CN111188572B - Automatic rapid pressurization control method for rotary drilling rig - Google Patents
Automatic rapid pressurization control method for rotary drilling rig Download PDFInfo
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- CN111188572B CN111188572B CN201911394155.7A CN201911394155A CN111188572B CN 111188572 B CN111188572 B CN 111188572B CN 201911394155 A CN201911394155 A CN 201911394155A CN 111188572 B CN111188572 B CN 111188572B
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- 238000005553 drilling Methods 0.000 title claims abstract description 23
- 238000000034 method Methods 0.000 title claims abstract description 22
- 239000003921 oil Substances 0.000 claims abstract description 191
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 33
- 239000003638 chemical reducing agent Substances 0.000 claims description 3
- 239000010687 lubricating oil Substances 0.000 claims description 3
- 230000008929 regeneration Effects 0.000 claims description 3
- 238000011069 regeneration method Methods 0.000 claims description 3
- 230000008901 benefit Effects 0.000 description 6
- 238000010276 construction Methods 0.000 description 3
- 230000001502 supplementing effect Effects 0.000 description 3
- 238000006073 displacement reaction Methods 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
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- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B3/00—Rotary drilling
- E21B3/02—Surface drives for rotary drilling
- E21B3/025—Surface drives for rotary drilling with a to-and-fro rotation of the tool
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- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B19/00—Handling rods, casings, tubes or the like outside the borehole, e.g. in the derrick; Apparatus for feeding the rods or cables
- E21B19/08—Apparatus for feeding the rods or cables; Apparatus for increasing or decreasing the pressure on the drilling tool; Apparatus for counterbalancing the weight of the rods
- E21B19/086—Apparatus for feeding the rods or cables; Apparatus for increasing or decreasing the pressure on the drilling tool; Apparatus for counterbalancing the weight of the rods with a fluid-actuated cylinder
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- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B4/00—Drives for drilling, used in the borehole
- E21B4/02—Fluid rotary type drives
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- Fluid Mechanics (AREA)
- General Life Sciences & Earth Sciences (AREA)
- Geochemistry & Mineralogy (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
An automatic rapid pressurization control method for a rotary drilling rig comprises the steps that a combination valve is matched with a pressurization oil cylinder to enable the pressurization oil cylinder to rapidly descend, the combination valve comprises a first balance valve, a second balance valve and a hydraulic control one-way valve, and a first interface, a second interface, a third interface, a fourth interface and a fifth interface are arranged on the combination valve; when the pressurizing oil cylinder moves downwards, hydraulic oil is pumped to the rodless cavity, so that the hydraulic oil in the rod cavity is pressed to the fourth port, meanwhile, control oil respectively reaches the external control ports of the first and second balance valves, the opening pressure and the pilot ratio of the first and second balance valves are adjusted, the control oil firstly opens the first balance valve, and the hydraulic oil from the rod cavity reaches the rodless cavity through the first balance valve and the pilot-controlled one-way valve due to the fact that the second balance valve is not opened yet, differential connection is formed, and the rapid descending of the pressurizing oil cylinder is achieved. The invention improves the descending speed of the oil cylinder through hydraulic control, and can automatically recover normal pressure to meet the load requirement when the load is increased.
Description
Technical Field
The invention belongs to the technical field of piling machinery, and particularly relates to an automatic rapid pressurization control method for a rotary drilling rig.
Background
The stroke of the pressurizing oil cylinder of the rotary drilling rig is long, the stroke of the pressurizing oil cylinder of the small rotary drilling rig is about 3.5 meters, and the stroke of the pressurizing oil cylinder of the large rotary drilling rig is about 5 meters. If the long stroke is realized by only reversing the multi-way valve to enable the multi-way valve to move downwards, the time consumption is long; meanwhile, the pressurizing oil cylinder is required to frequently move downwards when a pressurizing locking point is found and the drilling bucket is lowered for dumping in actual construction. When the pressurization goes down, the rodless cavity of the pressurization oil cylinder feeds oil, and the rod cavity returns to the oil tank after overcoming the pressure of the balance valve with a certain pilot ratio. Because the rodless chamber has about twice the cross-sectional area of the rodless chamber, the down-flow velocity is only about half the lift velocity. The overlong downlink time greatly reduces the operating efficiency of the rotary drilling rig, and the comprehensive benefit of a main machine of the rotary drilling rig is reduced for a long time.
