CN111980879A - High-pressure pulse fluid output device and rock hydraulic fracturing method - Google Patents
High-pressure pulse fluid output device and rock hydraulic fracturing method Download PDFInfo
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- CN111980879A CN111980879A CN202010688943.3A CN202010688943A CN111980879A CN 111980879 A CN111980879 A CN 111980879A CN 202010688943 A CN202010688943 A CN 202010688943A CN 111980879 A CN111980879 A CN 111980879A
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- 239000012530 fluid Substances 0.000 title claims abstract description 52
- 239000011435 rock Substances 0.000 title claims abstract description 22
- 238000000034 method Methods 0.000 title claims abstract description 15
- 239000007788 liquid Substances 0.000 claims abstract description 123
- 238000006073 displacement reaction Methods 0.000 claims abstract description 42
- 230000035485 pulse pressure Effects 0.000 claims abstract description 22
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 40
- 229910001220 stainless steel Inorganic materials 0.000 claims description 23
- 239000010935 stainless steel Substances 0.000 claims description 23
- 238000002347 injection Methods 0.000 claims description 15
- 239000007924 injection Substances 0.000 claims description 15
- 230000000694 effects Effects 0.000 claims description 12
- 230000033001 locomotion Effects 0.000 claims description 12
- 238000005336 cracking Methods 0.000 claims description 8
- 230000009471 action Effects 0.000 claims description 4
- 238000004146 energy storage Methods 0.000 claims description 4
- 238000001514 detection method Methods 0.000 claims description 2
- 238000005086 pumping Methods 0.000 claims description 2
- 239000003921 oil Substances 0.000 description 48
- 230000007246 mechanism Effects 0.000 description 23
- 239000010720 hydraulic oil Substances 0.000 description 7
- 230000008569 process Effects 0.000 description 3
- 239000000243 solution Substances 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 2
- 230000000977 initiatory effect Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000010349 pulsation Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000011109 contamination Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000000428 dust Substances 0.000 description 1
- 230000005284 excitation Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000005065 mining Methods 0.000 description 1
- 230000035699 permeability Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 230000007306 turnover Effects 0.000 description 1
- 238000009736 wetting Methods 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
- F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
- F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
- F04B9/111—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members
- F04B9/113—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members reciprocating movement of the pumping members being obtained by a double-acting liquid motor
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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
- E21B43/00—Methods or apparatus for obtaining oil, gas, water, soluble or meltable materials or a slurry of minerals from wells
- E21B43/25—Methods for stimulating production
- E21B43/26—Methods for stimulating production by forming crevices or fractures
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- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21C—MINING OR QUARRYING
- E21C37/00—Other methods or devices for dislodging with or without loading
- E21C37/06—Other methods or devices for dislodging with or without loading by making use of hydraulic or pneumatic pressure in a borehole
- E21C37/12—Other methods or devices for dislodging with or without loading by making use of hydraulic or pneumatic pressure in a borehole by injecting into the borehole a liquid, either initially at high pressure or subsequently subjected to high pressure, e.g. by pulses, by explosive cartridges acting on the liquid
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- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21C—MINING OR QUARRYING
- E21C45/00—Methods of hydraulic mining; Hydraulic monitors
- E21C45/02—Means for generating pulsating fluid jets
- E21C45/04—Means for generating pulsating fluid jets by use of highly pressurised liquid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B23/00—Pumping installations or systems
- F04B23/02—Pumping installations or systems having reservoirs
- F04B23/025—Pumping installations or systems having reservoirs the pump being located directly adjacent the reservoir
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/10—Valves; Arrangement of valves
- F04B53/1002—Ball valves
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- 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
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
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- 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
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
- F15B15/1428—Cylinders
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- 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
- F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
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Abstract
The invention discloses a high-pressure pulse fluid output device and a rock hydraulic fracturing method, wherein the high-pressure pulse fluid output device comprises a double-acting hydraulic cylinder controlled by an electro-hydraulic servo valve, a first single-acting pulse pressurizing cylinder and a second single-acting pulse pressurizing cylinder, wherein the second single-acting pulse pressurizing cylinder is provided with a displacement sensor for indirectly measuring the moving speed of an internal pressurizing piston, and one-way liquid outlet holes of the first single-acting pulse pressurizing cylinder and the second single-acting pulse pressurizing cylinder are connected to a high-pressure output main pipe; the high-pressure output main pipe is provided with a pressure sensor and a flow sensor, and the pressure sensor, the flow sensor, the displacement sensor and the electro-hydraulic servo valve are all electrically connected with the servo controller. The double-acting hydraulic cylinder controlled by the electro-hydraulic servo valve is connected with the first single-acting pulse pressurizing cylinder and the second pulse pressurizing cylinder on two sides, so that accurate hydraulic pulse pressure and pulse flow control can be realized, and the hydraulic control system has the advantages of simple structure and high stability.
Description
Technical Field
The invention belongs to the technical field of rock hydraulic fracturing, and particularly relates to a high-pressure pulse fluid output device and a rock hydraulic fracturing method.
Background
In order to improve the permeability of rocks or accelerate the wetting effect of rocks, the hydraulic fracturing technology is widely applied to the production fields of oil and gas, underground mining and the like. In the technical field of rock hydraulic fracturing, pulse hydraulic fracturing is an optimized fracturing technology for rock fracturing by converting continuous fluid into pulse fluid through a pulse device. Compared with common steady flow static fracturing, the pulse hydraulic fracturing has double-effect fracturing effects of water wedge effect and fatigue effect, and in recent years, the pulse hydraulic fracturing is applied to indoor physical model tests and field exploitation.
