CN103437754B - Pressurization control method and pressurization control system for rotary drilling rig - Google Patents
Pressurization control method and pressurization control system for rotary drilling rig Download PDFInfo
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- CN103437754B CN103437754B CN201310368278.XA CN201310368278A CN103437754B CN 103437754 B CN103437754 B CN 103437754B CN 201310368278 A CN201310368278 A CN 201310368278A CN 103437754 B CN103437754 B CN 103437754B
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- 238000005553 drilling Methods 0.000 title claims abstract description 48
- 238000000034 method Methods 0.000 title claims abstract description 22
- 230000008569 process Effects 0.000 claims abstract description 9
- 239000002828 fuel tank Substances 0.000 claims description 12
- 239000000446 fuel Substances 0.000 claims description 10
- 230000001105 regulatory effect Effects 0.000 claims description 8
- 230000007246 mechanism Effects 0.000 abstract description 6
- 239000003921 oil Substances 0.000 description 157
- 239000010720 hydraulic oil Substances 0.000 description 6
- 238000010586 diagram Methods 0.000 description 5
- 238000000465 moulding Methods 0.000 description 5
- 238000003825 pressing Methods 0.000 description 4
- 230000035939 shock Effects 0.000 description 4
- 241001074085 Scophthalmus aquosus Species 0.000 description 3
- 230000001276 controlling effect Effects 0.000 description 3
- 239000011435 rock Substances 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 238000001514 detection method Methods 0.000 description 2
- 230000005611 electricity Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000012544 monitoring process Methods 0.000 description 2
- 210000003371 toe Anatomy 0.000 description 2
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000005336 cracking Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- KQTVWCSONPJJPE-UHFFFAOYSA-N etridiazole Chemical compound CCOC1=NC(C(Cl)(Cl)Cl)=NS1 KQTVWCSONPJJPE-UHFFFAOYSA-N 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000012163 sequencing technique Methods 0.000 description 1
- 239000002689 soil Substances 0.000 description 1
- 238000013517 stratification Methods 0.000 description 1
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Abstract
The invention discloses a pressurization control method and a pressurization control system for a rotary drilling rig, wherein the pressurization control method for the rotary drilling rig comprises the following steps: respectively acquiring pressure values of rodless cavities of a left mast oil cylinder (11) and a right mast oil cylinder (16) of the rotary drilling rig; the controller processes the pressure value of the rodless cavity of the left mast oil cylinder (11) and the pressure value of the rodless cavity of the right mast oil cylinder (16) to obtain the pressure difference value of the rodless cavities of the left mast oil cylinder (11) and the right mast oil cylinder (16); and controlling the pressure of the rodless cavity of the pressurizing oil cylinder (20) according to the relation between the preset pressure difference value and the pressure of the rodless cavity of the pressurizing oil cylinder (20). The invention can automatically adjust the pressure and the pressurizing speed of the pressurizing oil cylinder on the power head, reduce the unbalance loading of a drill rod, a mast and the like caused by the impact load and the unbalance loading of a drill bit, reduce the vibration frequency, and avoid the occurrence of personal and equipment safety accidents caused by the damage of a working mechanism and the falling of damaged parts at high altitude due to the factors of human judgment error or operation delay and the like.
Description
Technical field
The present invention relates to technical field of engineering machinery, particularly relate to rotary drilling rig pressure control method and pressurizing control system.
Background technology
Rotary drilling rig uses pile foundation equipment comparatively widely at present, refer to Fig. 1, its course of work is, drill bit 4 declines with drilling rod 1 and reaches job position bottom stake holes 2, fluid motor-driven drilling rod 1 rotates, drilling rod 1 is connected with drill bit 4 by connecting square toes, and drilling rod 1 drives the brill tooth 5 of drill bit 4 cut and creep into operation.In drilling condition, pressurization oil cylinder applies a certain size downward pressure to unit head, and the piston rod of pressurization oil cylinder stretches out and drives unit head, drilling rod, drill bit to move down.