Patent document CN201710866759.1 discloses an intelligent control device and an intelligent control method for a rotary drilling rig, the intelligent control device for the rotary drilling rig comprises a pressurization oil cylinder, a power head motor, a controller, an adjusting device and a load measuring device, wherein the controller is respectively connected with the adjusting device and the load measuring device; the controller comprises an adjusting input quantity, the adjusting device is connected to the pressurizing oil cylinder and the power head motor, and the adjusting device controls oil delivery to the pressurizing oil cylinder and the power head motor according to the adjusting input quantity; the load measuring device is used for measuring the load of the pressurizing oil cylinder and the power head motor, and the adjusting device also controls the oil liquid conveyed to the pressurizing oil cylinder and the power head motor according to the load measuring device. The device can improve work efficiency to a certain extent through intelligent control, but its control mode is the electric control's that adopts mode, and not only the structure of device is complicated, has still additionally increased power consumption.
Therefore, a new automatic rapid pressurization control method for the rotary drilling rig is needed.
Disclosure of Invention
The invention aims to provide an automatic and rapid pressurization control method for a rotary drilling rig, and aims to solve the problems that the stroke of a pressurization oil cylinder of the rotary drilling rig is long, and the descending time consumption is long, which are provided by the background technology, so that the operation efficiency of the rotary drilling rig is influenced.
In order to achieve the purpose, the invention provides an automatic rapid pressurization control method of a rotary drilling rig, which comprises the steps that a combination valve is adopted to be matched with a pressurization oil cylinder to enable the pressurization oil cylinder to rapidly descend, the combination valve comprises a first balance valve, a second balance valve and a hydraulic control one-way valve, a first interface, namely an oil inlet and a reverse oil outlet of the combination valve, a second interface, namely a regeneration oil port, a third interface, namely a common external control port of the first balance valve and the second balance valve, a fourth interface, namely an oil outlet and a reverse oil inlet of the combination valve, and a fifth interface, namely an external drain port of the first balance valve are arranged on the combination valve; the first balance valve and the second balance valve comprise a check valve and a back pressure valve which are connected in parallel; the first interface is connected with an oil inlet and a reverse oil outlet of the second balance valve through a pressure pipeline, an oil outlet and a reverse oil inlet of the second balance valve are connected with the oil inlet and the reverse oil outlet of the first balance valve through the pressure pipeline, an oil outlet and a reverse oil inlet of the first balance valve are connected with a fourth interface through the pressure pipeline, and the fourth interface is connected with a rod cavity of the pressurizing oil cylinder through the pressure pipeline; the pressure pipeline between the oil outlet and the reverse oil inlet of the second balance valve and the oil inlet and the reverse oil outlet of the first balance valve is also connected with the inlet of the hydraulic control one-way valve; the outlet of the hydraulic control one-way valve is connected with the second interface through a pressure pipeline; the third interface is respectively connected with the outer control ports of the first balance valve and the second balance valve through control pipelines; a control pipeline is connected with a spring cavity of the hydraulic control one-way valve on a pressure pipeline between the first interface and the oil inlet and the reverse oil outlet of the second balance valve;
when the pressurizing oil cylinder needs to rapidly move downwards, hydraulic oil is conveyed to a first multi-way valve interface through an auxiliary pump and then reaches a rodless cavity of the pressurizing oil cylinder through a pressure pipeline, meanwhile, the hydraulic oil in a rod cavity of the pressurizing oil cylinder is pressed to a fourth interface of the combination valve, meanwhile, control oil communicated with the rodless cavity of the pressurizing oil cylinder respectively reaches a common external control port of the first balance valve and the second balance valve, the first balance valve is opened by the control oil through adjusting the opening pressure and the pilot ratio of the first balance valve and the second balance valve, and the hydraulic oil from the rod cavity of the pressurizing oil cylinder reaches the rodless cavity of the pressurizing oil cylinder through the first balance valve and the hydraulic control one-way valve because the second balance valve is not opened, so that differential connection is formed, and the pressurizing oil cylinder rapidly moves downwards;
when the load pressure is increased or the pressurizing oil cylinder reaches the maximum stroke, the second balance valve is gradually opened along with the increase of the pressure of the rodless cavity of the pressurizing oil cylinder, hydraulic oil coming from the rod cavity of the pressurizing oil cylinder returns to the oil tank after passing through the first interface and the second multi-way valve interface, meanwhile, the hydraulic control one-way valve is rapidly and automatically closed under the action of the reset spring force of the hydraulic control one-way valve, at the moment, the pressure of the rodless cavity also enables the hydraulic control one-way valve to be closed, the differential connection is automatically released because the hydraulic control one-way valve is reliably closed, and the pressurizing oil cylinder outputs larger thrust.