However, the existing pulse hydraulic fracturing device still has a plurality of performance defects. For example, the early pulse hydraulic fracturing device forms pulse fluid by using the turbulence of an excitation cavity, and the pulse effect and the pulse frequency of the device are difficult to control; the double-cylinder pulse pump applied on site directly outputs pulse fluid, the pulse frequency is controllable, but the frequency control range is small, the pulse waveform is single, and the flow output is unstable; later, in order to overcome the problems, patent CN108798673B discloses a water-driven high-pressure pulse fluid output device and an operation method thereof, which adopt two groups of single-acting pulse pressure cylinders to alternately output high-pressure pulse fluid to realize controllable pulse pressure output; however, the juxtaposed form structure of the two groups of single-acting pulse pressure cylinders is complex, the requirement on a control system is extremely high in the implementation process, and the difficulty in the double-cylinder reverse phase cooperative control is extremely high.
In view of the above, there is a need for improvements in the prior art.
Disclosure of Invention
The invention aims to provide a high-pressure pulse fluid output device and a rock hydraulic fracturing method.
In order to achieve the purpose, the invention adopts the following technical scheme:
the high-pressure pulse fluid output device comprises a double-acting hydraulic cylinder controlled by an electro-hydraulic servo valve, and a first single-acting pulse pressurizing cylinder and a second single-acting pulse pressurizing cylinder which have the same structure, wherein two ends of a piston rod of the double-acting hydraulic cylinder are respectively butted with pressurizing pistons of the first single-acting pulse pressurizing cylinder and the second single-acting pulse pressurizing cylinder on two sides;
a displacement sensor for indirectly measuring the moving speed of a pressurizing piston inside the second single-action pulse pressurizing cylinder is arranged on the second single-action pulse pressurizing cylinder, and the one-way liquid outlet holes of the first single-action pulse pressurizing cylinder and the second single-action pulse pressurizing cylinder are connected to a high-pressure output main pipe;
and the high-pressure output main pipe is provided with a pressure sensor and a flow sensor, and the pressure sensor, the flow sensor, the displacement sensor and the electro-hydraulic servo valve are all electrically connected with the servo controller.
Specifically, the servo controller is connected to an industrial personal computer.
Specifically, the displacement sensor is a magnetic displacement sensor, a pressurizing piston in the second single-acting pulse pressurizing cylinder is provided with a measuring rod mounting hole, a magnetic ring of the magnetic displacement sensor is fixedly mounted in the measuring rod mounting hole, the measuring rod of the magnetic displacement sensor coaxially penetrates through the magnetic ring and is inserted into the measuring rod mounting hole, and the axis of the measuring rod mounting hole and the axis of the magnetic ring are parallel to the moving direction of the pressurizing piston.
Specifically, a first one-way liquid inlet hole, a first one-way liquid outlet hole and a liquid outlet hole are formed in the first single-action pulse pressurizing cylinder, and a second one-way liquid inlet hole and a second one-way liquid outlet hole are formed in the second single-action pulse pressurizing cylinder;
the first one-way liquid inlet hole is connected with a first normally-open electromagnetic stop valve, the first one-way liquid outlet hole is connected with a second normally-open electromagnetic stop valve, the liquid outlet hole is connected with a first normally-closed electromagnetic stop valve, the second one-way liquid inlet hole is connected with a third normally-open high-pressure stop valve, and the second one-way liquid outlet hole is connected with a two-position three-way high-pressure electromagnetic valve;
the first normally-open type electromagnetic stop valve, the first normally-closed type electromagnetic stop valve, the second normally-open type electromagnetic stop valve, the third normally-open type high-pressure stop valve and the two-position three-way high-pressure electromagnetic valve are all connected with the servo controller.
Specifically, the output device further comprises a water tank, and the water tank is connected with the two-position three-way high-pressure electromagnetic valve, the first normally-open type electromagnetic stop valve and the third normally-open type high-pressure stop valve.
Specifically, an adjustable high-pressure overflow valve is arranged between the water tank and the high-pressure output main pipe.
Specifically, the second normally open type electromagnetic stop valve, the first normally closed type electromagnetic stop valve and the two-position three-way high-pressure electromagnetic valve are respectively connected with the input end of the high-pressure output main pipe through a first high-pressure output pipe, a second high-pressure output pipe and a third high-pressure output pipe.
Specifically, still be equipped with the stainless steel energy storage ware on the high pressure output house steward, the high pressure output house steward with be provided with the normal close formula electromagnetism stop valve of second between the stainless steel energy storage ware, the normal close formula electromagnetism stop valve of second with servo controller electric connection.
Specifically, the output device also comprises an oil tank, a hydraulic pump and an oil check valve;
the oil tank is connected with an oil supply hole of the electro-hydraulic servo valve through an oil supply passage, the hydraulic pump and the oil check valve are arranged on the oil supply passage, and an overflow valve, an inflatable accumulator and a pressure gauge are further arranged on the oil supply passage;
an oil return port of the electro-hydraulic servo valve is connected with the oil tank through a high-pressure oil pipe, and two output ports of the electro-hydraulic servo valve are respectively connected with two oil inlets of the double-acting hydraulic cylinder.
Specifically, the oil supply passage is further provided with a first oil filter and a second oil filter.