The brill tooth 5 of drill bit 4 meets the following two kinds situation in cutting and drilling process: one, part cutting face A is soil layer, and another part cutting face B is rock; Two, part cutting face A is hollow, when another cut-in without ball bevel B is rock, refers to Fig. 2, is symmetrical along the drill bit cross section center of circle because boring tooth 5, when cutting in the cutting face of different geology (pan soil, rock), bores the component Fb of tooth 5 in level, vertical direction
1, Fb
2with Fa
1, Fa
2differ in size, drill bit 4 can produce serious unbalance loading.The size of unbalance loading and following factor about: one, the hardness of two kinds of geological stratifications, intensity differ larger, and the partial load suffered by drill bit 4 is larger; Two, the plus-pressure of pressurization oil cylinder is larger, and the partial load suffered by drill bit 4 is larger; Three, the rotary speed of drill bit 4 is faster, and the partial load suffered by drill bit 4 is larger.Drill bit 4 unbalance loading can produce vibration, and drilling bucket 3, drilling rod 1, unit head and arbitrary-movement articulator also can bear corresponding unbalance loading load and vibrate accordingly, damage corresponding structural member.Partial load is larger, the vibration frequency produced is higher, suffered by structural member, shock loading is larger, the square toes that drilling bucket 3 can be caused time serious to be connected with drilling rod 1 snap, even rupture, drill bit is caused " to be buried " or drop from high-altitude, meanwhile, cause mast guide rail to snap, be out of shape, arbitrary-movement articulator U-type groove cracking, distortion etc., main operating mechanism cannot normally work.
Summary of the invention
The technical problem to be solved in the present invention is to provide and a kind ofly prevents drill bit unbalance loading and damage the pressure control method of structural member.
Rotary drilling rig pressure control method provided by the invention, comprises the following steps:
Obtain the force value of the left mast oil cylinder of rotary drilling rig and the rodless cavity of right mast oil cylinder respectively;
The force value of controller to the force value of left mast oil cylinder rodless cavity and right mast oil cylinder rodless cavity processes, and obtains the pressure difference of the rodless cavity of left mast oil cylinder and right mast oil cylinder;
According to the relation between the pressure difference preset and the pressure of pressurization oil cylinder rodless cavity, control the pressure of pressurization oil cylinder rodless cavity.
Preferably, further comprising the steps of: according to preset pressure difference and be described rotary drilling rig power head motor fuel feeding variable pump between relation, control variables pump delivery.
The present invention also provides a kind of rotary drilling rig pressurizing control system, comprising left mast oil cylinder, right mast oil cylinder and pressurization oil cylinder, also comprising: checkout gear, for detecting the rodless cavity force value of left mast oil cylinder and right mast oil cylinder; Controller, left mast oil cylinder rodless cavity force value and right mast oil cylinder rodless cavity force value are processed, obtain the pressure difference of the rodless cavity of left mast oil cylinder and right mast oil cylinder, and according to the relation between the pressure difference preset and the pressure of pressurization oil cylinder rodless cavity, control the pressure of pressurization oil cylinder rodless cavity.
Preferably, described checkout gear comprises the first pressure sensor and the second pressure sensor that are connected with the rodless cavity of described left mast oil cylinder and right mast oil cylinder respectively.
Preferably, described first pressure sensor and the second pressure sensor are provided with alarm; When described pressure difference reaches setting value, described alarm equipment alarm.
Preferably, described system also comprises and being connected and the first control valve regulated the pressure of this rodless cavity with the rodless cavity of described pressurization oil cylinder, described first control valve comprises a control end be connected with described controller, and described controller is by the pressure of the rodless cavity of described first governor valve control pressurization oil cylinder.
Preferably, described first control valve is electric proportional pressure control valve, and described electric proportional pressure control valve comprises and the oil-in be communicated with of described pressurization oil cylinder rodless cavity, the oil-out be communicated with fuel tank and the control end that is electrically connected with described controller.
Preferably, described system also comprises power head motor, for the variable pump of power head motor fuel feeding, is connected and the second control valve regulated this variable pump delivery with described variable pump.
Preferably, described second control valve is the electric proportional pressure-reducing valve be connected with described variable pump, described variable pump comprises the adjustment oil circuit regulated its discharge capacity, the control end that described electric proportional pressure-reducing valve comprises the oil-in be connected with the oil-out of described variable pump, the oil-out be connected with described adjustment oil circuit and is connected with described controller.
