CN117072066A - Oscillating nipple assembly and turbine type hydraulic oscillator - Google Patents

Abstract

The application relates to an oscillating nipple assembly and a turbine type hydraulic oscillator, which belong to the technical field of petroleum drilling and comprise a nipple shell, wherein the nipple shell is provided with a valve cavity and first flow passages respectively communicated with two ends of the valve cavity; the valve core is slidably connected in the valve cavity, a second flow passage communicated with the first flow passage is arranged in the valve core, the cross section of the second flow passage is smaller than that of the first flow passage, and an upper cavity and a lower cavity which are axially arranged at intervals are formed between the valve core and the short section shell. According to the Venturi effect, the fluid pressure in the first flow channel is larger than that of the second flow channel, the first flow channel is communicated with the upper cavity, the second flow channel is communicated with the lower cavity and the first flow channel is communicated with the lower cavity, and the second flow channel is communicated with the upper cavity, so that the two states alternately appear, the valve core is driven to reciprocate periodically along the axial direction by the fluid pressure difference formed between the upper cavity and the lower cavity, axial compensation oscillation is formed, the axial oscillation impact force of the hydraulic oscillator is improved, and drilling efficiency of a drilling tool is guaranteed.

Description

Oscillating nipple assembly and turbine type hydraulic oscillator

Technical Field

The application relates to the technical field of petroleum drilling, in particular to an oscillating nipple assembly and a turbine type hydraulic oscillator.

Background

At present, petroleum drilling has been developed into directional wells and horizontal wells, the drilling tool is clung to the lower side well wall due to the high inclination of the directional wells and the horizontal wells, so that the drilling tool is excessively rubbed in the drilling process, the drilling is seriously affected, and even the drilling pressure can not be transmitted to the drill bit, and the drilling can not be performed. The screw type hydraulic oscillator is adopted in the current drilling engineering to effectively transfer the drilling pressure and improve the efficiency of conventional drilling so as to solve the problems of drill sticking, incapability of transferring the drilling pressure and the like in the drilling process.

In the related art, the hydraulic oscillator improves the effectiveness of bit pressure transmission in the drilling process and reduces friction between the bottom drilling tool and the borehole through vibration generated by the hydraulic oscillator, namely the hydraulic oscillator overcomes the friction between the drill rod and the borehole wall through oscillation force to improve the drilling efficiency of the drilling tool, but the turbine hydraulic oscillator can only convert pressure difference generated by periodical change of axial fluid flow area between the movable valve and the static valve into vibration, the component force of vibration force generated in practice in the axial direction of the oscillator is small, the situation that the axial oscillation impact force of the oscillator is insufficient is difficult to ensure the drilling efficiency of the drilling tool.

Therefore, it is necessary to provide an oscillation nipple assembly to improve the axial oscillation impact force of the turbine hydraulic oscillator and ensure the drilling efficiency of the drilling tool.

Disclosure of Invention

The embodiment of the application provides an oscillation nipple assembly and a turbine type hydraulic oscillator, which are used for solving the problem that the axial oscillation impact force of the hydraulic oscillator in the related art is insufficient and the drilling efficiency of a drilling tool is difficult to ensure.

A first aspect of an embodiment of the present application provides an oscillating nipple assembly, comprising:

the nipple shell is provided with a valve cavity and first flow passages respectively communicated with two ends of the valve cavity;

the valve core is slidably connected in the valve cavity, a second flow passage communicated with the first flow passage is arranged in the valve core, the cross section of the second flow passage is smaller than that of the first flow passage, and an upper cavity and a lower cavity which are axially arranged at intervals are formed between the valve core and the short section shell;

the first flow channel and the second flow channel are alternately communicated with the upper chamber and the lower chamber, so that a fluid pressure difference formed between the upper chamber and the lower chamber drives the valve core to periodically reciprocate along the axial direction of the short section shell.

In some embodiments, the upper chamber and the lower chamber are both annular and have rectangular cross sections, and the rectangular cavities are located on the short section shell and the valve core on two opposite sides in the axial direction.

In some embodiments, the valve core is provided with a third flow passage communicated with the first flow passage, a fourth flow passage communicated with the second flow passage, a fifth flow passage communicated with the first flow passage and a sixth flow passage communicated with the second flow passage;

the third flow channel is used for communicating or cutting off the first flow channel and the upper chamber, the fourth flow channel is used for communicating or cutting off the second flow channel and the lower chamber, the fifth flow channel is used for communicating or cutting off the first flow channel and the lower chamber, and the sixth flow channel is used for communicating or cutting off the second flow channel and the upper chamber.