The rock hydraulic fracturing method adopting the high-pressure pulse fluid output device comprises the following steps:
step one, pre-injecting liquid
Connecting a high-pressure output main pipe with a fracturing pipe in a rock fracturing hole, injecting fracturing fluid into a water tank, taking the moving speed of a pressurizing piston monitored by a displacement sensor as a feedback signal, inputting a square wave moving speed control signal with positive and negative symmetry to a servo controller, controlling the reciprocating uniform motion of a hydraulic piston of a double-acting hydraulic cylinder by an electro-hydraulic servo valve, further pushing the pressurizing pistons of a first single-acting pulse pressurizing cylinder and a second single-acting pulse pressurizing cylinder to reciprocate at a uniform speed through a piston rod, alternately sucking water from the water tank at a uniform speed through a corresponding first single-phase liquid inlet hole and a corresponding second single-phase liquid inlet hole, alternately pumping water to the high-pressure output main pipe at a uniform speed, and indicating that the high-pressure output main pipe and the fracturing pipe are basically filled with the fracturing fluid after detection values of a flow sensor and a pressure sensor are stable;
step two, pressure control type pulse liquid injection in early stage
Controlling a pressurizing piston of the first single-action pulse pressurizing cylinder to retract to a limit position, namely controlling the first normally-open electromagnetic stop valve, the second normally-open electromagnetic stop valve and the third normally-open high-pressure stop valve to be closed, wherein the first single-action pulse pressurizing cylinder is filled with water; controlling the two-position three-way high-pressure electromagnetic valve to act, so that the second single-phase liquid outlet hole is decompressed through the two-position three-way high-pressure electromagnetic valve; controlling the first normally closed type electromagnetic stop valve to be opened, namely, the fluid in the corresponding liquid outlet hole is communicated to the high-pressure output main pipe, and at the moment, only the first single-action pulse pressure cylinder is connected with the high-pressure output main pipe;
the method comprises the steps that liquid pressure monitored by a pressure sensor is used as a feedback signal, a pulse pressure control signal is input to a servo controller, the pressure peak value is smaller than a rock cracking pressure value calculated theoretically, an electro-hydraulic servo valve controls a hydraulic piston of a double-acting hydraulic cylinder to reciprocate, a pressurizing piston of a first single-acting pulse pressurizing cylinder is pushed by a piston rod to reciprocate, at the moment, cracking liquid in the cylinder is alternately pushed out and sucked from a liquid outlet hole, a pair pressure lifting waveform is generated in a high-pressure output header pipe, the frequency, waveform and duration of servo control input are adjusted, a corresponding pulse pressure wave effect is generated in a rock cracking hole, and the fatigue pulse effect before fracturing is achieved;
step three, middle-period continuous liquid injection fracturing
After pressure control type pulse injection is completed, a moving speed monitored by a displacement sensor is used as a feedback signal, a negative constant-speed moving speed control signal is input into a servo controller, an electro-hydraulic servo valve controls a hydraulic piston of a double-acting hydraulic cylinder to advance towards a first single-acting pulse pressurizing cylinder at a constant speed, the pressurizing piston of the first single-acting pulse pressurizing cylinder is pushed to advance at a constant speed through a piston rod, corresponding in-cylinder fracturing fluid is continuously pushed out from a liquid outlet, the pressure in a high-pressure output header pipe and a fracturing pipe is continuously increased, and the pressure is monitored by a pressure sensor until the cracking pressure of a fracturing hole is reached; after hydraulic cracks are generated and the pressure is suddenly reduced, the pressure control type liquid injection is invalid;
step four, later-period flow control type pulse liquid injection
Controlling the first normally closed electromagnetic stop valve to be closed, namely disconnecting the liquid outlet hole from the outside; then, the first normally-open type electromagnetic stop valve, the second normally-open type electromagnetic stop valve and the third normally-open type high-pressure stop valve are controlled to be opened, and the two-position three-way high-pressure electromagnetic valve is controlled to be reset, so that the second one-way liquid outlet hole is connected with the high-pressure output main pipe through the two-position three-way high-pressure electromagnetic valve;
the method comprises the steps that a moving speed monitored by a displacement sensor is used as a feedback signal, a moving speed control signal is input to a servo controller, an electro-hydraulic servo valve controls a hydraulic piston of a double-acting hydraulic cylinder to do reciprocating non-uniform motion, the piston rod pushes pressurizing pistons of a first single-acting pulse pressurizing cylinder and a second single-acting pulse pressurizing cylinder to do non-uniform reciprocating motion, a corresponding first one-way liquid inlet hole and a corresponding second one-way liquid inlet hole alternately suck water from a water tank at a non-uniform speed, a corresponding first one-way liquid outlet hole and a corresponding second one-way liquid outlet hole alternately pump water to a high-pressure output main pipe at a non-uniform speed to form pulse flow output, a flow sensor monitors a pulse flow output state, at the moment, fracturing liquid is continuously input in a fracturing pipe in a flow pulse mode, further pulse action is generated on a formed hydraulic crack, and the fracturing.
Compared with the prior art, the invention has the beneficial effects that:
1. the pulse flow is accurate and controllable: a double-acting hydraulic pulse pressurization mechanism is adopted, and the reciprocating displacement stroke and the reciprocating speed of a pressurization piston are controlled through the cooperation of a displacement sensor and an electro-hydraulic servo valve, so that the reciprocating displacement stroke and the reciprocating speed are converted into the accurate control of real-time flow pulses of a first single-acting pulse pressurization cylinder and a second single-acting pulse pressurization cylinder.
2. The pulse pressure is accurate and controllable: the double-acting hydraulic pulse supercharging mechanism is adopted, a first single-acting pulse supercharging cylinder of the double-acting hydraulic pulse supercharging mechanism is provided with a liquid outlet hole, when pulse pressure waveform output is carried out, the liquid outlet hole is directly communicated with a high-pressure output main pipe, closed-loop control of pressure waveforms is carried out under the state that other liquid inlet and outlet ports are locked, and the full-range high-precision control of the pulse pressure waveform is realized.
3. The structure is simplified, and stability is high: when the double-acting hydraulic pulse supercharging mechanism is adopted to execute pressure pulse and flow pulse coupled hydraulic output, only one set of double-acting hydraulic cylinder, one set of electro-hydraulic servo valve and one set of servo controller are needed, and the relevant electromagnetic valves are matched to realize all functions.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings needed to be used in the description of the embodiments will be briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without creative efforts.
