CN111395959B - A Dynamic Pointing Rotary Steering Drilling Tool Test Bench Dynamic System - Google Patents
A Dynamic Pointing Rotary Steering Drilling Tool Test Bench Dynamic System Download PDFInfo
- Publication number
- CN111395959B CN111395959B CN202010237582.0A CN202010237582A CN111395959B CN 111395959 B CN111395959 B CN 111395959B CN 202010237582 A CN202010237582 A CN 202010237582A CN 111395959 B CN111395959 B CN 111395959B
- Authority
- CN
- China
- Prior art keywords
- valve
- oil
- way
- oil inlet
- filter
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Classifications
-
- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B7/00—Special methods or apparatus for drilling
- E21B7/04—Directional drilling
-
- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B47/00—Survey of boreholes or wells
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/041—Removal or measurement of solid or liquid contamination, e.g. filtering
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/042—Controlling the temperature of the fluid
- F15B21/0423—Cooling
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B9/00—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member
- F15B9/02—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type
- F15B9/04—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by varying the output of a pump with variable capacity
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B9/00—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member
- F15B9/02—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type
- F15B9/08—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor
- F15B9/09—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor with electrical control means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20576—Systems with pumps with multiple pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/405—Flow control characterised by the type of flow control means or valve
- F15B2211/40523—Flow control characterised by the type of flow control means or valve with flow dividers
- F15B2211/40538—Flow control characterised by the type of flow control means or valve with flow dividers using volumetric pumps or motors
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Life Sciences & Earth Sciences (AREA)
- Geology (AREA)
- Mining & Mineral Resources (AREA)
- Analytical Chemistry (AREA)
- Chemical & Material Sciences (AREA)
- Environmental & Geological Engineering (AREA)
- General Life Sciences & Earth Sciences (AREA)
- Geochemistry & Mineralogy (AREA)
- Fluid-Pressure Circuits (AREA)
- Geophysics (AREA)
Abstract
一种动态指向式旋转导向钻井工具试验台动力系统，包括模拟旋转液压系统和模拟加载液压系统，模拟旋转液压系统给导向钻井工具提供主轴驱动扭矩，模拟加载液压系统模拟钻头在破碎岩石时受到的反向扭矩以及轴向载荷；模拟旋转液压系统通过二位三通比例阀接收经过放大器放大的偏差电信号控制斜盘式变量泵的斜盘倾角，保证主轴驱动液压马达稳定无级调速；模拟加载液压系统执行元件为反扭矩加载缸和轴向加载缸，分别配备压力变送器，通过三位四通比例阀和比例压力阀，动态调节加载力；本发明为动态指向式旋转导向钻井工具试验台提供动力，结构简单、精度高、安全可靠。
A dynamic pointing type rotary steerable drilling tool test bench power system, including a simulated rotary hydraulic system and a simulated loading hydraulic system, the simulated rotary hydraulic system provides a main shaft driving torque to the steerable drilling tool, and the simulated loading hydraulic system simulates the impact of the drill bit when breaking rocks. Reverse torque and axial load; simulate the rotary hydraulic system to receive the deviation electric signal amplified by the amplifier through the two-position three-way proportional valve to control the swash plate inclination angle of the swash plate variable pump to ensure the stable and stepless speed regulation of the main shaft drive hydraulic motor; The executive elements of the loading hydraulic system are the anti-torque loading cylinder and the axial loading cylinder, which are respectively equipped with pressure transmitters, and the loading force is dynamically adjusted through the three-position four-way proportional valve and the proportional pressure valve; the present invention is a dynamic directional rotary steerable drilling tool. The test bench provides power, with simple structure, high precision, safety and reliability.
Description
Technical Field
The invention relates to the technical field of dynamic directional rotary steering drilling tool tests, in particular to a dynamic system of a test bed of a dynamic directional rotary steering drilling tool, which provides driving force for a main shaft of the test bed and provides reaction torque and axial load for a tested dynamic directional rotary steering drilling tool.
Background
The rotary steering drilling technology has many advantages in the exploitation of horizontal wells, extended reach wells and highly deviated wells, so the development of rotary steering drilling tools is very important. In order to test the performance of the dynamic directional rotary steerable drilling tool, the development of a test bench is very necessary.
Domestic rotary steerable drilling tool test beds are of many types, but test beds for dynamic directional rotary steerable drilling tool performance testing are under development. The existing test bed generally adopts two different power simulation drilling tool working conditions of electric power and hydraulic pressure, and has the advantages of complex structure, poor compatibility and high manufacturing and maintenance cost. The electric drive is used as the main shaft driving force of the test bed, the speed is regulated through the frequency conversion of the motor or the gear box, although the speed regulation purpose can be achieved, the frequency conversion speed regulation is easy to generate heat under the long-term high-pressure working condition, and the gear box speed regulating mechanism increases the size of the test bed.
Therefore, research and development of a test bed which is small in size, simple in structure, high in control precision and low in cost and takes hydraulic pressure as single power becomes a research and development team of a dynamic pointing type rotary steering drilling tool, and technical personnel in the field need to solve the problems urgently.