In some embodiments, the nipple housing is provided with a seventh runner, an eighth runner, a ninth runner and a tenth runner which are communicated with the upper chamber, the lower chamber;

the seventh flow channel is used for communicating or cutting off the third flow channel and the upper chamber, the eighth flow channel is used for communicating or cutting off the fourth flow channel and the lower chamber, the ninth flow channel is used for communicating or cutting off the fifth flow channel and the lower chamber, and the sixth flow channel is used for communicating or cutting off the sixth flow channel and the upper chamber.

In some embodiments, the valve core is provided with a guide key for limiting the valve core to rotate in the valve cavity, and the short section shell is provided with a guide groove for the guide key to slide along the short section shell axially.

In some embodiments, the nipple housing includes a static valve seat and a lower connector threaded onto the static valve seat, the static valve seat and the lower connector together enclosing the valve cavity housing the valve cartridge.

A second aspect of an embodiment of the present application provides a turbine type hydraulic oscillator, including:

the shell is of a tubular structure, and one end of the shell is connected with the oscillating nipple assembly;

the power assembly comprises a middle through shaft positioned in the shell and a turbine group for driving the middle through shaft to rotate, and the turbine group comprises a stator fixed in the shell and a rotor fixedly sleeved on the middle through shaft;

the pulse assembly comprises a movable valve communicated with the middle through shaft and a static valve plate communicated with the static valve seat, wherein eccentric holes are formed in the opposite ends of the movable valve and the static valve plate, and the movable valve rotates relative to the static valve plate to periodically change the flow area of the eccentric holes.

In some embodiments, the device further comprises a pressure holding prevention assembly positioned in the middle through shaft;

the anti-holding pressure assembly comprises an overflow sleeve communicated with the middle through shaft and in sliding connection, and an elastic body for driving the overflow sleeve to move towards the movable valve, a containing cavity is formed between the overflow sleeve and the movable valve, and fluid in the containing cavity drives the overflow sleeve to be far away from the movable valve to a set position so as to discharge liquid in the middle through shaft.

In some embodiments, one end of the middle through shaft, which is close to the static valve seat, is communicated with a flow dividing sleeve, the overflow sleeve is positioned in the flow dividing sleeve, one end of the overflow sleeve extends into the middle through shaft, and the movable valve is in threaded connection with the flow dividing sleeve so as to prevent the overflow sleeve and the elastic body from being separated from the flow dividing sleeve;

the flow dividing sleeve is provided with a flow dividing hole, the static valve seat is provided with a flow converging hole communicated with the flow dividing hole and the first flow passage, one end, close to the movable valve, of the flow dividing sleeve is provided with an overflow hole penetrating through the flow dividing sleeve in the radial direction, and the overflow hole is used for communicating or cutting off the middle through shaft and the flow dividing hole.

In some embodiments, an annular step is arranged in the shell, an annular flange is arranged on the outer surface of the middle through shaft, a bearing is connected between the middle through shaft and the shell, and the bearing is abutted between the annular step and the annular flange so that the movable valve and the static valve plate are in clearance fit.

The technical scheme provided by the application has the beneficial effects that:

the embodiment of the application provides an oscillating nipple assembly and a turbine type hydraulic oscillator, wherein a nipple shell is provided with a valve cavity and first flow passages respectively communicated with two ends of the valve cavity; the valve core is connected in the valve cavity in a sliding way, a second flow passage communicated with the first flow passage is arranged in the valve core, the cross section of the second flow passage is smaller than that of the first flow passage, and an upper cavity and a lower cavity which are axially arranged at intervals are formed between the valve core and the short section shell; the first flow channel and the second flow channel are alternately communicated with the upper chamber and the lower chamber, so that the fluid pressure difference formed between the upper chamber and the lower chamber drives the valve core to periodically reciprocate along the axial direction of the short section shell.

Therefore, according to the Venturi effect, the fluid pressure in the first flow channel is larger than the fluid pressure of the second flow channel, the first flow channel is communicated with the upper cavity, the second flow channel is communicated with the lower cavity and the first flow channel is communicated with the lower cavity, and the second flow channel is communicated with the upper cavity, and the two states alternately appear, so that the valve core is driven to periodically reciprocate along the axial direction by the fluid pressure difference formed between the upper cavity and the lower cavity, axial compensation oscillation is formed, the axial oscillation impact force of the hydraulic oscillator is improved, and the drilling efficiency of the drilling tool is ensured.