Fig. 1 is a schematic structural diagram of a high-pressure pulse fluid output device provided by an embodiment of the invention;
FIG. 2 is an isometric view of a double acting hydraulic pulse pressurization mechanism provided by an embodiment of the present invention;
FIG. 3 is a front cross-sectional view of a double acting hydraulic pulse pressurization mechanism provided by an embodiment of the present invention;
wherein: 1-hydraulic oil source and control mechanism; 2-double-acting hydraulic pulse supercharging mechanism; 3-a high-pressure fluid output mechanism; 4-a hydraulic oil source device; 5-a fluid control device; 6-high pressure oil pipe; 7-an oil tank; 8-a first oil filter; 9-a hydraulic pump; 10-check valve for oil; 11-a second oil filter; 12-an overflow valve; 13-a gas-filled accumulator; 14-pressure gauge; 15-three-position four-way electro-hydraulic servo valve; 16-a servo controller; 17-an industrial personal computer; 18-oil supply holes; 19-oil return port; 20-an output port; 21-double acting hydraulic cylinder; 22-a first single-acting pulse pressurized cylinder; 23-a second single-acting pulsed pressurized cylinder; 24-stainless steel pressurized cylinder; 25-a booster piston; 26-a cylinder cover; 27-a first one-way liquid inlet hole; 28-a first one-way liquid outlet hole; 29-liquid outlet holes; 30-liquid inlet one-way valve; 31-a first normally open electromagnetic stop valve; 32-liquid outlet one-way valve; 33-a second normally open electromagnetic stop valve; 34-a first normally closed electromagnetic stop valve; 35-a second one-way liquid inlet hole; 36-a second one-way liquid outlet hole; 37-a third normally open high pressure stop valve; 38-two-position three-way high-pressure solenoid valve; 39-displacement sensor attachment holes; 40-step-shaped round holes; 41-a magnetic displacement sensor; 42-a magnetic ring; 43-a measuring rod; 44-electron processing unit body; 45-high pressure seal ring; 46-a hydraulic piston; 47-a piston rod; 48-a first high pressure output pipe; 49-a second high pressure output pipe; 50-a third high pressure output pipe; 51-a high pressure output manifold; 52-a water tank; 53-a first output port; 54-a pressure sensor; 55-a flow sensor; 56-stainless steel accumulator; 57-a second normally closed electromagnetic stop valve; 58-high pressure relief valve; 59-a second output port; 60-high pressure pipeline.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
Referring to fig. 1, a high-pressure pulse fluid output device comprises a hydraulic oil source and control mechanism 1, a double-acting hydraulic pulse supercharging mechanism 2 and a high-pressure fluid output mechanism 3, wherein the hydraulic oil source and control mechanism 1 is matched with the double-acting hydraulic pulse supercharging mechanism 2 and is used for providing a hydraulic driving oil source and a servo control instruction; the double-acting hydraulic pulse supercharging mechanism 2 is connected with the high-pressure fluid output mechanism 3 and outputs controllable high-pressure pulsation and flow pulsation.
Referring to fig. 1, a hydraulic oil source and control mechanism 1 is mainly composed of a hydraulic oil source device 4 and a fluid control device 5; the hydraulic oil source device 4 comprises an oil tank 7, a hydraulic pump 9 and an oil check valve 10, wherein the oil tank 7, the hydraulic pump 9 and the oil check valve 10 are sequentially connected through a high-pressure oil pipe 6 to form an oil supply passage, and the oil supply passage is also provided with an overflow valve 12 for controlling the pressure of the oil supply passage, an inflatable accumulator 13 for maintaining the pressure of the oil supply passage to be stable and a pressure gauge 14 for displaying the oil pressure of the oil supply passage; the fluid control device 5 mainly comprises a three-position four-way electro-hydraulic servo valve 15, a servo controller 16 and an industrial personal computer 17; an oil supply hole 18 of the electro-hydraulic servo valve 15 is connected with an oil supply passage, an oil return port 19 of the electro-hydraulic servo valve 15 is connected with the oil tank 7 through a high-pressure oil pipe 6, and two output ports 20 of the electro-hydraulic servo valve 15 are connected with the double-acting hydraulic pulse supercharging mechanism 2 through the high-pressure oil pipe 6; the electro-hydraulic servo valve 15 is also electrically connected with a servo controller 16 and an industrial personal computer 17 in sequence.
In practical applications, the first oil filter 8 and the second oil filter 11 may be provided in the oil supply passage, and the relief valve 12, the charge accumulator 13, and the pressure gauge 14 may be provided in the oil supply passage between the oil check valve 10 and the second oil filter 11.
Referring to fig. 1-3, the double-acting hydraulic pulse pressurizing mechanism 2 comprises a double-acting hydraulic cylinder 21 controlled by an electro-hydraulic servo valve 15, a first single-acting pulse pressurizing cylinder 22 connected to one end of the double-acting hydraulic cylinder 21, and a second single-acting pulse pressurizing cylinder 23 connected to the other end of the double-acting hydraulic cylinder 21, wherein the first single-acting pulse pressurizing cylinder 22 and the second single-acting pulse pressurizing cylinder 23 have the same structure, are plunger type pressurizing structures, and comprise a stainless steel pressurizing cylinder 24, a pressurizing piston 25 and a cylinder cover 26;
in practical application, a first one-way liquid inlet hole 27, a first one-way liquid outlet hole 28 and a liquid outlet hole 29 are arranged in the stainless steel pressure cylinder 24 at the front end of the pressure piston 25 of the first single-action pulse pressure cylinder 22; the first one-way liquid inlet hole 27 is connected with a first normally open type electromagnetic stop valve 31 towards the outer side of the stainless steel pressure cylinder 24; the first one-way liquid outlet hole 28 is connected with a second normally open type electromagnetic stop valve 33 towards the outer side of the stainless steel pressure cylinder 24; the liquid outlet 29 is connected with a first normally closed electromagnetic stop valve 34 towards the outer side of the stainless steel pressure cylinder 24; a second one-way liquid inlet hole 35 and a second one-way liquid outlet hole 36 are arranged in the stainless steel pressure cylinder 24 at the front end of the pressure piston 25 of the second single-action pulse pressure cylinder 23; the second one-way liquid inlet hole 35 is connected with a third normally open type high-pressure stop valve 37 towards the outer side of the stainless steel pressurizing cylinder 24; the second one-way liquid outlet hole 36 is connected with a two-position three-way high-pressure electromagnetic valve 38 towards the outer side of the stainless steel pressure cylinder 24; the first one-way liquid inlet hole 27 and the second one-way liquid inlet hole 35 are liquid inlet one-way valves 30 arranged on the liquid inlet holes, and the first one-way liquid outlet hole 28 and the second one-way liquid outlet hole 36 are liquid outlet one-way valves 32 arranged on the liquid outlet holes.