In a specific embodiment, the combination valve further comprises a throttle valve, and the throttle valve is arranged on a control pipeline connected with the external control port of the first balance valve.
In a specific embodiment, the throttling valve is an 1/16PT damping hole, and the hole diameter is 0.3 mm-0.8 mm.
In a specific implementation mode, when the pressurizing oil cylinder needs to go down quickly, the first multi-way valve control interface is communicated with pilot pressure oil, hydraulic oil output by the auxiliary pump passes through the multi-way valve preposed pressure compensator to reach an oil inlet of the multi-way valve, and then is reversed by the multi-way valve to reach the first multi-way valve interface.
In a specific embodiment, the control method further includes: when the oil cylinder needs to be pressurized to move upwards, the second multi-way valve control interface is communicated with pilot pressure oil, hydraulic oil output by the auxiliary pump reaches an oil inlet of the multi-way valve through the pre-pressure compensator of the multi-way valve, and then is reversed by the multi-way valve to reach the second multi-way valve interface; after passing through the second multi-way valve interface, the hydraulic oil reaches the oil inlet and the reverse oil outlet of the second balance valve through the first interface, and simultaneously reaches the spring cavity of the hydraulic control one-way valve through the control pipeline to resist the hydraulic control one-way valve to feed the oil; the hydraulic oil reaches the rod cavity of the pressurizing oil cylinder through the second balance valve and the parallel one-way valve in the first balance valve, and the hydraulic oil in the rodless cavity of the pressurizing oil cylinder returns to the oil tank after passing through the interface of the first multi-way valve.
In a specific embodiment, the pressure set by the first balance valve is less than or equal to 32MPa, and the opening pilot ratio of the first balance valve is 4-6: 1; the set pressure of the second balance valve is less than or equal to 28MPa, and the opening pilot ratio of the second balance valve is 2.5-3.5: 1.
in a specific embodiment, the flow of the hydraulic control one-way valve is 100-200L/min, and the reverse closing pilot ratio is 1.6-2.0: 1.
in a specific embodiment, before the combination valve is adopted, the balance load is determined, including calculating the total mass of the power head, the speed reducer, the motor, the lubricating oil and the piston, calculating the effective acting area of the rod cavity of the pressurizing oil cylinder, and determining that the balance load pressure is within the bearing range of the hydraulic valve by calculating the balance load pressure.
In a specific embodiment, the first balance valve is an external leakage type valve, and an oil drainage pipeline is connected with the fifth interface.
Compared with the prior art, the invention has the following beneficial effects:
aiming at the special conditions that the stroke of a pressurizing oil cylinder of the rotary drilling rig is long, the descending speed is slow and the frequent descending movement is needed, the descending speed of the oil cylinder is improved through hydraulic control under the condition that the original electric control method is not changed, and the working condition that the normal pressure can be instantly and automatically recovered to meet the load requirement when the load is increased can be realized.