Drawings

In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings required for the description of the embodiments will be briefly described below, and it is apparent that the drawings in the following description are only some embodiments of the present application, and other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.

FIG. 1 is a schematic diagram of an embodiment of the present application;

FIG. 2 is a schematic illustration of an embodiment of the present application when the valve spool is in the upper position of the valve cavity;

FIG. 3 is a schematic illustration of an embodiment of the present application with a spool in a lower position in a valve cavity;

FIG. 4 is a schematic illustration of an embodiment of the present application when the overflow and tap holes are truncated;

FIG. 5 is a schematic illustration of an embodiment of the present application when the overflow aperture and the diverter aperture are in communication;

FIG. 6 is a schematic diagram of the connection of the diverter sleeve and the overflow sleeve according to an embodiment of the present application.

In the drawings, the list of components represented by the various numbers is as follows:

1. an upper joint; 2. a housing; 3. pressing the cap; 4. a movable sleeve is arranged; 5. a static sleeve is arranged on the upper part; 6. a rotor; 7. a stator; 8. an intermediate spacer; 9. a middle through shaft; 10. a serial bearing; 11. a lower movable sleeve; 12. a lower static sleeve; 13. a shunt sleeve; 14. an elastomer; 15. an overflow sleeve; 16. a valve; 17. a static valve plate; 18. a static valve seat; 19. a valve core; 20. a lower joint;

21. an upper chamber; 22. a lower chamber; 23. a first flow passage; 24. a second flow passage; d01, a fourth runner; d02, an eighth runner; d03, tenth runner; d04, a sixth runner; g01, a seventh runner; g02, a third runner; g03, ninth runner; g04, fifth runner; g05, confluence hole; f01, a shunt hole; y01, overflow aperture.

Detailed Description

For the purpose of making the objects, technical solutions and advantages of the embodiments of the present application more apparent, the technical solutions of the embodiments of the present application will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present application, and it is apparent that the described embodiments are some embodiments of the present application, but not all embodiments of the present application. All other embodiments, which can be made by those skilled in the art based on the embodiments of the application without making any inventive effort, are intended to be within the scope of the application.

The embodiment of the application provides an oscillation nipple assembly and a turbine type hydraulic oscillator, which can solve the problem that the axial oscillation impact force of the hydraulic oscillator in the related art is insufficient and the drilling efficiency of a drilling tool is difficult to ensure.

Referring to fig. 1 to 3, a first aspect of an embodiment of the present application provides an oscillating nipple assembly comprising:

the nipple shell is provided with a valve cavity and first flow passages 23 respectively communicated with two ends of the valve cavity;

the valve core 19 is slidably connected in the valve cavity, a second flow passage 24 communicated with the first flow passage 23 is arranged in the valve core 19, the cross section of the second flow passage 24 is smaller than that of the first flow passage 23, and an upper chamber 21 and a lower chamber 22 which are axially arranged at intervals are formed between the valve core 19 and the short section shell;

the first flow channel 23 and the second flow channel 24 alternately communicate with the upper chamber 21 and the lower chamber 22, so that a fluid pressure difference formed between the upper chamber 21 and the lower chamber 22 drives the spool 19 to periodically reciprocate along the axial direction of the sub housing.

According to the oscillating nipple assembly, the flow cross section of the first flow channel 23 at the two ends of the second flow channel 24 is larger than that of the second flow channel 24, and according to the Venturi effect, the fluid pressure in the first flow channel 23 is larger than that of the second flow channel 24, so that the first flow channel 23 is communicated with the upper cavity 21, the second flow channel 24 is communicated with the lower cavity 22 and the first flow channel 23 is communicated with the lower cavity 22, and the second flow channel 24 is communicated with the upper cavity 21, and the two states alternately appear, so that the fluid pressure difference formed between the upper cavity 21 and the lower cavity 22 drives the valve 16 core to reciprocate periodically along the axial direction to form axial compensating oscillation, thereby improving the axial oscillating impact force of the hydraulic oscillator and ensuring the drilling efficiency of a drilling tool.