A displacement sensor connecting hole 39 is formed in the center of the stainless steel pressure cylinder 24 at the front end of the pressure piston 25 of the second single-action pulse pressure cylinder 23, and a step-shaped round hole 40 is formed from the center of the front end face of the pressure piston 25 of the second single-action pulse pressure cylinder 23 to the inside of the pressure piston 25; a magnetic displacement sensor (magnetostrictive displacement sensor) 41 for indirectly measuring the movement speed of the booster piston is arranged on the front side of the stainless steel booster cylinder 24 of the second single-acting pulse booster cylinder 23, a magnetic ring 42 of the magnetic displacement sensor 41 is coaxially assembled at the front end of the stepped round hole 40, and a measuring rod 43 of the magnetic displacement sensor 41 is inserted into the cylinder through a displacement sensor connecting hole 39 and further coaxially inserted into the stepped round hole (measuring rod mounting hole) 40 through the center of the magnetic ring 42; the rear end of the measuring rod 43 is connected with an electronic processing unit body 44 of the magnetic displacement sensor 41 outside the stainless steel pressure cylinder 24, the electronic processing unit body 44 is fastened outside the displacement sensor connecting hole 39 in a bolt manner, and a high-pressure sealing ring 45 is arranged at the connecting position; the hole depth of the stepped round hole 40 is twice of the length of the measuring rod 43, the hole diameter is larger than the rod diameter of the measuring rod 43, a hydraulic piston 46 arranged in the center of the double-acting hydraulic cylinder 21 is connected with the pressurizing pistons 25 on the two sides through a piston rod 47, and the area of the hydraulic piston 46 is three to six times of that of the pressurizing piston 25. Of course, other types of displacement sensors can be used, but with the magnetic displacement sensor 41, since the movable magnetic ring 42 and the measuring rod (sensing element) 43, which are used for determining the position, are not in direct contact, the sensor can be used in extremely harsh industrial environments and is not susceptible to oil stains, solutions, dust or other contamination.
In the embodiment of the application, a double-acting hydraulic pulse pressurization mechanism is adopted, and the reciprocating displacement stroke and the reciprocating speed of a pressurization piston are controlled through the cooperation of a displacement sensor and an electro-hydraulic servo valve, so that the reciprocating displacement stroke and the reciprocating speed are converted into the accurate control of real-time flow pulses of a first single-acting pulse pressurization cylinder and a second single-acting pulse pressurization cylinder.
Referring to fig. 1-3, the high-pressure fluid output mechanism 3 is composed of a first high-pressure output pipe 48, a second high-pressure output pipe 49, a third high-pressure output pipe 50, a high-pressure output manifold 51 and a water tank 52; the first high-pressure output pipe 48, the second high-pressure output pipe 49, the third high-pressure output pipe 50 and the high-pressure output main pipe 51 are all high-pressure hard pipes; the first high-pressure output pipe 48 is connected with the second normally-open electromagnetic stop valve 33, and is used for communicating the high-pressure fluid in the first one-way liquid outlet hole 28 to the high-pressure output header pipe 51; the second high-pressure output pipe 49 is connected with the first normally closed type electromagnetic stop valve 34, and communicates the high-pressure fluid in the liquid outlet hole 29 to the high-pressure output header pipe 51 when the valve is opened, the third high-pressure output pipe 50 is connected with the first output port 53 of the two-position three-way high-pressure electromagnetic valve 38, and communicates the high-pressure fluid in the second one-way liquid outlet hole 36 to the high-pressure output header pipe 51 when the valve is opened, the high-pressure output header pipe 51 is provided with a pressure sensor 54, a flow sensor 55 and a stainless steel energy accumulator 56, a second normally closed type electromagnetic stop valve 57 is further arranged between the high-pressure output header pipe 51 and the stainless steel energy accumulator 56, an adjustable high-pressure overflow valve 58 is arranged between the water tank 52 and the high-pressure output header pipe 51, and the water tank 52 is further connected with the second output port 59 of.
Referring to fig. 1, the servo controller 16 is further electrically connected in parallel with the first normally-open type electromagnetic cut-off valve 31, the second normally-open type electromagnetic cut-off valve 33, the third normally-open type high-pressure cut-off valve 37, the first normally-closed type electromagnetic cut-off valve 34, the second normally-closed type electromagnetic cut-off valve 57, the two-position three-way high-pressure electromagnetic valve 38, the magnetic displacement sensor 41, the pressure sensor 54, and the flow sensor 55.
In this application embodiment, adopted two effect water conservancy pulse booster mechanisms, its first single-action pulse pressure cylinder be provided with out the liquid hole, when carrying out pulse pressure waveform output, go out the direct and high-pressure output house steward of liquid hole and switch on, under other business turn over liquid mouth states of locking, carry out the closed-loop control of pressure waveform, realize the high accuracy control of pulse pressure waveform full stroke.
In addition, this application embodiment only needs one set of two effect pneumatic cylinders, one set of electro-hydraulic servo valve and one set of servo controller, and the relevant solenoid valve of cooperation can realize whole functions, compares in current device, and its simple structure need not to carry out coordinated control, has improved device stability, and the cost is reduced.