Disclosure of Invention
In order to solve the defects of the prior art, the invention aims to provide a dynamic directional rotary steering drilling tool test bed power system, which adopts hydraulic elements, has small volume and simple structure, and improves the control precision of the test bed hydraulic system because a sensor element and a hydraulic proportional element are matched with each other.
In order to achieve the purpose, the technical scheme of the invention is as follows:
a dynamic directional rotary steering drilling tool test bed power system comprises a simulated rotary hydraulic system and a simulated loading hydraulic system;
the simulation rotary hydraulic system provides a main shaft driving force and comprises an oil tank 1, a first common filter 2.1, a second common filter 2.2, a swash plate type variable displacement pump 3, an adjusting cylinder 4, a two-position three-way proportional valve 5, a first one-way valve 6.1, a second one-way valve 6.2, a first precision filter 7.1, a main shaft driving motor 8, a first back pressure valve 9.1, an air cooler 10, a pressure gauge 11, a safety valve 12, a first two-position two-way valve 13.1 and a rotating speed sensor 15; an oil inlet of the first common filter 2.1 is connected with the oil tank 1, and an oil outlet is connected with an oil inlet of the inclined disc type variable pump 3; an oil outlet of the swash plate type variable pump 3 is connected with an oil inlet of a first one-way valve 6.1, a port P of a two-position three-way proportional valve 5 and a left cavity of an adjusting cylinder 4; an A port of the two-position three-way proportional valve 5 is connected with a right cavity of the adjusting cylinder 4, an O port of the two-position three-way proportional valve 5 is connected with the oil tank 1, and a hydraulic cylinder rod of the adjusting cylinder 4 is mechanically connected with a swash plate of the swash plate type variable pump 3; an oil outlet of the first one-way valve 6.1 is connected with an oil inlet of the first precision filter 7.1; an oil outlet of the first precision filter 7.1 is respectively connected with an oil inlet of the pressure gauge 11, an oil inlet of the safety valve 12, an oil outlet of the second one-way valve 6.2 and an oil inlet of the main shaft driving motor 8; an oil inlet of the second one-way valve 6.2 is connected with the oil tank 1; the rotating speed of the main shaft driving motor 8 is monitored by a rotating speed sensor 15, and an oil outlet of the main shaft driving motor 8 is connected with an oil inlet of a first backpressure valve 9.1; an oil outlet of the first back pressure valve 9.1 and an oil outlet of the safety valve 12 are simultaneously connected with an oil inlet of the air cooler 10; the port P of the first two-position two-way valve 13.1 is connected with a remote control oil path of the safety valve 12, and the port A of the first two-position two-way valve 13.1 is connected with an oil inlet of the air cooler 10; the oil outlet of the air cooler 10 is connected with the oil inlet of the second common filter 2.2; the oil outlet of the second common filter 2.2 is connected with the oil tank 1.
The simulated loading hydraulic system simulates reverse torque and axial force load of a drill bit when rock is crushed and comprises an oil tank 1, a third common oil filter 2.3, a fourth common oil filter 2.4, a third one-way valve 6.3, a fourth one-way valve 6.4, a fifth one-way valve 6.5, a second precision filter 7.2, a second back pressure valve 9.2, a second two-position two-way valve 13.2, a fixed displacement pump 16, a three-position four-way proportional valve 17, a flow dividing and collecting valve 18, a first pressure transmitter 19.1, a second pressure transmitter 19.2, a reverse torque loading cylinder 20.1, a reverse torque loading cylinder 20.2, a water cooler 21, a proportional pressure valve 22, a throttle valve 23, an axial loading cylinder 24 and an overflow valve 25; an oil inlet of the third ordinary oil filter 2.3 is connected with the oil tank 1, and an oil outlet of the third ordinary oil filter 2.3 is connected with an oil inlet of the constant delivery pump 16; an oil outlet of the fixed displacement pump 16 is connected with an oil inlet of a third one-way valve 6.3; an oil outlet of the third one-way valve 6.3 is connected with an oil inlet of the second precision filter 7.2, an oil inlet of the overflow valve 25 and an oil outlet of the fifth one-way valve 6.5; the oil outlet of the overflow valve 25 is connected with the oil tank 1; the oil outlet of the second precision filter 7.2 is connected with the P port of the three-position four-way proportional valve 17 and the oil inlet of the proportional pressure valve 22; the port A of the three-position four-way proportional valve 17 is connected with an oil inlet of the flow distributing and collecting valve 18; the oil outlet of the flow distributing and collecting valve 18 is respectively connected with a left cavity of a first counter-torque loading cylinder 20.1 and a right cavity of a second counter-torque loading cylinder 20.2; the port B of the three-position four-way proportional valve 17 is connected with a right cavity of a first counter torque loading cylinder 20.1 and a left cavity of a second counter torque loading cylinder 20.2; the working pressure of the first counter-torque loading cylinder 20.1 and the second counter-torque loading cylinder 20.2 is controlled by a first pressure transmitter 19.1; an O port of the three-position four-way proportional valve 17 is connected with an oil inlet of the water cooler 21; the oil outlet of the water cooler 21 is connected with the oil inlet of a fourth common oil filter 2.4; an oil outlet of the fourth common oil filter 2.4 is connected with an oil inlet of a fifth one-way valve 6.5 and an oil inlet of a second backpressure valve 9.2; the oil outlet of the second backpressure valve 9.2 is connected with the oil tank 1; an oil outlet of the proportional pressure valve 22 is connected with an oil inlet of the fourth one-way valve 6.4; an oil outlet of the fourth one-way valve 6.4 is connected with one end of the throttle valve 23 and a P port of the second two-position two-way valve 13.2; the other end of the throttle valve 23 is connected with an axial loading cylinder 24, and the working pressure of the axial loading cylinder 24 is controlled by a second pressure transmitter 19.2; and the port A of the second two-position two-way valve 13.2 is connected with an oil inlet of the water cooler 21.