Preferably, described variable pump comprises servo-cylinder and built-in reversal valve, the node C that described adjustment oil circuit comprises the node A be communicated with the oil-out of described variable pump, the Node B be connected with described electric proportional pressure-reducing valve and is communicated with the rodless cavity of described servo-cylinder, described built-in reversal valve comprises two hydraulic control ends, oil-in and oil return opening, oil-in and one of them hydraulic control end of described built-in reversal valve are connected with described node A, wherein another hydraulic control end is connected with described Node B, and its oil return opening is communicated with fuel tank.
Rotary drilling rig pressure control method provided by the invention can regulate pressurization oil cylinder to the applying pressure of unit head and pressing speed automatically, reduce the unbalance loading of the drilling rod, mast etc. caused because of the shock loading of drill bit and partial load, reduce vibration frequency, avoid because of factors such as artificial error in judgement or operation delay, cause operating mechanism to damage and the generation causing the person, device security accident because of part of damage falling from high altitude.
Accompanying drawing explanation
Fig. 1 is the drill bit construction operation schematic diagram of prior art;
Fig. 2 is the stressed schematic diagram of brill tooth in Fig. 1;
Fig. 3 is rotary drilling rig structural representation;
Fig. 4 is the left view of Fig. 3;
Fig. 5 is rotary drilling rig compression system schematic diagram of the present invention.
Symbol description
Detailed description of the invention
Below in conjunction with accompanying drawing, the specific embodiment of the present invention is described in detail.Should be understood that, detailed description of the invention described herein, only for instruction and explanation of the present invention, is not limited to the present invention.
In the present invention, when not doing contrary explanation, the noun of locality of use as " upper and lower " be for parts each under rotary drilling rig normal operating conditions between mutual alignment relationship description word.
Usually, rotary drilling rig comprises mast 10, left mast oil cylinder 11, right mast oil cylinder 16, drilling rod 50, controls the parts such as master winch (not shown), the arbitrary-movement articulator 30 be connected with drilling rod 50 and the unit head 40 that drilling rod 50 rises or decline, the pressurization oil cylinder 20 pressurizeed to unit head 40 and drill bit 60.The churning driven course of work refers to the course of work of the churning driven described in background technology, does not repeat them here.
Refer to Fig. 3 and Fig. 4, mast 10 can be made front, rear, left and right four directions within the specific limits around connection rotating disk 14 and rotate, and connecting rotating disk 14 within the specific limits can only transmitting force, and can not carry-over moment (moment of torsion or torque).One end of the piston rod of left mast oil cylinder 11, right mast oil cylinder 16 is connected with mast 10, and the other end is connected with jib lubbing mechanism assembly.When mast 10 does not deflect, left mast oil cylinder 11 is identical with the pressure of the rodless cavity of right mast oil cylinder 16, and pressure difference is between the two zero.Can not carry-over moment owing to connecting rotating disk 14, when the forward and backward torsion of mast 10 or left and right deflection, the wherein cylinder piston rod tension in right mast oil cylinder 16 and left mast oil cylinder 11 will be caused, and another cylinder piston rod pressurized; The rodless cavity pressure of the oil cylinder of piston rod tension reduces, and the rodless cavity pressure of the oil cylinder of piston rod pressurized raises, and finally causes the rodless cavity of right mast oil cylinder 16 and left mast oil cylinder 11 to produce new pressure difference.
The embodiment of the present invention discloses a kind of rotary drilling rig pressure control method, and the method comprises the following steps: the force value obtaining the left mast oil cylinder 11 of described rotary drilling rig and the rodless cavity of right mast oil cylinder 16 respectively; The force value of controller to the force value of the rodless cavity of left mast oil cylinder 11 and the rodless cavity of right mast oil cylinder 16 processes, and obtains the pressure difference of the rodless cavity of left mast oil cylinder 11 and right mast oil cylinder 16; According to the relation between the pressure of the rodless cavity of the pressure difference preset and pressurization oil cylinder 20, control the pressure of pressurization oil cylinder 20 rodless cavity.The invention enables can according to the pressure difference signal detected in the rodless cavity of left mast oil cylinder 11 and right mast oil cylinder 16, the applying pressure of automatic adjustment pressurization oil cylinder 20 pairs of unit heads 40 and pressing speed, reduce the unbalance loading of the drilling rod 50, mast 10 etc. caused because of the shock loading of drill bit 60 and partial load, reduce vibration frequency, avoid because of factors such as artificial error in judgement or operation delay, cause operating mechanism to damage and the generation causing the person, device security accident because of part of damage falling from high altitude.