The invention can improve the descending action of the oil cylinder by more than one time by changing the hydraulic control, thereby improving the working efficiency; when the load pressure is increased to a certain value, the differential connection can be automatically disconnected to meet the requirement of output power. Because the pressurizing oil cylinder is frequently used in construction, the descending speed of the oil cylinder is improved without additionally consuming any engine power, the requirements of energy conservation and environmental protection are met, the construction efficiency is obviously improved, the labor intensity of workers is reduced, and greater economic benefit is generated.
The low-load rapid pressurization can double the speed, and the working efficiency is greatly improved; the switching is automatically completed at the moment of natural pressurization when the rapid pressurization meets a large load. The same working time and the same fuel cost can create more economic benefits.
In addition to the objects, features and advantages described above, other objects, features and advantages of the present invention are also provided. The present invention will be described in further detail below with reference to the drawings.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this application, illustrate embodiments of the invention and, together with the description, serve to explain the invention and not to limit the invention. In the drawings:
FIG. 1 is a partial hydraulic schematic of a combination valve and pressurization cylinder according to one embodiment of the present invention;
FIG. 2 is a hydraulic schematic of one embodiment of the present invention;
FIG. 3 is a schematic view of a combination valve according to an embodiment of the present invention;
FIG. 4 is a hydraulic schematic diagram of a pressurization mode of a rotary drilling rig.
Wherein, 1, a first balance valve; 2. a throttle valve; 3. a hydraulic control check valve; 4. a second balancing valve; A. a first interface; B. a second interface; C. a third interface; D. a fourth interface; E. a fifth interface; AM1, first multiplex valve interface; BM1, a second multiplex valve interface; aM1, a first multi-way valve control interface; bM1, a second multi-way valve control interface.
Detailed Description
Embodiments of the invention will be described in detail below with reference to the drawings, but the invention can be implemented in many different ways, which are defined and covered by the claims.
Example 1
The invention discloses an automatic rapid pressurization control method for a rotary drilling rig, which comprises the following steps:
determining a balanced load: taking JVR36Z as an example, the total mass of the power head, the speed reducer, the motor, the lubricating oil and the piston is 7.9 tons at most, and the effective acting area of the rod cavity is 3.14x (8)2-5.52)＝106cm2The balance pressure is the ratio of the balance mass to the area equal to 7.5 MPa; considering factors such as friction force of a guide rail and the like, the actual balance pressure is generally lower, and the balance pressure is about 4-6.5 MPa; the tolerance pressure of the conventional hydraulic valve is 35 MPa; the equilibrium pressure is far lower than the tolerance pressure of the conventional hydraulic valve, so that the conventional hydraulic valve has a higher safety factor.
The automatic rapid pressurization control method further comprises the step of replacing an original balance valve with a combination valve, wherein the combination valve is matched with the pressurization oil cylinder to enable the pressurization oil cylinder to rapidly descend, the combination valve comprises a first balance valve 1, a second balance valve 4 and a hydraulic control one-way valve 3, a first interface A, namely an oil inlet and a reverse oil outlet of the combination valve, a second interface B, namely a regeneration oil port, a third interface C, namely a common external control port of the first balance valve and the second balance valve, a fourth interface D, namely an oil outlet and a reverse oil inlet of the combination valve, and a fifth interface E, namely an external drain port of the first balance valve are arranged on the combination valve; the first balance valve 1 and the second balance valve 4 comprise a check valve and a back pressure valve which are connected in parallel; the first interface A is connected with an oil inlet and a reverse oil outlet of the second balance valve 4 through a pressure pipeline, an oil outlet and a reverse oil inlet of the second balance valve 4 are connected with the oil inlet and the reverse oil outlet of the first balance valve 1 through the pressure pipeline, the oil outlet and the reverse oil inlet of the first balance valve 1 are connected with a fourth interface through the pressure pipeline, and the fourth interface is connected with a rod cavity of the pressurizing oil cylinder through the pressure pipeline; the pressure pipeline between the oil outlet and the reverse