Illustratively, the second flow passage 24 is a venturi passage, and when the drilling fluid passes through the second flow passage 24 on the valve core 19, the drilling fluid forms a low-pressure liquid area in the second flow passage 24, and a high-pressure liquid area is formed in the first flow passage 23 with two ends of the second flow passage 24 communicated;

when the valve core 19 is in the upper position, the upper chamber 21 is communicated with the first flow channel 23 to form a liquid high-pressure area, the lower chamber 22 is communicated with the second flow channel 24 to form a liquid low-pressure area, and the liquid pressure in the upper chamber 21 is greater than the liquid pressure in the lower chamber 22, so that the valve core 19 moves downwards;

when the valve core 19 is in the lower position, the upper chamber 21 is communicated with the second flow passage 24 to form a liquid low-pressure area, the lower chamber 22 is communicated with the first flow passage 23 to form a liquid high-pressure area, the liquid pressure in the lower chamber 22 is larger than the liquid pressure in the upper chamber 21, so that the valve core 19 moves upwards, and reciprocates in this way, so that axial compensation oscillation is formed to improve the axial oscillation impact force of the hydraulic oscillator, and the drilling efficiency of the drilling tool is ensured.

In some alternative embodiments: referring to fig. 1 to 3, the embodiment of the present application provides an oscillation nipple assembly, in which an upper chamber 21 and a lower chamber 22 are both annular and have a rectangular cross section, and the rectangular chambers are located on axially opposite sides of the nipple housing and the spool 19, respectively.

The upper chamber 21 and the lower chamber 22 of the embodiment of the application are both enclosed by the short section shell and the valve core 19, and the two end surfaces of the valve core 19 are the component surfaces of the upper chamber 21 and the lower chamber 22 respectively.

Illustratively, the two ends of the valve core 19 are integrally formed with bosses, the second flow channel 24 of the valve core 19 penetrates through the bosses on two sides, two ends of the cavity on the short section shell are provided with counter bores for partially accommodating the bosses, the bosses are in sliding connection with the counter bores, and the depth of the counter bores is smaller than the axial height of the bosses, so that the two ends of the valve core 19 and the short section shell respectively enclose an upper cavity 21 and a lower cavity 22 surrounding the bosses, and when a pressure difference exists between liquid in the upper cavity 21 and the lower cavity 22, the liquid can directly act on the end face of the valve core 19 to push the valve core 19 to move.

In some alternative embodiments: referring to fig. 1 to 3, an embodiment of the present application provides an oscillation nipple assembly, in which a valve element 19 is provided with a third flow channel G02 communicating with a first flow channel 23, a fourth flow channel D01 communicating with a second flow channel 24, a fifth flow channel G04 communicating with the first flow channel 23, and a sixth flow channel D04 communicating with the second flow channel 24;

the third flow path G02 is used to communicate or intercept the first flow path 23 and the upper chamber 21, the fourth flow path D01 is used to communicate or intercept the second flow path 24 and the lower chamber 22, the fifth flow path G04 is used to communicate or intercept the first flow path 23 and the lower chamber 22, and the sixth flow path D04 is used to communicate or intercept the second flow path 24 and the upper chamber 21.

The short section shell is provided with a seventh flow passage G01, an eighth flow passage D02 which are communicated with the upper cavity 21, a ninth flow passage G03 and a tenth flow passage D03 which are communicated with the lower cavity 22;

the seventh flow passage G01 is used to communicate or intercept the third flow passage G02 and the upper chamber 21, the eighth flow passage D02 is used to communicate or intercept the fourth flow passage D01 and the lower chamber 22, the ninth flow passage G03 is used to communicate or intercept the fifth flow passage G04 and the lower chamber 22, and the sixth flow passage D04 is used to communicate or intercept the sixth flow passage D04 and the upper chamber 21.

The multiple flow passages in the embodiment of the present application cooperate with each other, so that two states of the first flow passage 23 communicating with the upper chamber 21 and the second flow passage 24 communicating with the lower chamber 22 and the first flow passage 23 communicating with the lower chamber 22 and the second flow passage 24 communicating with the upper chamber 21 can alternately occur.

Specifically, the second flow passage 24 is a venturi passage, when the drilling fluid passes through the second flow passage 24 on the valve core 19, the drilling fluid forms a low-pressure liquid area in the second flow passage 24, and a high-pressure liquid area is formed in the first flow passage 23 with two ends of the second flow passage 24 communicated;

when the valve core 19 is in the upper position, the upper chamber 21 is communicated with the first flow passage 23 through the third flow passage G02 and the seventh flow passage G01 to form a liquid high-pressure area, the lower chamber 22 is communicated with the second flow passage 24 through the fourth flow passage D01 and the eighth flow passage D02 to form a liquid low-pressure area, and the liquid pressure in the upper chamber 21 is larger than the liquid pressure in the lower chamber 22, so that the valve core 19 moves downwards;

when the valve core 19 is in the lower position, the upper chamber 21 is communicated with the first flow passage 23 through the sixth flow passage D04 and the tenth flow passage D03 to form a liquid low-pressure area, the lower chamber 22 is communicated with the first flow passage 23 through the fifth flow passage G04 and the ninth flow passage G03 to form a liquid high-pressure area, the liquid pressure in the lower chamber 22 is larger than that in the upper chamber 21, so that the valve core 19 moves upwards, reciprocates in this way, axial compensation oscillation is formed to improve the axial oscillation impact force of the hydraulic oscillator, and drilling efficiency of a drilling tool is ensured.

