailed Description

Example 1:

a three-dimensional vibration hydraulic oscillator comprises a pipe body 1, wherein an eccentric turbine 3 is arranged in the pipe body 1, a sliding sleeve structure capable of rotating relatively is formed between the outer wall of the eccentric turbine 3 and the inner wall of the pipe body 1, an inclined hole 35 which penetrates through the eccentric turbine 3 along the axial direction is formed in a turbine body 30 of the eccentric turbine 3, an included angle a is formed between the inclined hole 35 and the axis of the pipe body 1, an inner sleeve 39 is arranged on the inner wall of the inclined hole 35, and a turbine blade 31 is fixedly arranged in the inner sleeve 39;

still be equipped with fixed valve piece 4 in body 1, fixed valve piece 4 is located eccentric turbine 3's low reaches, and eccentric turbine 3 contacts with fixed valve piece 4, is equipped with the discharge orifice 41 that link up along body 1 axial on the fixed valve piece 4, and discharge orifice 41 is the eccentric orfice. The size of the flow cross section between the inclined bore 35 and the through-flow bore 41 of the eccentric turbine 3 varies cyclically with the rotation of the eccentric turbine 3. From this structure, when pressure medium passes through eccentric turbine 3, drive eccentric turbine 3 and rotate promptly, because eccentric turbine 3 is eccentric structure, drive whole body 1 and produce radial vibration, when body 1 connects in series on the drilling tool through the outer cone connector 11 and the interior cone connector 12 at both ends, then will vibrate and transmit the drilling tool with the mode of transverse wave. As shown in fig. 5, the size of the flow cross section between the eccentric bore of the eccentric turbine 3 and the flow passage 41 varies cyclically with the rotation of the eccentric turbine 3. Due to the change of the through-flow cross section, the pressure medium generates periodic vibration and transmits the vibration to the drilling tool in the form of longitudinal waves, so that axial vibration is formed, and the vibration pattern is shown in fig. 6. Preferably, the eccentricity of the overflowing hole 41 of the fixed valve plate 4 can be adjusted by replacement, so that the fixed valve plate can be adapted to different underground geological conditions, and the optimal effect can be achieved. The optimization effect in this example means that a balance is achieved between the anti-back-pressure effect, the pressure loss and the use cost. Through measurement and calculation, the structure of the invention is simplified, so the production and manufacturing cost is greatly reduced, the volume is correspondingly reduced, even if a plurality of rotating tools are connected in series, the total pressure consumption and the use cost are lower than those of the screw motor type hydraulic oscillator with better oscillation effect in the prior art. The inner sleeve 39 is adopted, and the turbine blade 31 is arranged in the inner sleeve 39, so that the processing difficulty of the eccentric turbine 3 is greatly reduced, and the technical problem of arranging the turbine blade 31 in the inclined hole 35 is particularly solved.

In a preferred embodiment, as shown in fig. 4, the turbine blade 31 is a plurality of helical blades arranged along the circumference of the inner wall of the inner sleeve 39, and the centers of the helical blades are connected to each other by a connecting column 36. Preferably, the turbine blades 31 are three to four spiral blades uniformly arranged along the circumference of the inner wall of the inclined hole 35, each spiral blade is spaced apart by 120 ° in the circumference, and the middle portions of each spiral blade are connected to each other. When the pressure medium passes through the turbine blades 31, the eccentric turbine 3 is rotated. Preferably, each helical blade is welded together by a connecting post 36.

In a preferred embodiment, as shown in fig. 4, a limiting step 13 is further disposed at one end of the pipe body 1 near the downstream, and the fixed valve plate 4 is fixedly disposed on the limiting step 13. In an alternative, the limiting step 13 is formed on the inner wall of the pipe body 1 by machining, and in another alternative, the limiting step 13 is formed by a collar fixedly mounted, for example, by interference fitting or thread fitting. The position of the limiting step 13 is fixedly provided with a fixed valve plate 4, the fixed valve plate 4 and the inner wall of the pipe body 1 are circumferentially positioned through threads or mutually meshed grooves, and the axial positioning is realized through the limiting step 13; or the end surface of the fixed valve plate 4 and the limiting step 13 are circumferentially positioned through mutually meshed grooves, and the axial positioning is realized through the limiting step 13.

In a preferred embodiment, as shown in fig. 4, the inclined hole 35 of the eccentric turbine 3 is concentrically arranged with the pipe 1 at the upstream end, and is eccentrically arranged with the pipe 1 at the downstream end. Upstream in this example refers to the left side in fig. 4, and downstream refers to the right side in fig. 4. With the structure, the eccentric turbine 3 can be driven to rotate more conveniently, and the eccentric turbine 3 is prevented from being clamped. And is convenient to be matched with the guide cylinder 2 to reduce the axial pressure of the eccentric turbine 3. The eccentric turbine 3 is prevented from being pressed on the fixed valve plate 4 due to overhigh pressure of the pressure medium.

In the preferred embodiment, the inner sleeve 39 is divided axially into a helical section 37 and a straight section 38;

the turbine blades 31 are arranged in the spiral section 37, and the spiral section 37 is positioned at one end of the inner sleeve 39 close to the upstream; the straight section 38 is located at the end near the downstream end, and no turbine blades 31 are provided in the straight section 38. With this structure, the range of variation of the flow cross section can be made larger with the same pipe diameter. See the structure in fig. 1, 2.