oil inlet of the second balance valve 4 and the oil inlet and the reverse oil outlet of the first balance valve 1 is also connected with the inlet of the hydraulic control one-way valve 3; the outlet of the hydraulic control one-way valve 3 is connected with the second interface B through a pressure pipeline; the third interface C is respectively connected with the outer control ports of the first balance valve and the second balance valve through control pipelines; a control pipeline is connected with a spring cavity of the hydraulic control one-way valve 3 on a pressure pipeline between the first interface A and the oil inlet and reverse oil outlet of the second balance valve 4; the first balance valve 1 is an external leakage type valve and is connected with an oil drainage pipeline to be connected with a fifth interface E;
when the pressurizing oil cylinder needs to rapidly move downwards, the first multi-way valve control interface aM1 is communicated with pilot pressure oil, the hydraulic oil output by the auxiliary pump reaches an oil inlet of the multi-way valve through the multi-way valve preposed pressure compensator, reaches the first multi-way valve interface AM1 after being reversed through the multi-way valve, reaches the rodless cavity of the pressurizing oil cylinder through a pressure pipeline, meanwhile, the hydraulic oil in the rod cavity of the pressurizing oil cylinder is pressed to the fourth interface D of the combination valve, meanwhile, the control oil communicated with the rodless cavity of the pressurizing oil cylinder respectively reaches the common external control ports of the first balance valve and the second balance valve, the control oil firstly opens the first balance valve 1 through adjusting the opening pressure and the pilot ratio of the first balance valve and the second balance valve, and because the second balance valve 4 is not opened, the hydraulic oil from the rod cavity of the pressurizing oil cylinder reaches the rodless cavity of the pressurizing oil cylinder through the first balance valve 1 and the pilot valve 3, so as to form, the pressurizing oil cylinder can move downwards quickly;
when the load pressure is increased or the pressurizing oil cylinder reaches the maximum stroke, the second balance valve 4 is gradually opened along with the increase of the pressure of the rodless cavity of the pressurizing oil cylinder, hydraulic oil coming from the rod cavity of the pressurizing oil cylinder returns to the oil tank after passing through the first interface and the second multi-way valve interface, meanwhile, the hydraulic control one-way valve is rapidly and automatically closed under the action of the reset spring force of the hydraulic control one-way valve, at the moment, the pressure of the rodless cavity also enables the hydraulic control one-way valve to be closed, the differential connection is automatically released because the hydraulic control one-way valve is reliably closed, and the pressurizing oil cylinder outputs larger thrust.
When the oil cylinder needs to be pressurized to move upwards, the second multi-way valve control interface bM1 is communicated with pilot pressure oil, hydraulic oil output by the auxiliary pump passes through the pre-pressure compensator of the multi-way valve to reach an oil inlet of the multi-way valve, and is reversed by the multi-way valve to reach a second multi-way valve interface BM 1; after passing through the second multi-way valve interface BM1, the hydraulic oil reaches the oil inlet and the reverse oil outlet of the second balance valve 4 through the first interface A and simultaneously reaches the spring cavity of the hydraulic control one-way valve 3 through the control pipeline to resist the oil inlet of the hydraulic control one-way valve 3; the hydraulic oil reaches the rod cavity of the pressurizing oil cylinder through the second balance valve 4 and the parallel one-way valve in the first balance valve 1, and the hydraulic oil in the rodless cavity of the pressurizing oil cylinder passes through the first multi-way valve interface AM1 and then returns to the oil tank through the oil return filter.
When the pressurizing oil cylinder moves downwards, hydraulic oil in a rod cavity of the pressurizing oil cylinder is guided to a rodless cavity through an oil return pipeline to form differential connection, and the theoretical volume of the hydraulic oil required by the downward movement of the pressurizing oil cylinder is the volume of a corresponding piston rod. If the diameters of the piston and the piston rod of the oil cylinder are D and D respectively, the ratio of the differential downlink speed to the normal downlink speed is D2/d2. If D and D are 160mm and 110mm respectively, the differential descending speed is 2.1 times of the original descending speed and is 1.1 times of the lifting speed.
In a specific embodiment, the combination valve further comprises a throttle valve 2, and the throttle valve 2 is arranged on a control pipeline connected with an external control port of the first balance valve 1.