It should be noted that, described pressure difference refers to the absolute value of the difference of the pressure of the rodless cavity of left mast oil cylinder 11 and right mast oil cylinder 16.
Pass between the pressure of the rodless cavity of described pressure difference and pressurization oil cylinder 20 is: described pressure difference becomes large, then the pressure of the rodless cavity of the oil cylinder 20 that pressurizes correspondingly diminishes, and described pressure difference diminishes, then the pressure of the rodless cavity of the oil cylinder 20 that pressurizes correspondingly becomes large.
Further, this pressure control method also comprise according to preset pressure difference and for power head motor 42 fuel feeding variable pump 44 discharge capacity between relation, the discharge capacity of control variables pump 44.The discharge capacity of variable pump 44 is relevant with the rotating speed of power head motor 42, and the rotating speed of power head motor 42 is relevant with the rotating speed of unit head 40, and the discharge capacity of variable pump 44 is larger, and unit head 40 rotating speed is larger, and correspondingly, the rotating speed of drill bit 60 is higher.Therefore, can control according to the discharge capacity of described pressure difference to variable pump 44, making can according to the pressure difference in the rodless cavity of left mast oil cylinder 11 and right mast oil cylinder 16, automatic adjustment drill bit 60 rotating speed, reduce shock loading and the partial load of drill bit 60, reduce vibration frequency, avoid because of factors such as artificial error in judgement or operation delay, cause operating mechanism to damage and the generation causing the person, device security accident because of part of damage falling from high altitude.
Described pressure difference and for power head motor 42 fuel feeding variable pump 44 discharge capacity between pass be: described pressure difference becomes greatly, and the discharge capacity of described variable pump 44 correspondingly diminishes, and described pressure difference diminishes, and the discharge capacity of described variable pump 44 correspondingly becomes large.
It should be noted that, controller according to preset pressure difference and pressurization oil cylinder 20 rodless cavity pressure between relation, control the step of the pressure of pressurization oil cylinder 20 rodless cavity and controller according to default pressure difference and be power head motor 42 fuel feeding variable pump 44 discharge capacity between relation, sequencing is not had between the step of the discharge capacity of control variables pump 44, namely, controller control can be first control to pressurize oil cylinder 20 rodless cavity pressure after the discharge capacity of control variables pump 44 again, also can be the pressure of rodless cavity and the discharge capacity of variable pump 44 that controller controls pressurization oil cylinder 20 simultaneously, can also be the pressure controlling the rodless cavity of pressurization oil cylinder 20 after controller controls to be the discharge capacity of first control variables pump 44 again.
The embodiment of the present invention also discloses a kind of rotary drilling rig pressurizing control system, this system comprises left mast oil cylinder 11, right mast oil cylinder 16 and pressurization oil cylinder 20, also comprise: checkout gear, for detecting the force value of the rodless cavity of left mast oil cylinder 11 and right mast oil cylinder 16; Controller, force value for the force value of the rodless cavity to left mast oil cylinder 11 and the rodless cavity of right mast oil cylinder 16 processes, obtain the pressure difference of the rodless cavity of left mast oil cylinder 11 and right mast oil cylinder 16, and according to the relation between the pressure difference preset and the pressure of pressurization oil cylinder 20 rodless cavity, control the pressure of pressurization oil cylinder 20 rodless cavity.The present invention detects the force value of the rodless cavity of left mast oil cylinder 11 and right mast oil cylinder 16 automatically by checkout gear, the force value of acquisition is carried out process and is obtained corresponding pressure difference by controller automatically, and the pressure of pressurization oil cylinder 20 rodless cavity is automatically controlled according to this pressure difference, the pressure process of pressurization oil cylinder 20 pairs of unit heads 40 is controlled automatically, reliability is high, automaticity is high, greatly reduces the labour intensity of equipment operator.
Pass between the pressure of the rodless cavity of described pressure difference and pressurization oil cylinder 20 is: described pressure difference becomes large, then the pressure of the rodless cavity of the oil cylinder 20 that pressurizes correspondingly diminishes, and described pressure difference diminishes, then the pressure of the rodless cavity of the oil cylinder 20 that pressurizes correspondingly becomes large.