The first precision filter 7.1 and the second precision filter 7.2 are provided with a bypass one-way valve and a filtering impurity saturation alarm device.
A liquid level meter 26 is arranged in the oil tank 1.
The invention has the beneficial effects that:
1) the stepless speed regulation function of the test bed can be better realized by adopting the swash plate type variable pump to drive the main shaft driving motor, the hydraulic system does not need to be stopped, the two-position three-way proportional valve can be directly controlled to drive the regulating cylinder, the inclination angle of the swash plate type variable pump is changed, the rotating speed of the main shaft driving motor is monitored by the rotating speed sensor in real time, a rotating speed signal is fed back to the two-position three-way proportional valve through the amplifier, and the rotating speed of the main shaft of the test bed is dynamically regulated.
2) The analog loading hydraulic system is characterized in that hydraulic oil provided by the fixed displacement pump is respectively supplied to the counter torque loading cylinder and the axial loading cylinder, one part of the hydraulic oil discharged by the counter torque loading cylinder and the axial loading cylinder flows back to the oil tank, and the other part of the hydraulic oil flows to the outlet of the fixed displacement pump for oil supplement, so that the system is compact in structure.
3) A flow distributing and collecting valve is adopted to supply oil to the two anti-torque loading cylinders simultaneously, so that the two cylinders can synchronously run and apply pressure to the friction disc, and anti-torque required by experiments is provided.
4) The pressure electric signal collected by the first pressure transmitter is compared with the input expected electric signal, the obtained difference value is fed back to the three-position four-way proportional valve through the amplifier, the size of the valve core opening of the three-position four-way proportional valve is changed, the flow entering the two reactive torque loading cylinders is adjusted, the stable reactive torque loading is ensured, and the redundant hydraulic oil returns to the oil tank through the overflow valve.
5) The pressure electric signal acquired by the second pressure transmitter is compared with the input expected electric signal, the obtained difference value is fed back to the proportional pressure valve through the amplifier, the size of the valve core opening of the proportional pressure valve is changed, the flow entering the axial loading cylinder is adjusted, the axial loading load is ensured to be stable, and redundant hydraulic oil returns to the oil tank.
Drawings
FIG. 1 is a schematic diagram of a hydraulic system used in the present invention.
In the figure: an oil tank 1; a first common oil filter 2.1; a second general filter 2.2; a swash plate type variable displacement pump 3; an adjusting cylinder 4; a two-position three-way proportional valve 5; a first one-way valve 6.1; a second one-way valve 6.2; a third one-way valve 6.3; a fourth one-way valve 6.4; a fifth one-way valve 6.5; a first fine filter 7.1; a second precision filter 7.2; a spindle drive motor 8; a first back pressure valve 9.1; a second backpressure valve 9.2; an air cooler 10; a pressure gauge 11; a safety valve 12; a first two-position two-way valve 13.1; a second two-position two-way valve 13.2; a coupling 14; a rotation speed sensor 15; a constant flow pump 16; a three-position four-way proportional valve 17; a flow distributing and collecting valve 18; a first pressure transmitter 19.1; a second pressure transmitter 19.2; reaction torque loading a cylinder 20.1; a reaction torque loading two-cylinder 20.2; a water cooler 21; a proportional pressure valve 22; a throttle valve 23; an axial loading cylinder 24; an overflow valve 25; a level gauge 26.
FIG. 2 is a schematic diagram of the simulated reaction torque principle of the present invention.
In the figure: reaction torque loading a cylinder 20.1; a reaction torque loading two-cylinder 20.2; a slide lever 27; a friction block 28; a friction disk 29; the shaft 30 is loaded with a counter torque.
FIG. 3 is a schematic diagram of electro-hydraulic proportional control employed in the present invention.
In the figure: u shaperi(i ═ 1,2,3) for input of desired voltage signal, Uci(i ═ 1,2,3) for monitoring the feedback voltage signal, Δ Ui(i ═ 1,2,3) is an offset electrical signal, Δ Ui＝Uri-Uci。
Detailed Description
The invention will be further described with reference to fig. 1,2 and 3, and the embodiments described below by way of the drawings are exemplary and are intended to be illustrative of the invention only and should not be construed as limiting the invention.