In a preferred scheme, as shown in fig. 4, a guide shell 2 is fixedly arranged at the upstream of an eccentric turbine 3, a guide hole 21 is arranged in the guide shell 2, the guide hole 21 is of an inverted cone structure, the inner diameter of one end close to the upstream is larger, the inner diameter of one end close to the downstream is smaller, and the downstream end face of the guide shell 2 is in contact with the end face of the eccentric turbine 3;

the downstream end of the pilot hole 21 is concentric with the inclined hole 35. The guide shell 2 has the function of reducing the axial pressure of the eccentric turbine 3. And secondly, the flow velocity of the pressure medium is improved, so that the pressure medium can better do work on the turbine blades 31 to drive the eccentric turbine 3 to rotate. In a further preferred scheme, a conical guide cap is arranged at the downstream central position of the guide cylinder 2, and the tip of the guide cap is aligned with the upstream so that the pressure medium acts on the position of the root of the turbine blade 31 more. The structure of the deflector cap is not shown in the figures.

In a preferred scheme, as shown in fig. 4, an end face seal ring 34 is arranged between the downstream end face of the guide shell 2 and the end face of the eccentric turbine 3; since the eccentric turbine 3 is mainly subjected to pressure from left to right in fig. 4, the sealing ring 34 is provided there to form a seal and compensate for the change in clearance due to axial play of the eccentric turbine 3.

An outer wall bearing 32 is arranged between the outer wall of the eccentric turbine 3 and the inner wall of the pipe body 1, and at least two groups of the outer wall bearings 32 are arranged along the axial direction; preferably, the outer wall bearing 32 in this example is a teflon sliding bearing. The outer wall bearing 32 is configured as an annular inlay or a plurality of columnar inlays. It is also possible to use ball bearings.

An end face bearing 33 is arranged between the end face of the eccentric turbine 3 and the end face of the fixed valve plate 4. To withstand the axial pressure of the eccentric turbine 3. The end face bearing 33 is preferably a teflon plain bearing. It is also possible to use ball bearings. The invention has the advantage of being capable of obtaining higher processing precision. Is suitable for manufacturing and production of small batches.

Example 2:

the scheme in the embodiment 1 can realize the radial and axial compound vibration of the drilling tool with a simplified structure, has low realization cost and wide application prospect, but has larger processing difficulty of the eccentric turbine 3. In order to solve the technical problem. On the basis of embodiment 1, a method for manufacturing the three-dimensional vibratory hydroscillator comprises the following steps:

s1, machining and forming the turbine blade 31; the turbine blades 31 are typically rolled on a dedicated rolling roller apparatus.

S2, welding the turbine blades 31 together through connecting columns 36 to form a turbine blade assembly; a tool for fixing the turbine blade 31 is required in the welding process to ensure the connection accuracy between the turbine blade 31 and the connecting column 36.

S3, finishing the outer contour shape of the turbine blade assembly; the outer contour shape here refers to the contour shape of the turbine blade assembly in the axial and radial projection planes. The finish machining comprises cylindrical grinding machining.

S4, fixing the turbine blade assembly in the inner sleeve 39;

preferably, as shown in fig. 2, a plurality of welding holes 301 are provided in the wall of the inner sleeve 39, the positions of the welding holes 301 correspond to the positions of the outer edges of the turbine blades 31, and the turbine blades 31 are welded and connected by the welding holes 301.

In the preferred embodiment shown in FIG. 1, inner sleeve 39 is divided axially into a helical section 37 and a straight section 38;

the turbine blades 31 are arranged in the spiral section 37, and the spiral section 37 is positioned at one end of the inner sleeve 39 close to the upstream; the straight line section 38 is positioned at one end close to the downstream, and the turbine blade 31 is not arranged in the straight line section 38;

turbine blades 31 are near the upstream end of the turbine body 30.

S5, machining the inclined hole 35 in the turbine body 30;

the axis of the inclined hole 35 and the axis of the turbine body 30 form an included angle a;

the axis of the inclined hole 35 intersects the axis of the turbine body 30 at a position near the upstream end of the turbine body 30;

during machining, the turbine body 30 is supported to be consistent with the axis of the machining tool of the inclined hole 35 through the tool, and then drilling and boring machining are carried out, so that machining of the inclined hole 35 can be achieved.

S6, fixing the inner sleeve 39 in the inclined hole 35; in this embodiment, the inner sleeve 39 is preferably secured within the angled bore 35 by an interference fit. Or a plurality of pin holes which are evenly distributed along the circumference are processed between the inner sleeve 39 and the turbine body 30, and then the locking pins are driven in for fixation.

The machining of the eccentric turbine 3 is completed through the above steps.

The above-described embodiments are merely preferred embodiments of the present invention, and should not be construed as limiting the present invention, and features in the embodiments and examples in the present application may be arbitrarily combined with each other without conflict. The protection scope of the present invention is defined by the claims, and includes equivalents of technical features of the claims. I.e., equivalent alterations and modifications within the scope hereof, are also intended to be within the scope of the invention.