In a specific embodiment, the throttle valve 2 is an 1/16PT orifice with a bore diameter of 0.3mm to 0.8 mm.
Determination of individual parameters
When the auxiliary pump displacement is Q and the engine speed is n, the rod chamber oil supply flow Q becomes nqx (D) when the differential connection is performed2-d2) And d 2. If the auxiliary pump has a displacement of 71ml/red, the diameters of the large and small cavities of the piston of the pressurizing oil cylinder160mm and 110mm respectively, the theoretical oil supplementing flow rate during differential rapid operation is 134L/min, and the oil supplementing flow rate can be positioned at 120L/min by considering the volumetric efficiency and the mechanical efficiency, so that a balance valve and a hydraulic control one-way valve with the through flow rate of about 120L/min can be selected according to the oil supplementing flow rate. The maximum pressure of the first balance valve 1 is set to 32MPa, the opening pilot ratio is 5: 1; the maximum pressure of the second balance valve 4 is set to 28MPa, the opening pilot ratio is 3: 1; the flow of the hydraulic control one-way valve is 160L/min, the reverse closing pilot ratio is 1.8: 1; in order to make the opening smooth.
The pipeline assembly mode of the combination valve can be completely exchanged with the assembly mode of the original balance valve, compared with the original balance valve, an oil drainage pipe is additionally arranged on an external pipeline of the combination valve and leads to an oil tank, and a regenerated oil pipe with the length of about 400mm is additionally arranged between a pressurizing oil cylinder and the combination valve.
The low-load rapid pressurization can double the speed, and the working efficiency is greatly improved; the switching is automatically completed at the moment of natural pressurization when the rapid pressurization meets a large load. The same working time and the same fuel cost can create more economic benefits.
The reason that the pressurizing oil cylinder can realize differential quick descending is that the load required before actual pressurizing drilling of the pressurizing oil cylinder is low, meanwhile, pressure difference is generated between a large cavity and a small cavity on two sides of an oil cylinder piston, and the hydraulic oil pressure of a rod cavity is greater than that of a rodless cavity, so that the hydraulic oil of the rod cavity enters the rodless cavity to regenerate and accelerate. When the pressure required by the pressurized drilling load is increased, the rod cavity offsets the load, the acting force output by the differential mode cannot overcome the required load pressure, and the differential connection must be cancelled.
The combination valve of the present invention is commercially available.
The foregoing is a more detailed description of the invention in connection with specific preferred embodiments and it is not intended that the invention be limited to these specific details. For those skilled in the art to which the invention pertains, several simple deductions and substitutions can be made without departing from the spirit of the invention, and all shall be considered as belonging to the protection scope of the invention.
Claims (9)
1. The automatic rapid pressurization control method of the rotary drilling rig is characterized by comprising the steps that a combination valve is matched with a pressurization oil cylinder to enable the pressurization oil cylinder to rapidly move downwards, the combination valve comprises a first balance valve (1), a second balance valve (4) and a hydraulic control one-way valve (3), a first interface (A), namely an oil inlet and a reverse oil outlet of the combination valve, a second interface (B), namely a regeneration oil port, a third interface (C), namely a common external control port of the first balance valve and the second balance valve, a fourth interface (D), namely an oil outlet and a reverse oil inlet of the combination valve, and a fifth interface (E), namely an external drain port of the first balance valve are arranged on the combination valve; the first balance valve (1) and the second balance valve (4) comprise a check valve and a back pressure valve which are connected in parallel; the first connector (A) is connected with an oil inlet and a reverse oil outlet of the second balance valve (4) through a pressure pipeline, an oil outlet and a reverse oil inlet of the second balance valve (4) are connected with the oil inlet and the reverse oil outlet of the first balance valve (1) through the pressure pipeline, an oil outlet and a reverse oil inlet of the first balance valve (1) are connected with a fourth connector through the pressure pipeline, and the fourth connector is connected with a rod cavity of the pressurizing