As shown in FIG. 1, a dynamic directional rotary steerable drilling tool test bed power system comprises a simulated rotary hydraulic system and a simulated loading hydraulic system;
the simulation rotary hydraulic system provides a main shaft driving force and comprises an oil tank 1, a first common filter 2.1, a second common filter 2.2, a swash plate type variable displacement pump 3, an adjusting cylinder 4, a two-position three-way proportional valve 5, a first one-way valve 6.1, a second one-way valve 6.2, a first precision filter 7.1, a main shaft driving motor 8, a first back pressure valve 9.1, an air cooler 10, a pressure gauge 11, a safety valve 12, a first two-position two-way valve 13.1 and a rotating speed sensor 15; an oil inlet of the first common filter 2.1 is connected with the oil tank 1, and an oil outlet is connected with an oil inlet of the inclined disc type variable pump 3; an oil outlet of the swash plate type variable pump 3 is connected with an oil inlet of a first one-way valve 6.1, a port P of a two-position three-way proportional valve 5 and a left cavity of an adjusting cylinder 4; an A port of the two-position three-way proportional valve 5 is connected with a right cavity of the adjusting cylinder 4, an O port of the two-position three-way proportional valve 5 is connected with the oil tank 1, and a hydraulic cylinder rod of the adjusting cylinder 4 is mechanically connected with a swash plate of the swash plate type variable pump 3; an oil outlet of the first one-way valve 6.1 is connected with an oil inlet of the first precision filter 7.1; an oil outlet of the first precision filter 7.1 is respectively connected with an oil inlet of the pressure gauge 11, an oil inlet of the safety valve 12, an oil outlet of the second one-way valve 6.2 and an oil inlet of the main shaft driving motor 8; an oil inlet of the second one-way valve 6.2 is connected with the oil tank 1; the rotating speed of the main shaft driving motor 8 is monitored by a rotating speed sensor 15, and an oil outlet of the main shaft driving motor 8 is connected with an oil inlet of a first backpressure valve 9.1; an oil outlet of the first back pressure valve 9.1 and an oil outlet of the safety valve 12 are simultaneously connected with an oil inlet of the air cooler 10; the port P of the first two-position two-way valve 13.1 is connected with a remote control oil path of the safety valve 12, and the port A of the first two-position two-way valve 13.1 is connected with an oil inlet of the air cooler 10; the oil outlet of the air cooler 10 is connected with the oil inlet of the second common filter 2.2; the oil outlet of the second common filter 2.2 is connected with the oil tank 1.
The simulated loading hydraulic system simulates reverse torque and axial force load of a drill bit when rock is crushed and comprises an oil tank 1, a third common oil filter 2.3, a fourth common oil filter 2.4, a third one-way valve 6.3, a fourth one-way valve 6.4, a fifth one-way valve 6.5, a second precision filter 7.2, a second back pressure valve 9.2, a second two-position two-way valve 13.2, a fixed displacement pump 16, a three-position four-way proportional valve 17, a flow dividing and collecting valve 18, a first pressure transmitter 19.1, a second pressure transmitter 19.2, a reverse torque loading cylinder 20.1, a reverse torque loading cylinder 20.2, a water cooler 21, a proportional pressure valve 22, a throttle valve 23, an axial loading cylinder 24 and an overflow valve 25; an oil inlet of the third ordinary oil filter 2.3 is connected with the oil tank 1, and an oil outlet of the third ordinary oil filter 2.3 is connected with an oil inlet of the constant delivery pump 16; an oil outlet of the fixed displacement pump 16 is connected with an oil inlet of a third one-way valve 6.3; an oil outlet of the third one-way valve 6.3 is connected with an oil inlet of the second precision filter 7.2, an oil inlet of the overflow valve 25 and an oil outlet of the fifth one-way valve 6.5; the oil outlet of the overflow valve 25 is connected with the oil tank 1; the oil outlet of the second precision filter 7.2 is connected with the P port of the three-position four-way proportional valve 17 and the oil inlet of the proportional pressure valve 22; the port A of the three-position four-way proportional valve 17 is connected with an oil inlet of the flow distributing and collecting valve 18; the oil outlet of the flow distributing and collecting valve 18 is respectively connected with a left cavity of a first counter-torque loading cylinder 20.1 and a right cavity of a second counter-torque loading cylinder 20.2; the port B of the three-position four-way proportional valve 17 is connected with a right cavity of a first counter torque loading cylinder 20.1 and a left cavity of a second counter torque loading cylinder 20.2; the working pressure of the first counter-torque loading cylinder 20.1 and the second counter-torque loading cylinder 20.2 is controlled by a first pressure transmitter 19.1; an O port of the three-position four-way proportional valve 17 is connected with an oil inlet of the water cooler 21; the oil outlet of the water cooler 21 is connected with the oil inlet of a fourth common oil filter 2.4; an oil outlet of the fourth common oil filter 2.4 is connected with an oil inlet of a fifth one-way valve 6.5 and an oil inlet of a second backpressure valve 9.2; the oil outlet of the second backpressure valve 9.2 is connected with the oil tank 1; an oil outlet of the proportional pressure valve 22 is connected with an oil inlet of the fourth one-way valve 6.4; an oil outlet of the fourth one-way valve 6.4 is connected with one end of the throttle valve 23 and a P port of the second two-position two-way valve 13.2; the other end of the throttle valve 23 is connected with an axial loading cylinder 24, and the working pressure of the axial loading cylinder 24 is controlled by a second pressure transmitter 19.2; and the port A of the second two-position two-way valve 13.2 is connected with an oil inlet of the water cooler 21.