Referring to fig. 1-3, the specific process of hydraulic fracturing rock by using the high-pressure pulse fluid output device of the above embodiment is as follows:
step one, pre-injecting liquid
Firstly, connecting a high-pressure output main pipe 51 with a fracturing pipe in a rock fracturing hole by using a high-pressure pipeline 60, injecting fracturing fluid into a water tank 52, and adjusting an adjustable high-pressure overflow valve 58 to an extremely low level of pressure; then, the high-pressure pulse fluid output device is started, and the second normally closed electromagnetic stop valve 57 is controlled to be opened so as to communicate with the stainless steel energy accumulator 56, and a square wave movement speed control signal with positive and negative symmetry is input to the servo controller 16 by taking the movement speed monitored by the magnetic displacement sensing as a feedback signal;
then, the electro-hydraulic servo valve 15 controls the hydraulic piston 46 of the double-acting hydraulic cylinder 21 to reciprocate at a constant speed, further the piston rod 47 pushes the pressurizing piston 25 of the first single-acting pulse pressurizing cylinder 22 and the second single-acting pulse pressurizing cylinder 23 to reciprocate at a constant speed, the corresponding first one-way liquid inlet hole 27 and the second one-way liquid inlet hole 35 alternately suck water from the water tank 52 at a constant speed, the corresponding first one-way liquid outlet hole 28 and the second one-way liquid outlet hole 36 alternately pump water to the first high-pressure output pipe 48 and the third high-pressure output pipe 50 at a constant speed, the water is collected into the high-pressure output header pipe 51 to form continuous flow without interruption, the continuous flow is further kept stable under the regulation and control of the stainless steel energy accumulator 56, and the flow sensor 55 monitors the output of constant flow; after that, when the adjustable high-pressure overflow valve 58 reaches the set pressure value, the relief flow is opened, and the pressure signal of the pressure sensor 54 is maintained stable, so that the high-pressure pipeline 60 and the fracturing pipe are indicated to be basically filled with the fracturing fluid.
Step two, pressure control type pulse liquid injection in early stage
Firstly, controlling the booster piston 25 of the first single-acting pulse booster cylinder 22 to retract to the limit position, namely, the first single-acting pulse booster cylinder 22 is filled with water; then, the second normally closed electromagnetic stop valve 57 is controlled to close to disconnect the stainless steel accumulator 56 from the high-pressure output manifold 51, and the adjustable high-pressure relief valve 58 is adjusted to the maximum relief pressure; then, the first normally-open type electromagnetic stop valve 31, the second normally-open type electromagnetic stop valve 33 and the third normally-open type high-pressure stop valve 37 are controlled to be closed, namely the corresponding first one-way liquid inlet hole 27, the corresponding first one-way liquid outlet hole 28 and the corresponding second one-way liquid inlet hole 35 are closed; controlling the two-position three-way high-pressure electromagnetic valve 38 to act, so that the second one-way liquid outlet hole 36 is connected with the water tank 52 for pressure relief through a second output port 59 of the two-position three-way high-pressure electromagnetic valve 38; the first normally closed electromagnetic stop valve 34 is controlled to be opened, namely the fluid in the corresponding liquid outlet hole 29 is communicated to the high-pressure output header pipe 51 through the second high-pressure output pipe 49, and at the moment, only the first single-action pulse pressurizing cylinder 22 is connected with the high-pressure output header pipe 51;
then, the liquid pressure monitored by the pressure sensor 54 is used as a feedback signal, a pulse pressure control signal with a sine wave, a square wave, a triangular wave or any waveform is input to the servo controller 16, and the pressure peak value is smaller than the rock fracture initiation pressure value calculated in theory; after that, the electro-hydraulic servo valve 15 controls the reciprocating motion of the hydraulic piston 46 of the double-acting hydraulic cylinder 21, the piston rod 47 pushes the pressurizing piston 25 of the first single-acting pulse pressurizing cylinder 22 to reciprocate, at this time, the fracturing fluid in the cylinder is alternately pushed out and sucked from the liquid outlet hole 29, a pair pressure lifting waveform is generated in the high-pressure output main pipe 51, the frequency, the waveform and the duration of the servo control input are adjusted, and then a corresponding pulse pressure wave action is generated in the rock fracturing hole, so that the fatigue pulse effect before fracturing is achieved.
Step three, middle-period continuous liquid injection fracturing
After the pressure control type pulse liquid injection is finished, a negative constant-speed moving speed control signal is input to the servo controller 16 by taking the moving speed monitored by the magnetic displacement sensor as a feedback signal; furthermore, the electro-hydraulic servo valve 15 controls the hydraulic piston 46 of the double-acting hydraulic cylinder 21 to advance towards the first single-acting pulse pressurized cylinder 22 at a constant speed, the pressurized piston 25 of the first single-acting pulse pressurized cylinder 22 is pushed by the piston rod 47 to advance at a constant speed, the corresponding in-cylinder fracturing fluid is continuously pushed out from the liquid outlet 29, the pressure in the high-pressure output main pipe 51 and the fracturing pipe is continuously increased, the pressure is monitored by the pressure sensor 54 until the fracture initiation pressure of the fracturing hole is reached, and after a hydraulic fracture is generated, the pressure is suddenly reduced, and the pressure control type liquid injection fails.