Illustratively, the third flow channel G02 and the fifth flow channel G04 are each in an L-shaped structure and extend to the end face and the outer circumferential face of the spool 19; the fourth flow channel D01 and the sixth flow channel D04 are both arranged along the radial direction of the valve core 19 and extend to the outer circular surface of the valve core 19, specifically, the first flow channel 23 is a venturi tube, and the fourth flow channel D01 and the sixth flow channel D04 are both communicated with the throat section of the venturi tube; the seventh flow channel G01, the eighth flow channel D02, the ninth flow channel G03 and the tenth flow channel D03 are all in a U-shaped structure, and both ends face the outer circular surface of the valve core 19.

In some alternative embodiments: referring to fig. 1 to 3, an embodiment of the present application provides an oscillation nipple assembly, in which a valve core 19 of the oscillation nipple assembly is provided with a guide key for restricting rotation of the valve core 19 in a valve cavity, and a nipple housing is provided with a guide groove for sliding the guide key along the axial direction of the nipple housing.

The valve core 19 of the embodiment of the application is of a hollow cylindrical structure, so as to avoid dislocation of the flow passages on the valve core 19 and the valve cavity caused by rotation of the valve core 19 in the valve cavity, and therefore, a guide key is arranged on the valve core 19, and meanwhile, a guide groove which accommodates the guide key and is in sliding connection with the guide key is arranged on the short section shell, so that the valve core 19 can only axially slide in the valve cavity.

In some alternative embodiments: referring to fig. 1 to 3, an embodiment of the present application provides an oscillating nipple assembly, the nipple housing of which comprises a static valve seat 18 and a lower connector 20 screwed onto the static valve seat 18, the static valve seat 18 and the lower connector 20 together enclosing a valve cavity for accommodating a valve core 19.

The short joint shell of the embodiment of the application comprises the static valve seat 18 and the lower joint 20 which is connected with the static valve seat 18 in a threaded manner, the static valve seat 18 and the lower joint 20 jointly enclose a valve cavity for accommodating the valve core 19, and the valve core 19 can be taken out and replaced by disassembling the static valve seat 18 and the lower joint 20.

Referring to fig. 1 to 6, a second aspect of an embodiment of the present application provides a turbine type hydraulic oscillator, comprising:

the shell 2 is of a tubular structure, and one end of the shell 2 is connected with the oscillation nipple assembly of any one embodiment;

the power assembly comprises a middle through shaft 9 positioned in the shell 2 and a turbine group for driving the middle through shaft 9 to rotate, wherein the turbine group comprises a stator 7 fixed in the shell 2 and a rotor 6 fixedly sleeved on the middle through shaft 9;

the pulse assembly comprises a movable valve 16 communicated with the middle through shaft 9 and a static valve plate 17 communicated with a static valve seat 18, wherein eccentric holes are formed in the opposite ends of the movable valve 16 and the static valve plate 17, the movable valve 16 rotates relative to the static valve plate 17 to periodically change the flow area of the eccentric holes, the static valve plate 17 is in threaded connection with the static valve seat 18, and a lower connector 20 is in threaded connection with the shell 2.

The shell 2 of the turbine type hydraulic oscillator is provided with the power assembly and the pulse assembly, the rotor 6 of the power assembly drives the movable valve 16 of the pulse assembly to rotate relative to the static valve plate 17 so as to periodically change the flow area of the eccentric hole, so that the liquid pressure flowing through the movable valve 16 and the static valve plate 17 changes along with the change of the flow area, pressure pulses are generated, the pressure pulses are transmitted to the drill string to drive the drill string to vibrate, and the pressure supporting condition in the drilling process is avoided.

The high-pressure drilling fluid enters from the inlet of the casing 2 and flows into the turbine group formed by the stator 7 and the rotor 6, the turbine group drives the middle through shaft 9 to rotate, the middle through shaft 9 drives the movable valve 16 with the eccentric hole at the end part to rotate, and the movable valve 16 rotates relative to the static valve plate 17 with the eccentric hole due to the dislocation arrangement of the eccentric hole on the movable valve 16 and the eccentric hole on the static valve plate 17, so that the flow area between the movable valve 16 and the static valve plate 17 changes from large to small and periodically, the pressure of the drilling fluid changes along with the change of the flow area, and pressure pulses are generated to be transmitted to the drill string to drive the drill string to vibrate, and the pressure supporting condition in the drilling process is avoided.