The first precision filter 7.1 and the second precision filter 7.2 are provided with a bypass one-way valve and a filtering impurity saturation alarm device.
A liquid level meter 26 is arranged in the oil tank 1, and the liquid level of the oil tank 1 is measured through the liquid level meter 26.
The working principle of the invention is as follows:
the working principle of the analog rotary hydraulic system is as follows:
as shown in fig. 1 and 3, the analog rotary hydraulic system provides a main shaft driving force: the main shaft driving motor 8 is controlled to rotate by adopting the inclined disc type variable displacement pump 3, the main shaft driving motor 8 is connected with a main shaft of a test bed of the dynamic directional type rotary steering drilling tool through a coupler 14, the main shaft of the test bed is provided with a rotating speed sensor 15, and the rotating speed n acquired by the rotating speed sensor is converted into an electric signal Uc1，Uc1And expected electrical signal Ur1Comparing the obtained deviation electric signal delta U1The working position and the valve port size of the two-position three-way proportional valve 5 are controlled through amplification of an amplifier, hydraulic oil enters a right cavity of the adjusting cylinder 4 from an oil inlet P port of the two-position three-way proportional valve 5 through the working port A or directly enters a left cavity of the adjusting cylinder, the adjusting cylinder 4 is pushed to change the inclined angle of the inclined disc type variable pump 3, the oil outlet flow of the inclined disc type variable pump 3 and the oil inlet flow of the main shaft driving motor 8 are changed, and the purpose of stepless and stable speed regulation of the main shaft is achieved.
When the hydraulic system works normally, the first backpressure valve 9.1 reduces the impact when the rotating speed of the main shaft driving motor 8 changes, and the system runs more stably. When the main shaft driving motor 8 brakes, resistance is generated, and braking efficiency is improved.
When the hydraulic system works normally, the safety valve 12 plays a role in safety pressure limiting protection. When the main shaft driving motor 8 is unloaded and braked, the safety valve 12 is in a full open state, and high-pressure oil directly returns to the oil tank through the first two-position two-way valve 13.1.
Because the main shaft of the invention belongs to the operation with large torque and low rotating speed, the main shaft driving motor 8 can continue to rotate due to inertia during braking, and cavitation can be generated because the oil inlet of the main shaft driving motor 8 stops supplying oil. In order to solve the cavitation phenomenon, the oil inlet of the main shaft driving motor 8 is connected with an oil tank through a second one-way valve 6.2 which is reversely arranged, and in the braking process, hydraulic oil can be sucked from the oil tank as long as the pressure of the oil inlet of the main shaft driving motor 8 is lower than the atmospheric pressure, so that the cavitation phenomenon is prevented.
The hydraulic system loop is provided with an air cooler 10 for cooling hydraulic oil. The first fine filter 7.1 is installed at the outlet of the swash plate type variable pump 3, and a safety valve is connected in parallel to prevent the swash plate type variable pump 3 from being overloaded and protect other hydraulic elements except the swash plate type variable pump 3.
The working principle of the analog loading hydraulic system is as follows:
the simulation loading hydraulic system simulates reverse torque and axial force load which a drill bit receives when the drill bit is used for crushing rocks, hydraulic oil provided by the fixed displacement pump 16 is respectively supplied to the reverse torque loading cylinders 20.1 and 20.2 and the axial loading cylinder 24, part of the hydraulic oil discharged by the reverse torque loading cylinders and the axial loading cylinders flows back to the oil tank, and part of the hydraulic oil flows to the outlet of the fixed displacement pump for oil supplement, so that the system is compact in structure.
As shown in fig. 1,2 and 3, the analog loading hydraulic system is divided into a reaction torque loading hydraulic system and an axial loading hydraulic system, and simulates reaction torque loading hydraulic pressure: when the three-position four-way proportional valve 17 is in the left working position, hydraulic oil enters the flow dividing and collecting valve 18 through the oil inlet P and the working oil port a of the three-position four-way proportional valve 17, at this time, the flow dividing valve 18 plays an equivalent flow dividing role, the counter torque loading one cylinder 20.1 and the counter torque loading two cylinder 20.2 simultaneously push the friction block 28 to be close to the friction disc 29, and the mechanical structure of the friction block can slide along the sliding rod 27. The pressure P exerted by the friction block 28 on the friction disc 29 is monitored by the first pressure transmitter 19.12And converted into a voltage signal Uc2，Uc2And expected electrical signal Ur2Comparing the obtained deviation electric signal delta U2The pressure of the reactive torque loading cylinder is ensured to reach a desired value by feeding back to the three-position four-way proportional valve 17 through the amplifier, the size of a valve port of the three-position four-way proportional valve 17 is adjusted, stable reactive torque loading is realized, and redundant hydraulic oil flows back to the oil tank through the overflow valve 25. When the three-position four-way proportional valve 17 is in the right working position, hydraulic oil enters the first counter-torque loading cylinder 20.1 and the second counter-torque loading cylinder 20.2 through the oil inlet P and the working oil port B of the three-position four-way proportional valve 17, separation of the friction block 28 and the friction disc 29 is achieved, pressure applied to the friction disc 29 by the friction block 28 is reduced, loading of counter torque is reduced, the process of adjusting the three-position four-way proportional valve 17 is similar to that in the left working position, and the flow distributing and collecting valve 18 plays a role at the moment.