oil cylinder through the pressure pipeline; an oil outlet and a reverse oil inlet of the second balance valve (4) and a pressure pipeline between an oil inlet and a reverse oil outlet of the first balance valve (1) are also connected with an inlet of the hydraulic control one-way valve (3); an outlet of the hydraulic control one-way valve (3) is connected with the second interface (B) through a pressure pipeline; the third interface (C) is respectively connected with the outer control ports of the first balance valve and the second balance valve through control pipelines; a control pipeline is connected with a spring cavity of the hydraulic control one-way valve (3) on a pressure pipeline between the first interface (A) and the oil inlet and the reverse oil outlet of the second balance valve (4);
when the pressurizing oil cylinder needs to rapidly move downwards, hydraulic oil is conveyed to a first multi-way valve interface (AM1) through an auxiliary pump and then reaches a rodless cavity of the pressurizing oil cylinder through a pressure pipeline, meanwhile, the hydraulic oil in a rod cavity of the pressurizing oil cylinder is pressed to a fourth interface (D) of a combination valve, meanwhile, control oil communicated with the rodless cavity of the pressurizing oil cylinder respectively reaches a common external control port of a first balance valve and a second balance valve, the control oil opens the first balance valve (1) firstly by adjusting the opening pressure and the pilot ratio of the first balance valve and the second balance valve, and the hydraulic oil coming from the rod cavity of the pressurizing oil cylinder reaches the rodless cavity of the pressurizing oil cylinder through the first balance valve (1) and a hydraulic control one-way valve (3) because the second balance valve (4) is not opened, so that differential connection is formed, and the pressurizing oil cylinder rapidly moves downwards;
when the load pressure is increased, the second balance valve (4) is gradually opened along with the increase of the pressure of the rodless cavity of the pressurizing oil cylinder, hydraulic oil from the rod cavity of the pressurizing oil cylinder returns to the oil tank after passing through the first interface (A) and the second multi-way valve interface (BM1), meanwhile, the hydraulic control one-way valve (3) is rapidly and automatically closed under the action of the reset spring force, at the moment, the pressure of the rodless cavity also enables the hydraulic control one-way valve (3) to be closed, the differential connection is automatically released due to the fact that the hydraulic control one-way valve (3) is reliably closed, and the pressurizing oil cylinder outputs larger thrust to meet the load requirement.
2. A control method according to claim 1, characterized in that the combination valve further comprises a throttle valve (2), which throttle valve (2) is arranged in a control line connected to the outer control port of the first counter-balance valve (1).
3. A control method according to claim 2, characterized in that the throttle valve (2) is an 1/16PT orifice with a hole diameter of 0.3-0.8 mm.
4. The control method according to claim 1, characterized in that when the pressurized oil cylinder needs to descend rapidly, the first multi-way valve control interface (aM1) is connected with pilot pressure oil, hydraulic oil output by the auxiliary pump passes through the multi-way valve pre-pressure compensator to reach an oil inlet of the multi-way valve, and then is reversed by the multi-way valve to reach the first multi-way valve interface (AM 1).
5. The control method according to claim 1, characterized by further comprising: when the oil cylinder needs to be pressurized to move upwards, a second multi-way valve control interface (bM1) is communicated with pilot pressure oil, hydraulic oil output by the auxiliary pump reaches an oil inlet of the multi-way valve through the pre-pressure compensator of the multi-way valve, and then is reversed by the multi-way valve to reach a second multi-way valve interface (BM 1); after passing through the second multi-way valve interface (BM1), the hydraulic oil reaches the oil inlet and the reverse oil outlet of the second balance valve (4) through the first interface (A), and simultaneously reaches the spring cavity of the hydraulic control one-way valve (3) through the control pipeline to resist the oil inlet of the hydraulic control one-way valve (3); the hydraulic oil reaches the rod cavity of the pressurizing oil cylinder through the second balance valve (4) and the parallel one-way valve in the first balance valve (1), and the hydraulic oil in the rodless cavity of the pressurizing oil cylinder returns to the oil tank after passing through the first multi-way valve interface (AM 1).