Described checkout gear is for detecting the force value of the rodless cavity of left mast oil cylinder 11 and right mast oil cylinder 16, therefore, as long as described checkout gear has detected pressures and the force value of detection is sent to the function of controller, such as, can be but be not limited to the pressure sensor in the present embodiment.Particularly, described checkout gear comprises the first pressure sensor 12 and the second pressure sensor 17, and described first pressure sensor 12 is connected with the rodless cavity of described left mast oil cylinder 11, for detecting the force value of this rodless cavity in real time; Described second pressure sensor 17 is connected with the rodless cavity of described right mast oil cylinder 16, for detecting the force value of this rodless cavity in real time.The force value of detection is sent to controller by described first pressure sensor 12 and the second pressure sensor 17, in the present embodiment, the first pressure sensor 12 and the second pressure sensor 17 are also provided with alarm, when described pressure difference reaches setting value, alarm equipment alarm, alert.
In order to realize the Stress control of the rodless cavity to described pressurization oil cylinder 20, described pressurizing control system also comprises and being connected and the first control valve controlled the pressure of this rodless cavity with the rodless cavity of described pressurization oil cylinder 20, and described first control valve comprises a control end be connected with described controller, the oil revolving end be connected with fuel tank, the oil inlet end that is communicated with the in-line of described pressurization oil cylinder 20 rodless cavity.Described controller is according to the relation between the pressure difference preset and the pressure of pressurization oil cylinder 20 rodless cavity, send a control signal to the control end of described first control valve, described first control valve controls the pressure of the in-line of pressurization oil cylinder 20 rodless cavity according to this control signal.When described pressure difference is larger, the hydraulic oil increased on the in-line of the rodless cavity of pressurization oil cylinder 20 enters the flow of fuel tank by this first control valve, the pressure of the rodless cavity of pressurization oil cylinder 20 is reduced, in like manner, when described pressure difference is less, the hydraulic oil reduced on the in-line of the rodless cavity of pressurization oil cylinder 20 enters the flow of fuel tank by this first control valve, the pressure of the rodless cavity of pressurization oil cylinder 20 is increased.
Be understandable that, this the first control valve can be the valve of the arbitrary form with above-mentioned functions, such as, can be pile-up valve, overflow valve, in the present embodiment, described first control valve is electric proportional pressure control valve 24, the oil-in of described electric proportional pressure control valve 24 is connected with the in-line of the rodless cavity of described pressurization oil cylinder 20, the control end of described electric proportional pressure control valve 24 is electrically connected with described controller, this control end is the control end of the first control valve, and the oil-out of described electric proportional pressure control valve 24 is connected with fuel tank.Described controller is according to the relation between the pressure difference preset and the pressure of pressurization oil cylinder 20 rodless cavity, convert described pressure difference signal to control end that the signal of telecommunication is sent to described electric proportional pressure control valve 24, the spool aperture of described electric proportional pressure control valve 24 and the current in proportion of its control end, when described pressure difference is larger, spool aperture is large, hydraulic oil on the in-line of the rodless cavity of corresponding pressurization oil cylinder 20 is increased by the flow of this electric proportional pressure control valve 24 overflow to fuel tank, the pressure of the rodless cavity of pressurization oil cylinder 20 is reduced, cause pressurization oil cylinder 20 to unit head 40 so that the moulding pressure to drill bit 60 less, the speed of pressurization is also less downwards simultaneously, the vibration that unbalance loading produces is less.In like manner, when described pressure difference is less, spool aperture is little, hydraulic oil on the in-line of the rodless cavity of corresponding pressurization oil cylinder 20 is reduced by the flow of this electric proportional pressure control valve 24 overflow to fuel tank, make pressurize oil cylinder 20 rodless cavity pressure increase, cause pressurization oil cylinder 20 to unit head 40 so that the moulding pressure to drill bit 60 larger.
Affecting drill bit 60 unbalance loading and vibrative factor except pressurizeing except the moulding pressure of oil cylinder 20, also having the velocity of rotation of unit head 40.Therefore, described pressurizing control system also comprises power head motor 42, for the variable pump 44 of power head motor 42 fuel feeding, is connected and the second control valve controlled the discharge capacity of this variable pump 44 with described variable pump 44, and described variable pump 44 comprises the adjustment oil circuit 446 regulated its discharge capacity.Controller, according to the relation between the pressure difference preset and the discharge capacity of variable pump 44, regulates the discharge capacity of described variable pump 44.The discharge capacity of described variable pump 44 changes, the rotating speed of power head motor 42 is changed, also respective change can be there is in the rotating speed of unit head 40 and drill bit 60, control system of the present invention can be regulated the rotating speed of unit head 40 and drill bit 60 automatically according to the force value change of the rodless cavity of left mast oil cylinder 11 and right mast oil cylinder 16, reliability is high, automaticity is high, greatly reduces the labour intensity of equipment operator.
Described pressure difference and for power head motor 42 fuel feeding variable pump 44 discharge capacity between pass be: described pressure difference becomes greatly, and the discharge capacity of described variable pump 44 correspondingly diminishes, and described pressure difference diminishes, and the discharge capacity of described variable pump 44 correspondingly becomes large.
Be understandable that, this the second control valve can be the valve of the arbitrary form with above-mentioned functions, such as, can be pile-up valve, overflow valve, reducing valve, in the present embodiment, described second control valve is preferably electric proportional pressure-reducing valve 46, and the control end that electric proportional pressure-reducing valve 46 comprises the oil-in be connected with the oil-out of described variable pump 44, the oil-out be connected with the adjustment oil circuit 446 of described variable pump 44 and is connected with described controller, this control end is the control end of described second control valve.
Refer to Fig. 5, Fig. 5 is the hydraulic schematic diagram of the embodiment of the present invention, now in conjunction with this hydraulic schematic diagram, is described in detail the course of work of the present invention.Described pressurizing control system also comprises for described pressurization oil cylinder 20, the hydraulic pump 26 of left mast oil cylinder 11 and right mast oil cylinder 16 fuel feeding, and be separately positioned on described hydraulic pump 26 and pressurization oil cylinder 20, reversal valve 25 between left mast oil cylinder 11 and right mast oil cylinder 16, namely, on oil circuit between described pressurization oil cylinder 20 and hydraulic pump 26, oil circuit on oil circuit between left mast oil cylinder 11 and hydraulic pump 26 and between right mast oil cylinder 16 and hydraulic pump 26 is provided with reversal valve 25, the hydraulic oil that hydraulic pump 26 exports by described reversal valve 25 is optionally connected to rod chamber or the rodless cavity of corresponding oil cylinder.Further, the oil circuit between the rod chamber of described pressurization oil cylinder 20 and corresponding reversal valve 25 is provided with the first equalizing valve 22, described first equalizing valve 22 comprises the control port be connected with the rodless cavity of described pressurization oil cylinder 20; The rod chamber of described left mast oil cylinder 11 and the oil circuit between rodless cavity and corresponding reversal valve 25 are provided with the second equalizing valve 13, and two second equalizing valves 13 have interlock function; The rod chamber of described right mast oil cylinder 16 and the oil circuit between rodless cavity and corresponding reversal valve 25 are provided with the 3rd equalizing valve 18, and two second equalizing valves 13 have interlock function.
Described first pressure sensor 12 is connected on the oil circuit between the rodless cavity of described left mast oil cylinder 11 and the second equalizing valve 13, and for the force value of the rodless cavity of mast oil cylinder 11 left described in Real-Time Monitoring, and this force value is sent to controller.Described second pressure sensor 17 is connected on the oil circuit between the rodless cavity of described right mast oil cylinder 16 and the 3rd equalizing valve 18, and for the force value of the rodless cavity of mast oil cylinder 16 right described in Real-Time Monitoring, and this force value is sent to controller.
The oil-in of described electric proportional pressure control valve 24 is connected on the oil circuit between the rodless cavity of described pressurization oil cylinder 20 and the first equalizing valve 22, and its oil-out is connected to fuel tank, and its control end is connected to controller.When controller obtain described left mast oil cylinder 11 and right mast oil cylinder 16 rodless cavity pressure difference become large time, illustrate that drill bit 60 creates unbalance loading load, controller converts this pressure difference to current value, and this current value is sent to the control end of electric proportional pressure control valve 24, the spool aperture of electricity proportional pressure control valve 24 becomes large, the pressure pressurizeed in oil cylinder 20 rodless cavity is reduced, and then reduces the moulding pressure of pressurization oil cylinder 20 pairs of unit heads 40, so that the vibration that reduction drill bit 60 brings because of unbalance loading load.In like manner, when the pressure difference of rodless cavity of the described left mast oil cylinder 11 that controller obtains and right mast oil cylinder 16 diminishes, illustrate that drill bit 60 unbalance loading load is less, the spool aperture of electricity proportional pressure control valve 24 diminishes, the pressure pressurizeed in oil cylinder 20 rodless cavity is increased, thus suitably increase the moulding pressure of pressurization oil cylinder 20 pairs of unit heads 40, drill bit 60 can carry out creeping into operation under rational pressure.
Further, oil circuit between described variable pump 44 and described power head motor 42 is provided with selector valve 43, the hydraulic oil that variable pump 44 exports by described selector valve 43 is optionally connected to the opposite end of power head motor 42, makes power head motor 42 forward or reverse.The oil-in of described electric proportional pressure-reducing valve 46 is connected on the oil circuit between the oil-out of described variable pump 44 and described selector valve 43, and the oil-out of described electric proportional pressure-reducing valve 46 is connected on described adjustment oil circuit 446.Particularly, described variable pump 44 comprises built-in swash plate servo-cylinder 440 and built-in reversal valve 442, the node C that described adjustment oil circuit 446 comprises the node A be communicated with the oil-out of described variable pump 44, the Node B be connected with described electric proportional pressure-reducing valve 46 and is communicated with the rodless cavity of described servo-cylinder 440.Described built-in reversal valve 442 comprises two hydraulic control ends, oil-in and oil return opening, oil-in and one of them hydraulic control end of described built-in reversal valve 442 are connected with described node A, wherein another hydraulic control end is connected with described Node B, its oil return opening is communicated with fuel tank, the hydraulic control end be connected with described Node B is provided with spring, described Node B and spring force are to the aperture of the pressure of this hydraulic control end and the built-in reversal valve 442 of the pressure co-controlling of node A to another hydraulic control end, and then control the pressure being entered described node C by node A, namely the pressure entering the rodless cavity of servo-cylinder 440 is controlled, and then reach the object of discharge capacity of control variables pump 44.In said process, controller is according to the relation between the pressure difference preset and the discharge capacity of variable pump 44, convert described pressure difference signal to control end that the signal of telecommunication is sent to described electric proportional pressure-reducing valve 46, control end controls the aperture of this electric proportional pressure-reducing valve 46, and then the pressure of Controlling vertex B, reach the object of the aperture controlling built-in reversal valve 442.
Below a preferred embodiment of the present invention is described in detail by reference to the accompanying drawings, but, be not limited to the detail in above-mentioned embodiment.Within the scope of technical conceive of the present invention, can carry out multiple simple variant to technical scheme of the present invention, these simple variant all belong to protection scope of the present invention.
Claims (10)
1. rotary drilling rig pressure control method, is characterized in that, comprises the following steps:
Obtain the force value of the left mast oil cylinder (11) of described rotary drilling rig and the rodless cavity of right mast oil cylinder (16) respectively;
Controller processes the force value of the rodless cavity of described left mast oil cylinder (11) and the force value of right mast oil cylinder (16) rodless cavity, obtains the pressure difference of the rodless cavity of left mast oil cylinder (11) and right mast oil cylinder (16);
According to the relation between the pressure of the rodless cavity of the pressure difference preset and pressurization oil cylinder (20), control the pressure of oil cylinder (20) rodless cavity of pressurizeing.
2. rotary drilling rig pressure control method as claimed in claim 1, it is characterized in that, further comprising the steps of: according to preset pressure difference and be described rotary drilling rig power head motor (42) fuel feeding variable pump (44) discharge capacity between relation, the discharge capacity of control variables pump (44).
3. rotary drilling rig pressurizing control system, comprise left mast oil cylinder (11), right mast oil cylinder (16) and pressurization oil cylinder (20), it is characterized in that, described rotary drilling rig pressurizing control system also comprises: checkout gear, for detecting the force value of the rodless cavity of left mast oil cylinder (11) and right mast oil cylinder (16); Controller, the force value of the force value of the rodless cavity of left mast oil cylinder (11) and the rodless cavity of right mast oil cylinder (16) is processed, obtain the pressure difference of the rodless cavity of left mast oil cylinder (11) and right mast oil cylinder (16), and according to the relation between the pressure difference preset and the pressure of pressurization oil cylinder (20) rodless cavity, control the pressure of the rodless cavity of pressurization oil cylinder (20).
4. rotary drilling rig pressurizing control system as claimed in claim 3, it is characterized in that, described checkout gear comprises the first pressure sensor (12) and the second pressure sensor (17) that are connected with the rodless cavity of described left mast oil cylinder (11) and right mast oil cylinder (16) respectively.
5. rotary drilling rig pressurizing control system as claimed in claim 4, is characterized in that, described first pressure sensor (12) and the second pressure sensor (17) are provided with alarm; When described pressure difference reaches setting value, described alarm equipment alarm.
6. rotary drilling rig pressurizing control system as claimed in claim 4, it is characterized in that, described system also comprises and being connected and the first control valve regulated the pressure of this rodless cavity with the rodless cavity of described pressurization oil cylinder (20), described first control valve comprises a control end be connected with described controller, and described controller is by the pressure of the rodless cavity of described first governor valve control pressurization oil cylinder.
7. rotary drilling rig pressurizing control system as claimed in claim 6, it is characterized in that, described first control valve is electric proportional pressure control valve (24), and described electric proportional pressure control valve (24) comprises and the oil-in be communicated with of described pressurization oil cylinder (20) rodless cavity, the oil-out be communicated with fuel tank and the control end be electrically connected with described controller.
8. rotary drilling rig pressurizing control system as claimed in claim 3, it is characterized in that, described system also comprises power head motor (42), for the variable pump (44) of power head motor (42) fuel feeding, is connected and the second control valve regulated the discharge capacity of this variable pump (44) with described variable pump (44).
9. rotary drilling rig pressurizing control system as claimed in claim 8, it is characterized in that, described second control valve is the electric proportional pressure-reducing valve (46) be connected with described variable pump (44), described variable pump (44) comprises the adjustment oil circuit (446) regulated its discharge capacity, the control end that described electric proportional pressure-reducing valve (46) comprises the oil-in be connected with the oil-out of described variable pump (44), the oil-out be connected with described adjustment oil circuit (446) and is connected with described controller.
10. rotary drilling rig pressurizing control system as claimed in claim 9, it is characterized in that, described variable pump (44) comprises servo-cylinder (440) and built-in reversal valve (442), described adjustment oil circuit (446) comprises the node A be communicated with the oil-out of described variable pump (44), the Node B be connected with described electric proportional pressure-reducing valve (46), and the node C to be communicated with the rodless cavity of described servo-cylinder (440), described built-in reversal valve (442) comprises two hydraulic control ends, oil-in and oil return opening, oil-in and one of them hydraulic control end of described built-in reversal valve (442) are connected with described node A, wherein another hydraulic control end is connected with described Node B, its oil return opening is communicated with fuel tank.
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| CN104595273B (en) * | 2015-01-14 | 2017-03-01 | 柳州柳工挖掘机有限公司 | Engineering machinery refinement hydraulic system |
| CN106351900B (en) * | 2016-09-27 | 2018-12-18 | 桂林航天工业学院 | A kind of anti-deflection rock drilling control system |
| CN108868739A (en) * | 2018-07-16 | 2018-11-23 | 高邮市恒辉机械有限公司 | A kind of rotary digging driller mast control device |
| CN112065359B (en) * | 2020-09-21 | 2023-05-16 | 北京三一智造科技有限公司 | Drilling control method and rotary drilling rig |
| CN112727435B (en) * | 2020-12-31 | 2023-09-01 | 恒天九五重工有限公司 | Intelligent rock entering control device and method for rotary drilling rig |
| CN114526274A (en) * | 2022-01-18 | 2022-05-24 | 北京三一智造科技有限公司 | Control method of rotary drilling rig, hydraulic system and rotary drilling rig |
| CN115875009B (en) * | 2023-02-06 | 2023-06-20 | 中建隧道装备制造有限公司 | Advanced drilling machine control method for hard rock drilling |
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