In some alternative embodiments: referring to fig. 4 to 6, the embodiment of the present application provides a turbine hydraulic oscillator, which further includes a pressure holding prevention assembly located in the middle through shaft 9; the anti-holding pressure assembly comprises an overflow sleeve 15 which is communicated with the middle through shaft 9 and is in sliding connection with the middle through shaft 9, and an elastic body 14 which drives the overflow sleeve 15 to move towards the movable valve 16, a containing cavity is formed between the overflow sleeve 15 and the movable valve 16, and fluid in the containing cavity drives the overflow sleeve 15 to be far away from the movable valve 16 to a set position so as to discharge liquid in the middle through shaft 9.

The middle through shaft 9 is communicated with a split sleeve 13 at one end close to a static valve seat 18, an overflow sleeve 15 is positioned in the split sleeve 13, one end of the overflow sleeve extends into the middle through shaft 9, and a movable valve 16 is in threaded connection with the split sleeve 13 so as to prevent the overflow sleeve 15 and an elastic body 14 from being separated from the split sleeve 13;

the flow dividing sleeve 13 is provided with a flow dividing hole F01, the static valve seat 18 is provided with a converging hole G05 for communicating the flow dividing hole F01 with the first flow passage 23, one end of the overflow sleeve 15, which is close to the movable valve 16, is provided with an overflow hole Y01 which radially penetrates through the overflow sleeve 15, and the overflow hole Y01 is used for communicating or cutting off the middle through shaft 9 and the flow dividing hole F01.

The anti-holding pressure assembly provided by the embodiment of the application can prevent the problem that the drilling is affected due to the increase of the pressure in the oscillator when the turbine group is braked, and has the advantages of simple structure, safety, reliability and easiness in implementation.

Illustratively, the elastic body 14 is a spring, the overflow sleeve 15 is of a T-shaped structure, and the spring is sleeved on the overflow sleeve 15 and is propped between the overflow sleeve 15 and the middle through shaft 9;

during normal operation, the spring on the overflow sleeve 15 has a certain compression amount, the elastic force of the spring keeps the overflow sleeve 15 and the movable valve 16 in contact, the overflow hole Y01 on the overflow sleeve 15 and the flow distribution hole F01 on the flow distribution sleeve 13 are staggered, and the drilling fluid passes through the holes of the driven valve 16 and the static valve;

when the pressure in the oscillator is too high, the pressure value exceeds a certain range to influence normal drilling, the drilling fluid in the containing cavity formed between the overflow sleeve 15 and the movable valve 16 pushes the overflow sleeve 15 to compress the spring away from the movable valve 16 due to the too high pressure, when the overflow hole Y01 on the overflow sleeve 15 is communicated with the flow distribution hole F01 on the flow distribution sleeve 13, the drilling fluid is partially distributed from the holes on the overflow sleeve 15 and the flow distribution sleeve 13, the pressure in the oscillator is reduced, and when the pressure value is reduced to the range which can be born by the drilling working condition, the elasticity of the spring pushes the overflow sleeve 15 back to the initial position, so that the overflow hole Y01 on the overflow sleeve 15 and the flow distribution hole F01 on the flow distribution sleeve 13 are staggered mutually.

In some alternative embodiments: referring to fig. 1, an embodiment of the present application provides a turbine hydraulic oscillator, in which an annular step is provided in a housing 2 of the turbine hydraulic oscillator, an annular flange is provided on the outer surface of a central through shaft 9, a bearing is connected between the central through shaft 9 and the housing 2, and the bearing abuts between the annular step and the annular flange to enable a movable valve 16 and a static valve plate 17 to be in clearance fit.

According to the embodiment of the application, the axial gap is arranged between the movable valve 16 and the static valve plate 17, so that the consumption of the end surface friction force between the movable valve 16 and the static valve plate 17 on the power performance of the turbine is reduced, specifically, the lower end surface of the bearing is abutted against the annular step of the shell 2 by connecting the bearing between the middle through shaft 9 and the shell 2, the annular flange on the middle through shaft 9 is abutted against the upper end surface of the bearing to prevent the movable valve 16 from contacting the static valve plate 17 downwards, preferably, the gap between the movable valve 16 and the static valve plate 17 is smaller than 1mm, and the pressure release caused by the gap does not influence the performance of the oscillator.