The simulation axial loading hydraulic pressure: the hydraulic oil enters the axial loading cylinder 24 through the proportional pressure valve 22, and the pressure P exerted on the dynamic directional rotary guiding well drilling tool by the axial loading cylinder 24 is monitored by the second pressure transmitter 19.23And converted into a voltage signal Uc3，Uc3And expected electrical signal Ur3Comparing the obtained deviation electric signal delta U3The axial loading pressure is fed back to the proportional pressure valve 22 through the amplifier, the second two-position two-way valve 13.2 is in the left working position at the moment, and the redundant hydraulic oil flows back to the oil tank. When unloading is needed, the second two-position two-way valve 13.2 is in the right working position, and hydraulic oil flows back to the oil tank through the second two-position two-way valve 13.2 due to the elastic force of the spring of the axial loading cylinder 24 and the elastic restoring force of the guide drilling tool.
The fourth non return valve 6.4 prevents the returning hydraulic oil from impacting the proportional pressure valve 22 and the throttle 23 ensures a smooth axial loading speed.
The loading system is prone to heating and is cooled by the water cooler 21 against the hydraulic oil returning to the tank. The second backpressure valve 9.2 ensures that the oil return of the analog torque loading hydraulic system is stable, and the impact is reduced. The fifth one-way valve 6.5 can supplement the pressure of the analog loading hydraulic system instantly, and the energy consumption is reduced. The second precision filter 7.2 prevents impurities in the hydraulic oil from entering the precision element three-position four-way proportional valve 17 and the proportional pressure valve 22, the second precision filter 7.2 is installed at the outlet of the fixed displacement pump 16, and the fixed displacement pump 16 is prevented from being overloaded by the safety valve connected in parallel.
The level gauge 26 monitors the page height to avoid the situation that the liquid level is too low and the swash plate type variable displacement pump 3 and the fixed displacement pump 16 are sucked empty. The second common filter 2.2 and the fourth common filter 2.4 of the oil return circuit filter impurities in the hydraulic circuit, and the cleanness of hydraulic oil is guaranteed.
The construction, features and effects of the invention are explained in detail in the embodiments described above with reference to the drawings, which are only preferred embodiments of the invention. Various modifications and alterations may occur to those skilled in the art without departing from the spirit and scope of the invention, and such modifications and alterations should be accorded the broadest interpretation so as to encompass all such modifications and alterations.
Claims (3)
1. A dynamic directional rotary steering drilling tool test bed power system is characterized by comprising a simulated rotary hydraulic system and a simulated loading hydraulic system;
the simulation rotary hydraulic system provides a main shaft driving force and comprises an oil tank (1), a first common filter (2.1), a second common filter (2.2), a swash plate type variable pump (3), an adjusting cylinder (4), a two-position three-way proportional valve (5), a first one-way valve (6.1), a second one-way valve (6.2), a first precision filter (7.1), a main shaft driving motor (8), a first back pressure valve (9.1), an air cooler (10), a pressure gauge (11), a safety valve (12), a first two-position two-way valve (13.1) and a rotating speed sensor (15); an oil inlet of the first common filter (2.1) is connected with the oil tank (1), and an oil outlet of the first common filter is connected with an oil inlet of the inclined disc type variable pump (3); an oil outlet of the swash plate type variable pump (3) is connected with an oil inlet of a first one-way valve (6.1), a P port of a two-position three-way proportional valve (5) and a left cavity of an adjusting cylinder (4); an A port of the two-position three-way proportional valve (5) is connected with a right cavity of the adjusting cylinder (4), an O port of the two-position three-way proportional valve (5) is connected with the oil tank (1), and a hydraulic cylinder rod of the adjusting cylinder (4) is mechanically connected with a swash plate of the swash plate type variable pump (3); an oil outlet of the first one-way valve (6.1) is connected with an oil inlet of the first precision filter (7.1); an oil outlet of the first precision filter (7.1) is respectively connected with an oil inlet of the pressure gauge (11) and the safety valve (12), an oil outlet of the