Step four, later-period flow control type pulse liquid injection
The first normally closed electromagnetic stop valve 34 is controlled to be closed, namely the liquid outlet hole 29 is disconnected from the outside; then, the first normally-open type electromagnetic stop valve 31, the second normally-open type electromagnetic stop valve 33 and the third normally-open type high-pressure stop valve 37 are controlled to be opened, namely the corresponding first one-way liquid inlet hole 27, the corresponding first one-way liquid outlet hole 28 and the corresponding second one-way liquid inlet hole 35 are opened; the two-position three-way high-pressure electromagnetic valve 38 is controlled to reset, so that the second one-way liquid outlet hole 36 is connected with the third high-pressure output pipe 50 through the first output port 53 of the two-position three-way high-pressure electromagnetic valve 38; at the moment, the double-acting hydraulic pulse supercharging mechanism 2 returns to the state of the first step;
then, the stainless steel energy accumulator 56 is kept disconnected from the high-pressure output manifold 51, the moving speed monitored by the magnetic displacement sensor is used as a feedback signal, a moving speed control signal of sine wave or duty square wave or triangular wave or any waveform is input to the servo control, the electro-hydraulic servo valve 15 controls the reciprocating non-uniform motion of the hydraulic piston 46 of the double-acting hydraulic cylinder 21, the piston rod 47 pushes the pressurizing pistons 25 of the first single-acting pulse pressurizing cylinder 22 and the second single-acting pulse pressurizing cylinder 23 to do non-uniform reciprocating motion, the corresponding first one-way liquid inlet hole 27 and the second one-way liquid inlet hole 35 alternately suck water from the water tank 52 at a non-uniform speed, the corresponding first one-way liquid outlet hole 28 and the corresponding second one-way liquid outlet hole 36 alternately pump water to the first high-pressure output pipe 48 and the first high-pressure output pipe 48 at a non-uniform speed, and the water is collected into the high-pressure output manifold 51 to form pulse, the flow sensor 55 monitors the pulse flow output status; at the moment, the fracturing fluid is continuously input in the fracturing pipe in the form of flow pulse, further pulse action is generated on the formed hydraulic fracture, and the later expansion process of the hydraulic fracture is continuously acted.
The above examples are merely illustrative for clearly illustrating the present invention and are not intended to limit the embodiments. Other variations and modifications will be apparent to persons skilled in the art in light of the above description. Nor is it intended to be exhaustive of all embodiments. And obvious variations or modifications of the invention may be made without departing from the scope of the invention.
Claims (10)
1. High-pressure pulse fluid output device, its characterized in that: the hydraulic system comprises a double-acting hydraulic cylinder controlled by an electro-hydraulic servo valve, and a first single-acting pulse pressurizing cylinder and a second single-acting pulse pressurizing cylinder which are same in structure, wherein two ends of a piston rod of the double-acting hydraulic cylinder are respectively butted with pressurizing pistons of the first single-acting pulse pressurizing cylinder and the second single-acting pulse pressurizing cylinder on two sides;
a displacement sensor for indirectly measuring the moving speed of a pressurizing piston in the second single-action pulse pressurizing cylinder is arranged on the second single-action pulse pressurizing cylinder, and one-way liquid outlet holes of the first single-action pulse pressurizing cylinder and the second single-action pulse pressurizing cylinder are connected to a high-pressure output main pipe;
and the high-pressure output main pipe is provided with a pressure sensor and a flow sensor, and the pressure sensor, the flow sensor, the displacement sensor and the electro-hydraulic servo valve are all electrically connected with the servo controller.
2. The high-pressure pulsed fluid output device according to claim 1, characterized in that: the displacement sensor is a magnetic displacement sensor, a pressurizing piston in the second single-action pulse pressurizing cylinder is provided with a measuring rod mounting hole, a magnetic ring of the magnetic displacement sensor is fixedly mounted in the measuring rod mounting hole, a measuring rod of the magnetic displacement sensor coaxially penetrates through the magnetic ring and is inserted into the measuring rod mounting hole, and the axis of the measuring rod mounting hole and the axis of the magnetic ring are parallel to the moving direction of the pressurizing piston.
3. The high-pressure pulsed fluid output device according to claim 2, characterized in that: the first single-action pulse pressurizing cylinder is provided with a first one-way liquid inlet hole, a first one-way liquid outlet hole and a liquid outlet hole, and the second single-action pulse pressurizing cylinder is provided with a second one-way liquid inlet hole and a second one-way liquid outlet hole;
the first one-way liquid inlet hole is connected with a first normally-open electromagnetic stop valve, the first one-way liquid outlet hole is connected with a second normally-open electromagnetic stop valve, the liquid outlet hole is connected with a first normally-closed electromagnetic stop valve, the second one-way liquid inlet hole is connected with a third normally-open high-pressure stop valve, and the second one-way liquid outlet hole is connected with a two-position three-way high-pressure electromagnetic valve;
the first normally-open type electromagnetic stop valve, the first normally-closed type electromagnetic stop valve, the second normally-open type electromagnetic stop valve, the third normally-open type high-pressure stop valve and the two-position three-way high-pressure electromagnetic valve are all connected with the servo controller.
4. The high-pressure pulsed fluid output device according to claim 3, characterized in that: the output device further comprises a water tank, and the water tank is connected with the two-position three-way high-pressure electromagnetic valve, the first normally-open type electromagnetic stop valve and the third normally-open type high-pressure stop valve.
5. The high-pressure pulsed fluid output device according to claim 4, characterized in that: an adjustable high-pressure overflow valve is arranged between the water tank and the high-pressure output main pipe.
6. The high-pressure pulsed fluid output device according to claim 4, characterized in that: the second normally open type electromagnetic stop valve, the first normally closed type electromagnetic stop valve and the two-position three-way high-pressure electromagnetic valve are respectively connected with the input end of the high-pressure output main pipe through a first high-pressure output pipe, a second high-pressure output pipe and a third high-pressure output pipe.
7. The high-pressure pulsed fluid output device according to claim 4, characterized in that: still be equipped with the stainless steel energy storage ware on the high pressure output house steward, the high pressure output house steward with be provided with the normal close formula electromagnetism stop valve of second between the stainless steel energy storage ware, the normal close formula electromagnetism stop valve of second with servo controller electric connection.