The bearing comprises a serial bearing 10 and a sliding bearing which are positioned between the middle through shaft 9 and the shell 2, the sliding bearing comprises a lower static sleeve 12 and a lower movable sleeve 11, meanwhile, an upper static sleeve 5 and an upper movable sleeve 4 which are positioned above the stator 7 and the rotor 6 are arranged between the middle through shaft 9 and the shell 2, and an intermediate spacer sleeve 8 is arranged between the stator 7 and the outer ring of the serial bearing 10;

an upper joint 1 is arranged at one end of the shell 2 far away from the lower joint 20, and the upper joint 1 is in threaded connection with the shell 2 so as to tightly press and position an upper static sleeve 5, a stator 7, an intermediate spacer 8, an outer ring of a serial bearing 10 and a lower static sleeve 12 on the end surface of an annular step;

the split sleeve 13 is in threaded connection with the middle through shaft 9 so as to tightly press and position the lower movable sleeve 11 and the inner ring of the serial bearing 10 on the end surface of the annular flange, so that the middle through shaft 9 is axially positioned, the axial movement of the middle through shaft 9 is avoided, and the axial clearance formed by the movable valve 16 and the static valve plate 17 is ensured to be unchanged;

the end of the middle through shaft 9, which is close to the upper joint 1, is provided with a pressing cap 3 for closing an opening of the pressing cap 3, and the pressing cap 3 is in threaded connection with the middle through shaft 9 so as to tightly press and position the upper movable sleeve 4 and the rotor 6 on the end surface of the annular flange, so that the rotor 6 and the upper movable sleeve 4 are fixed on the middle through shaft 9, and the rotor 6 drives the middle through shaft 9 to rotate when fluid passes through;

the upper static sleeve 5 is provided with a plurality of overflow holes which axially penetrate through the upper static sleeve 5, the middle through shaft 9 is provided with a plurality of inclined holes which radially penetrate through the annular flange, so that high-pressure drilling fluid can be concentrated to pass through the gap between the stator 7 and the rotor 6 from the overflow holes, the efficiency of converting pressure into power is improved, the rotating speed of the rotor 6 is ensured, and meanwhile, the drilling fluid can be converged into the middle through shaft 9 from the plurality of inclined holes.

In the description of the present application, it should be noted that the azimuth or positional relationship indicated by the terms "upper", "lower", etc. are based on the azimuth or positional relationship shown in the drawings, and are merely for convenience of describing the present application and simplifying the description, and are not indicative or implying that the apparatus or element in question must have a specific azimuth, be constructed and operated in a specific azimuth, and thus should not be construed as limiting the present application. Unless specifically stated or limited otherwise, the terms "mounted," "connected," and "coupled" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present application can be understood by those of ordinary skill in the art according to the specific circumstances.

It should be noted that in the present application, relational terms such as "first" and "second" and the like are used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Moreover, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the phrase "comprising one … …" does not exclude the presence of other like elements in a process, method, article, or apparatus that comprises the element.

The foregoing is only a specific embodiment of the application to enable those skilled in the art to understand or practice the application. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the application. Thus, the present application is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims (10)

1. An oscillating nipple assembly, comprising:

the nipple shell is provided with a valve cavity and first flow passages (23) which are respectively communicated with two ends of the valve cavity;

the valve core (19), the valve core (19) is slidably connected in the valve cavity, a second flow passage (24) communicated with the first flow passage (23) is arranged in the valve core (19), the cross section of the second flow passage (24) is smaller than that of the first flow passage (23), and an upper cavity (21) and a lower cavity (22) which are axially arranged at intervals are formed between the valve core (19) and the short section shell;

the first flow channel (23) and the second flow channel (24) are alternately communicated with the upper chamber (21) and the lower chamber (22) so that a fluid pressure difference formed between the upper chamber (21) and the lower chamber (22) drives the valve core (19) to periodically reciprocate along the axial direction of the short joint shell.

2. The oscillating nipple assembly of claim 1, wherein:

the upper chamber (21) and the lower chamber (22) are both annular, the annular section is a rectangular cavity, and two opposite surfaces of the rectangular cavity in the axial direction are respectively positioned on the short section shell and the valve core (19).