second one-way valve (6.2) and an oil inlet of the main shaft driving motor (8); an oil inlet of the second one-way valve (6.2) is connected with the oil tank (1); the rotating speed of the main shaft driving motor (8) is monitored by a rotating speed sensor (15), and an oil outlet of the main shaft driving motor (8) is connected with an oil inlet of a first back pressure valve (9.1); an oil outlet of the first back pressure valve (9.1) and an oil outlet of the safety valve (12) are simultaneously connected with an oil inlet of the air cooler (10); the P port of the first two-position two-way valve (13.1) is connected with a remote control oil way of the safety valve (12), and the A port of the first two-position two-way valve (13.1) is connected with an oil inlet of the air cooler (10); the oil outlet of the air cooler (10) is connected with the oil inlet of the second common filter (2.2); the oil outlet of the second common filter (2.2) is connected with the oil tank (1);
the simulated loading hydraulic system simulates reverse torque and axial force load of a drill bit when rock is broken and comprises an oil tank (1), a third common oil filter (2.3), a fourth common oil filter (2.4), a third one-way valve (6.3), a fourth one-way valve (6.4), a fifth one-way valve (6.5), a second precision filter (7.2), a second back pressure valve (9.2), a second two-position two-way valve (13.2), a fixed displacement pump (16), a three-position four-way proportional valve (17), a flow dividing and collecting valve (18), a first pressure transmitter (19.1), a second pressure transmitter (19.2), a reverse torque loading cylinder (20.1), a reverse torque loading cylinder (20.2), a water cooler (21), a proportional pressure valve (22), a throttle valve (23), an axial loading cylinder (24) and an overflow valve (25); an oil inlet of the third common oil filter (2.3) is connected with the oil tank (1), and an oil outlet of the third common oil filter (2.3) is connected with an oil inlet of the constant delivery pump (16); an oil outlet of the fixed displacement pump (16) is connected with an oil inlet of a third one-way valve (6.3); an oil outlet of the third one-way valve (6.3) is connected with an oil inlet of the second precision filter (7.2), an oil inlet of the overflow valve (25) and an oil outlet of the fifth one-way valve (6.5); an oil outlet of the overflow valve (25) is connected with the oil tank (1); an oil outlet of the second precision filter (7.2) is connected with a P port of the three-position four-way proportional valve (17) and an oil inlet of the proportional pressure valve (22); the port A of the three-position four-way proportional valve (17) is connected with an oil inlet of the flow distributing and collecting valve (18); the oil outlet of the flow distributing and collecting valve (18) is respectively connected with the left cavity of the first reactive torque loading cylinder (20.1) and the right cavity of the second reactive torque loading cylinder (20.2); the port B of the three-position four-way proportional valve (17) is connected with a right cavity of a first counter torque loading cylinder (20.1) and a left cavity of a second counter torque loading cylinder (20.2); the working pressure of the first counter-torque loading cylinder (20.1) and the second counter-torque loading cylinder (20.2) is controlled by a first pressure transmitter (19.1); an O port of the three-position four-way proportional valve (17) is connected with an oil inlet of the water cooler (21); the oil outlet of the water cooler (21) is connected with the oil inlet of a fourth common oil filter (2.4); the oil outlet of the fourth common oil filter (2.4) is connected with the oil inlet of a fifth one-way valve (6.5) and the oil inlet of a second backpressure valve (9.2); an oil outlet of the second back pressure valve (9.2) is connected with the oil tank (1); an oil outlet of the proportional pressure valve (22) is connected with an oil inlet of a fourth one-way valve (6.4); an oil outlet of the fourth one-way valve (6.4) is connected with one end of the throttle valve (23) and a P port of the second two-position two-way valve (13.2); the other end of the throttle valve (23) is connected with an axial loading cylinder (24), and the working pressure of the axial loading cylinder (24) is controlled by a second pressure transmitter (19.2); the A port of the second two-position two-way valve (13.2) is connected with the oil inlet of the water cooler (21).
2. A dynamic directional rotary steerable drilling tool test bench power system according to claim 1, characterized in that the first (7.1) and second (7.2) precision filters are provided with a bypass check valve and a filtered impurity saturation alarm.