8. The high-pressure pulsed fluid output device according to any one of claims 4 to 7, characterized in that: the output device also comprises an oil tank, a hydraulic pump and an oil check valve;
the oil tank is connected with an oil supply hole of the electro-hydraulic servo valve through an oil supply passage, the hydraulic pump and the oil check valve are arranged on the oil supply passage, and an overflow valve, an inflatable accumulator and a pressure gauge are further arranged on the oil supply passage;
an oil return port of the electro-hydraulic servo valve is connected with the oil tank through a high-pressure oil pipe, and two output ports of the electro-hydraulic servo valve are respectively connected with two oil inlets of the double-acting hydraulic cylinder.
9. The high-pressure pulsed fluid output device of claim 8, wherein: the oil supply passage is also provided with a first oil filter and a second oil filter.
10. Rock hydraulic fracturing method using a high pressure pulsed fluid output device according to any of claims 4 to 9, characterized in that it comprises:
step one, pre-injecting liquid
Connecting a high-pressure output main pipe with a fracturing pipe in a rock fracturing hole, injecting fracturing fluid into a water tank, taking the moving speed of a pressurizing piston monitored by displacement sensing as a feedback signal, inputting a square wave moving speed control signal with positive and negative symmetry to a servo controller, controlling the reciprocating uniform motion of a hydraulic piston of a double-acting hydraulic cylinder by an electro-hydraulic servo valve, further pushing the pressurizing pistons of a first single-acting pulse pressurizing cylinder and a second single-acting pulse pressurizing cylinder to reciprocate at a uniform speed through a piston rod, alternately sucking water from the water tank at a uniform speed through a corresponding first single-phase liquid inlet hole and a corresponding second single-phase liquid inlet hole, alternately pumping water to the high-pressure output main pipe at a uniform speed, and indicating that the high-pressure output main pipe and the fracturing pipe are basically filled with the fracturing fluid after detection values of a flow sensor and a pressure sensor are stable;
step two, pressure control type pulse liquid injection in early stage
Controlling a pressurizing piston of the first single-action pulse pressurizing cylinder to retract to a limit position, namely controlling the first normally-open electromagnetic stop valve, the second normally-open electromagnetic stop valve and the third normally-open high-pressure stop valve to be closed, wherein the first single-action pulse pressurizing cylinder is filled with water; controlling the two-position three-way high-pressure electromagnetic valve to act, so that the second single-phase liquid outlet hole is decompressed through the two-position three-way high-pressure electromagnetic valve; controlling the first normally closed type electromagnetic stop valve to be opened, namely, the fluid in the corresponding liquid outlet hole is communicated to the high-pressure output main pipe, and at the moment, only the first single-action pulse pressure cylinder is connected with the high-pressure output main pipe;
the method comprises the steps that liquid pressure monitored by a pressure sensor is used as a feedback signal, a pulse pressure control signal is input to a servo controller, the pressure peak value is smaller than a rock cracking pressure value calculated theoretically, an electro-hydraulic servo valve controls a hydraulic piston of a double-acting hydraulic cylinder to reciprocate, a pressurizing piston of a first single-acting pulse pressurizing cylinder is pushed by a piston rod to reciprocate, at the moment, cracking liquid in the cylinder is alternately pushed out and sucked from a liquid outlet hole, the frequency, waveform and duration time of servo control input are adjusted, and a corresponding pulse pressure wave effect is generated in a rock cracking hole, so that a fatigue pulse effect before cracking is achieved;
step three, middle-period continuous liquid injection fracturing
After pressure control type pulse injection is finished, a moving speed monitored by a displacement sensor is used as a feedback signal, a negative constant-speed moving speed control signal is input into a servo controller, an electro-hydraulic servo valve controls a hydraulic piston of a double-acting hydraulic cylinder to advance towards a first single-acting pulse pressurizing cylinder at a constant speed, the pressurizing piston of the first single-acting pulse pressurizing cylinder is pushed to advance at a constant speed through a piston rod, corresponding in-cylinder fracturing fluid is continuously pushed out from a liquid outlet, the pressure in a high-pressure output header pipe and a fracturing pipe is continuously increased, the pressure is monitored by a pressure sensor until the fracturing pressure of a fracturing hole is reached, and after a hydraulic crack is generated, the pressure control type injection fails after the pressure is suddenly reduced;
step four, later-period flow control type pulse liquid injection
Controlling the first normally closed electromagnetic stop valve to be closed, namely disconnecting the liquid outlet hole from the outside; then, the first normally-open type electromagnetic stop valve, the second normally-open type electromagnetic stop valve and the third normally-open type high-pressure stop valve are controlled to be opened, and the two-position three-way high-pressure electromagnetic valve is controlled to be reset, so that the second one-way liquid outlet hole is connected with the high-pressure output main pipe through the two-position three-way high-pressure electromagnetic valve;
the method comprises the steps that a moving speed monitored by a displacement sensor is used as a feedback signal, a moving speed control signal is input to a servo controller, an electro-hydraulic servo valve controls a hydraulic piston of a double-acting hydraulic cylinder to do reciprocating non-uniform motion, the piston rod pushes pressurizing pistons of a first single-acting pulse pressurizing cylinder and a second single-acting pulse pressurizing cylinder to do non-uniform reciprocating motion, a corresponding first one-way liquid inlet hole and a corresponding second one-way liquid inlet hole alternately suck water from a water tank at a non-uniform speed, a corresponding first one-way liquid outlet hole and a corresponding second one-way liquid outlet hole alternately pump water to a high-pressure output main pipe at a non-uniform speed to form pulse flow output, a flow sensor monitors a pulse flow output state, at the moment, fracturing liquid is continuously input in a fracturing pipe in a flow pulse mode, further pulse action is generated on a formed hydraulic crack, and the fracturing.
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