3. The oscillating nipple assembly of claim 1, wherein:

the valve core (19) is provided with a third flow passage (G02) communicated with the first flow passage (23), a fourth flow passage (D01) communicated with the second flow passage (24), a fifth flow passage (G04) communicated with the first flow passage (23) and a sixth flow passage (D04) communicated with the second flow passage (24);

the third flow channel (G02) is used for communicating or cutting off the first flow channel (23) and the upper chamber (21), the fourth flow channel (D01) is used for communicating or cutting off the second flow channel (24) and the lower chamber (22), the fifth flow channel (G04) is used for communicating or cutting off the first flow channel (23) and the lower chamber (22), and the sixth flow channel (D04) is used for communicating or cutting off the second flow channel (24) and the upper chamber (21).

4. The oscillating nipple assembly of claim 3, wherein:

a seventh runner (G01), an eighth runner (D02) and a ninth runner (G03) and a tenth runner (D03) which are communicated with the upper chamber (21), the lower chamber (22) and the upper chamber are arranged on the short joint shell;

the seventh flow channel (G01) is used for communicating or cutting off the third flow channel (G02) and the upper chamber (21), the eighth flow channel (D02) is used for communicating or cutting off the fourth flow channel (D01) and the lower chamber (22), the ninth flow channel (G03) is used for communicating or cutting off the fifth flow channel (G04) and the lower chamber (22), and the sixth flow channel (D04) is used for communicating or cutting off the sixth flow channel (D04) and the upper chamber (21).

5. The oscillating nipple assembly of claim 1, wherein:

the valve core (19) is provided with a guide key for limiting the valve core (19) to rotate in the valve cavity, and the short section shell is provided with a guide groove for the guide key to slide along the axial direction of the short section shell.

6. The oscillating nipple assembly of claim 1, wherein:

the nipple shell comprises a static valve seat (18) and a lower connector (20) which is connected to the static valve seat (18) in a threaded mode, and the static valve seat (18) and the lower connector (20) jointly enclose a valve cavity for accommodating a valve core (19).

7. A turbine type hydraulic oscillator, comprising:

a casing (2), wherein the casing (2) is of a tubular structure, and one end of the casing (2) is connected with the oscillation nipple assembly according to any one of claims 1 to 6;

the power assembly comprises a middle through shaft (9) positioned in the shell (2) and a turbine group for driving the middle through shaft (9) to rotate, wherein the turbine group comprises a stator (7) fixed in the shell (2) and a rotor (6) fixedly sleeved on the middle through shaft (9);

the pulse assembly comprises a movable valve (16) communicated with the middle through shaft (9) and a static valve plate (17) communicated with the static valve seat (18), wherein eccentric holes are formed in the opposite ends of the movable valve (16) and the static valve plate (17), and the movable valve (16) rotates relative to the static valve plate (17) to periodically change the overflow area of the eccentric holes.

8. The turbine type hydraulic oscillator as set forth in claim 7, wherein:

the anti-holding-down pressure assembly is positioned in the middle through shaft (9);

the anti-holding pressure assembly comprises an overflow sleeve (15) which is communicated with the middle through shaft (9) and is in sliding connection, and an elastic body (14) which drives the overflow sleeve (15) to move towards the movable valve (16), a containing cavity is formed between the overflow sleeve (15) and the movable valve (16), and fluid in the containing cavity drives the overflow sleeve (15) to be far away from the movable valve (16) to a set position so as to discharge liquid in the middle through shaft (9).

9. The turbine type hydraulic oscillator as set forth in claim 8, wherein:

one end of the middle through shaft (9) close to the static valve seat (18) is communicated with a split sleeve (13), the overflow sleeve (15) is positioned in the split sleeve (13) and one end of the overflow sleeve extends into the middle through shaft (9), and the movable valve (16) is in threaded connection with the split sleeve (13) so as to prevent the overflow sleeve (15) and the elastic body (14) from separating from the split sleeve (13);

be provided with on reposition of redundant personnel cover (13) and divide flow aperture (F01), be equipped with on static disk seat (18) and link up converging hole (G05) of flow aperture (F01) and first runner (23), the one end that overflow cover (15) is close to movable valve (16) is equipped with overflow hole (Y01) that radially runs through overflow cover (15), overflow hole (Y01) are arranged in the intercommunication or cut off through axle (9) and reposition of redundant personnel hole (F01).

10. The turbine-type hydraulic oscillator as set forth in claim 9, wherein:

an annular step is arranged in the shell (2), an annular flange is arranged on the outer surface of the middle through shaft (9), a bearing is connected between the middle through shaft (9) and the shell (2), and the bearing is abutted between the annular step and the annular flange so that the movable valve (16) and the static valve plate (17) are in clearance fit.