6. A control method according to claim 1, characterized in that the first balancing valve (1) has an opening pilot ratio of 4-6: 1; the opening pilot ratio of the second balance valve (4) is 2.5-3.5: 1.
7. the control method according to claim 1, wherein the flow rate of the pilot-operated check valve is 100-200L/min, and the reverse closing pilot ratio is 1.6-2.0: 1.
8. the control method of claim 1, wherein before the combination valve is used, the balance load is determined, the method comprises the steps of calculating the total mass of the power head, the speed reducer, the motor, the lubricating oil and the piston, calculating the effective acting area of a rod cavity of the pressurizing oil cylinder, and confirming that the balance load pressure is within the bearing range of the hydraulic valve by calculating the balance load pressure.
9. Control method according to claim 1, characterized in that the first counter-balance valve (1) is an external bleed valve, to which a bleed line is connected to a fifth connection (E).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911394155.7A CN111188572B (en) | 2019-12-30 | 2019-12-30 | Automatic rapid pressurization control method for rotary drilling rig |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911394155.7A CN111188572B (en) | 2019-12-30 | 2019-12-30 | Automatic rapid pressurization control method for rotary drilling rig |
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| Publication Number | Publication Date |
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| CN111188572A CN111188572A (en) | 2020-05-22 |
| CN111188572B true CN111188572B (en) | 2021-07-02 |
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| CN201911394155.7A Active CN111188572B (en) | 2019-12-30 | 2019-12-30 | Automatic rapid pressurization control method for rotary drilling rig |
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| CN (1) | CN111188572B (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SU1062388A1 (en) * | 1982-10-27 | 1983-12-23 | Предприятие П/Я В-2823 | Hydraulic drive of drilling machine |
| CN201513115U (en) * | 2009-08-27 | 2010-06-23 | 北京市三一重机有限公司 | High-low double-speed pressurizing system of rotary drilling rig |
| CN203296681U (en) * | 2013-06-19 | 2013-11-20 | 上海中联重科桩工机械有限公司 | Rotary drilling rig pressurizing system and rotary drilling rig with same |
| CN204312429U (en) * | 2014-11-24 | 2015-05-06 | 番禺珠江钢管有限公司 | A kind of hydraulic differential circuit system be made up of screw-in cartridge valve |
| CN105089491A (en) * | 2015-07-27 | 2015-11-25 | 北京市三一重机有限公司 | Rotary drilling rig |
| CN106438521A (en) * | 2016-11-11 | 2017-02-22 | 徐工消防安全装备有限公司 | Hydraulic circuit of the differential telescopic system and aerial work platform using hydraulic circuit of the differential telescopic system |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20180030792A1 (en) * | 2016-07-26 | 2018-02-01 | Premier Coil Solutions, Inc. | Control system and methods for moving a coiled tubing string at substantially constant rates |
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2019
- 2019-12-30 CN CN201911394155.7A patent/CN111188572B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SU1062388A1 (en) * | 1982-10-27 | 1983-12-23 | Предприятие П/Я В-2823 | Hydraulic drive of drilling machine |
| CN201513115U (en) * | 2009-08-27 | 2010-06-23 | 北京市三一重机有限公司 | High-low double-speed pressurizing system of rotary drilling rig |
| CN203296681U (en) * | 2013-06-19 | 2013-11-20 | 上海中联重科桩工机械有限公司 | Rotary drilling rig pressurizing system and rotary drilling rig with same |
| CN204312429U (en) * | 2014-11-24 | 2015-05-06 | 番禺珠江钢管有限公司 | A kind of hydraulic differential circuit system be made up of screw-in cartridge valve |
| CN105089491A (en) * | 2015-07-27 | 2015-11-25 | 北京市三一重机有限公司 | Rotary drilling rig |
| CN106438521A (en) * | 2016-11-11 | 2017-02-22 | 徐工消防安全装备有限公司 | Hydraulic circuit of the differential telescopic system and aerial work platform using hydraulic circuit of the differential telescopic system |
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| CN111188572A (en) | 2020-05-22 |
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