3. A dynamic directional rotary steerable drilling tool test rig power system as claimed in claim 1, said oil tank (1) having a level gauge (26) disposed therein.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010237582.0A CN111395959B (en) | 2020-03-30 | 2020-03-30 | A Dynamic Pointing Rotary Steering Drilling Tool Test Bench Dynamic System |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010237582.0A CN111395959B (en) | 2020-03-30 | 2020-03-30 | A Dynamic Pointing Rotary Steering Drilling Tool Test Bench Dynamic System |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN111395959A CN111395959A (en) | 2020-07-10 |
| CN111395959B true CN111395959B (en) | 2021-09-07 |
Family
ID=71434811
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010237582.0A Active CN111395959B (en) | 2020-03-30 | 2020-03-30 | A Dynamic Pointing Rotary Steering Drilling Tool Test Bench Dynamic System |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN111395959B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112412337B (en) * | 2020-11-30 | 2022-11-01 | 中国海洋石油集团有限公司 | A sliding steerable drilling tool face angle change experiment system and its use method |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1472443A (en) * | 2002-04-26 | 2004-02-04 | �ֶ������ɷ�����˾ | Valve for actuating bidirectional hydraulic cylinder and use of cylinder tray thereof |
| CN201526546U (en) * | 2009-11-17 | 2010-07-14 | 华东交通大学 | A hydraulic control system for underground explosion-proof hoist using multi-pump combination technology |
| WO2010093691A1 (en) * | 2009-02-11 | 2010-08-19 | M-I L.L.C. | Autochoke system |
| CN102953682A (en) * | 2011-08-31 | 2013-03-06 | 中国石油化工股份有限公司 | Tilting tray plunger type rotary guide well drilling tool |
| CN103135512A (en) * | 2011-12-02 | 2013-06-05 | 中铁隧道集团有限公司 | Shield electro-hydraulic control system comprehensive test platform |
| CN103235605A (en) * | 2013-04-19 | 2013-08-07 | 南京工业大学 | Working condition simulation load loading control system and method for numerical control turntable test bed |
| CN103438036A (en) * | 2013-08-01 | 2013-12-11 | 中冶南方工程技术有限公司 | Three-stage pressure control pump |
| CN107219084A (en) * | 2017-06-06 | 2017-09-29 | 西安石油大学 | Dynamic guiding type rotary steering drilling tool property test platform |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US10597999B2 (en) * | 2016-10-20 | 2020-03-24 | Baker Hughes, A Ge Company, Llc | Downhole component support systems and methods of installation |
-
2020
- 2020-03-30 CN CN202010237582.0A patent/CN111395959B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1472443A (en) * | 2002-04-26 | 2004-02-04 | �ֶ������ɷ�����˾ | Valve for actuating bidirectional hydraulic cylinder and use of cylinder tray thereof |
| WO2010093691A1 (en) * | 2009-02-11 | 2010-08-19 | M-I L.L.C. | Autochoke system |
| CN201526546U (en) * | 2009-11-17 | 2010-07-14 | 华东交通大学 | A hydraulic control system for underground explosion-proof hoist using multi-pump combination technology |
| CN102953682A (en) * | 2011-08-31 | 2013-03-06 | 中国石油化工股份有限公司 | Tilting tray plunger type rotary guide well drilling tool |
| CN103135512A (en) * | 2011-12-02 | 2013-06-05 | 中铁隧道集团有限公司 | Shield electro-hydraulic control system comprehensive test platform |
| CN103235605A (en) * | 2013-04-19 | 2013-08-07 | 南京工业大学 | Working condition simulation load loading control system and method for numerical control turntable test bed |
| CN103438036A (en) * | 2013-08-01 | 2013-12-11 | 中冶南方工程技术有限公司 | Three-stage pressure control pump |
| CN107219084A (en) * | 2017-06-06 | 2017-09-29 | 西安石油大学 | Dynamic guiding type rotary steering drilling tool property test platform |
Also Published As
| Publication number | Publication date |
|---|---|
| CN111395959A (en) | 2020-07-10 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101598232B (en) | Control Valve Electrohydraulic Actuator | |
| CN101692027B (en) | Universal material testing machine for variable rotating speed pump control hydraulic servo loading system | |
| CN112377487A (en) | Hydraulic comprehensive test platform | |
| CN100376886C (en) | Axial piston pump sliding shoe pair lubrication characteristics test device | |
| CN105317785B (en) | Development machine multifunctional hydraulic testing stand | |
| CN111395959B (en) | A Dynamic Pointing Rotary Steering Drilling Tool Test Bench Dynamic System | |
| CN1235032C (en) | Lubricating property testing device for port plate pair of axial plunger pump | |
| CN101737371B (en) | Zero maintaining mechanism of 2D digital servo valve | |
| CN102788056A (en) | Hydraulic control system of electro-hydraulic feedback proportion throttle cartridge valve | |
| CN202789805U (en) | Hydraulic control device of electro-hydraulic feedback proportional throttling cartridge valve | |
| CN109944835A (en) | A kind of hydraulic system and drilling machine of drilling machine | |
| CN205677896U (en) | EHA VPVM drives helm gear | |
| CN207093478U (en) | A kind of hydraulic pressure performs equipment | |
| CN213451126U (en) | Hydraulic comprehensive test platform | |
| CN210499555U (en) | A hydraulic feed type horizontal wheelbase surface grinder | |
| CN106114483A (en) | The braking method combined based on hydraulic pressure and electric mechanical and brakes | |
| CN106593976B (en) | Drilling machine hydraulic wireline winch testing stand | |
| CN109185242A (en) | A kind of large size reel sprinkling irrigation machine fluid pressure drive device | |
| CN201650907U (en) | Zero Position Holding Mechanism of 2D Digital Servo Valve | |
| CN201173221Y (en) | Electrohydraulic servo system power-off protection device | |
| CN107091253A (en) | A kind of hydraulic pressure performs equipment | |
| CN203793644U (en) | Four-redundant combined steering engine with monitoring piston | |
| CN206320093U (en) | A kind of rig hydraulic wireline winch testing stand | |
| CN110397646A (en) | A kind of cylinder control system and control method | |
| CN106438533B (en) | A kind of electric proportional control formula rock drill automatic anti-blocking pricker hydraulic control system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |