CN115559953B - Drill rod-blocking-preventing hydraulic oil circuit structure of rock drill and hydraulic control method - Google Patents
Drill rod-blocking-preventing hydraulic oil circuit structure of rock drill and hydraulic control method Download PDFInfo
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- CN115559953B CN115559953B CN202211284096.XA CN202211284096A CN115559953B CN 115559953 B CN115559953 B CN 115559953B CN 202211284096 A CN202211284096 A CN 202211284096A CN 115559953 B CN115559953 B CN 115559953B
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- 239000011435 rock Substances 0.000 title claims abstract description 67
- 238000000034 method Methods 0.000 title claims abstract description 40
- 239000010720 hydraulic oil Substances 0.000 title claims abstract description 14
- 239000003921 oil Substances 0.000 claims abstract description 127
- 238000005553 drilling Methods 0.000 claims description 22
- 230000008859 change Effects 0.000 claims description 10
- 230000002265 prevention Effects 0.000 claims description 10
- 238000011010 flushing procedure Methods 0.000 claims description 3
- 230000009471 action Effects 0.000 abstract description 25
- 230000000694 effects Effects 0.000 abstract description 2
- 230000004044 response Effects 0.000 abstract description 2
- 230000000903 blocking effect Effects 0.000 abstract 2
- 238000010009 beating Methods 0.000 abstract 1
- 230000001105 regulatory effect Effects 0.000 description 11
- 230000008569 process Effects 0.000 description 8
- 230000002159 abnormal effect Effects 0.000 description 4
- 238000005520 cutting process Methods 0.000 description 4
- 230000001276 controlling effect Effects 0.000 description 3
- 238000004080 punching Methods 0.000 description 3
- 239000002893 slag Substances 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007123 defense Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
Classifications
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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
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
- F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
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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
- E21B1/00—Percussion drilling
- E21B1/02—Surface drives for drop hammers or percussion drilling, e.g. with a cable
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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
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
-
- 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
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/16—Special measures for feedback, e.g. by a follow-up device
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/505—Pressure control characterised by the type of pressure control means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/78—Control of multiple output members
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Life Sciences & Earth Sciences (AREA)
- Geology (AREA)
- Mining & Mineral Resources (AREA)
- Environmental & Geological Engineering (AREA)
- General Life Sciences & Earth Sciences (AREA)
- Geochemistry & Mineralogy (AREA)
- Earth Drilling (AREA)
Abstract
The invention provides a hydraulic oil way structure of a rock drill for preventing drill bits from being blocked and a hydraulic control method, belongs to the technical field of tunnel engineering equipment, and solves the problem that the conventional rock drill control method still has the drill bits due to electrical control; the hydraulic control system comprises a propulsion control oil circuit for connecting a pump and a propulsion oil cylinder, an impact control oil circuit for connecting the pump and the impact oil cylinder, a rotation control oil circuit for connecting the pump and a rotation motor, a propulsion control valve group and an anti-seizing valve group which are arranged on the propulsion control oil circuit, and an impact control valve group and an anti-idle-beating valve group which are arranged on the impact control oil circuit; the propulsion control oil circuit is also connected with the idle-run-preventing valve group through a first hydraulic feedback oil circuit, the impact control oil circuit is also connected with the propulsion control valve group through a second hydraulic feedback oil circuit, and the rotation control oil circuit is also connected with the drill rod blocking preventing valve group through a third hydraulic feedback oil circuit; the hydraulic valve is directly fed back to various action valves by a hydraulic method, and the hydraulic valve has the effects of preventing drill rod blocking and quick response in the aspect of key hydraulic action time sequence coordination of the rock drill.
Description
Technical Field
The invention belongs to the technical field of tunnel engineering equipment, and is applied to rock drill equipment, in particular to a rock drill hydraulic oil way structure capable of preventing drill rod from being blocked and a hydraulic control method.
Background
In the using process of the rock drill, the moving process of the rock drill relates to various control modes such as waterway control, gas circuit control, lubrication control, hydraulic control and the like; the hydraulic control is used for enabling the rock drill to make various hydraulic actions, including a propelling action, a rotating action and an impact action, wherein the propelling action is divided into forward and backward movements, the rotating action is divided into forward rotation and reverse rotation, and the impact action is divided into high-pressure impact and low-pressure impact; in order to realize the mutual coordination and time sequence control between the hydraulic actions, the adaptability requirements of the rock drill to different rock strata are met, the phenomenon of drill rod clamping is avoided, and therefore the hydraulic actions are required to be accurately controlled.
The existing control method is a pressure sensing type electric control method, namely, the pressure sensor is used for detecting the corresponding pipeline pressure of each hydraulic movement, and after the program comparison and calculation, an electric control signal is output to control the corresponding electromagnetic valve to act, so that the corresponding hydraulic action is realized; meanwhile, the hydraulic actions are closely matched, for example, when the rock drill performs high-pressure impact, the forward pushing action and the forward rotating action are simultaneously performed, so that normal cutting operation can be performed.
In the normal cutting operation process, if the drill bit enters a crack, the resistance to rotation of the drill bit is suddenly increased and exceeds the maximum rotation moment provided by the system; at this time, the drill rod should be quickly retracted, and the drill rod is pushed in again after being pulled out, so that the crack can be avoided, and if the retraction is not quick, the drill rod is very likely to be blocked and can not be pulled out; in the prior art, when the drill bit is about to enter the crack, the rotary pressure is suddenly increased, and the rotary pressure value reaches P after test max When the bit is stuck, the following control logic is set: the pressure sensor detects the rotation pressure when the pressure value reaches P max -4 (MPa) at which the propulsion solenoid valve is switched off, stopping propulsion; when the pressure continues to increase, the pressure value reaches P max -2 (MPa), the propulsion solenoid valve is powered reversely, and the propulsion action is performed to retreat; therefore, the prior art avoids the revolving pressure reaching P by extracting the sensing pressure max Thereby avoiding the phenomenon that the drill bit enters the crack to be blocked.
However, the control method of the prior art has certain disadvantages as follows:
1. because the pressure feedback, the program calculation, the electric output, the electromagnetic valve action and the pipeline pressure change of the sensor all need a certain time; even if the time course is short, it is uncertain whether the variation value of the actual pressure in the time period is preset to 2 or 4 (MPa); the electromagnetic sensor type control method needs to accumulate a large amount of working condition data, calculates effective control logic according to the working condition data, further tests working conditions, has long period, is difficult to accurately control, and is difficult to consider various working conditions, particularly the condition of abrupt change of the working conditions;
2. if the working condition is suddenly changed, such as the stratum suddenly hardens, the pressure change value contains a pressure peak value which is more than 2 or 4 (MPa), so that P is instantaneously reached max The value is difficult to immediately respond to the program, so that misoperation of equipment is caused, the phenomenon of drill rod clamping is caused, and the engineering progress is influenced;
3. the electric control of the sensor is easy to be influenced by the cutting environment, and the high temperature, the loose plug, the broken cable due to falling rocks, the data disorder and other consequences caused by the cutting environment can all happen, so that the hydraulic misoperation is caused, and the reliability of the existing control method is poor.
Disclosure of Invention
According to the invention, the hydraulic method is used for directly feeding back to various action valves, so that the effect of preventing the drill rod is generated in the aspect of the key hydraulic action time sequence coordination of the rock drill; under different working conditions, the invention has wider adaptability, quick response and reliable action, so that the stability and reliability of the rock drilling operation of the rock drill are extremely high.
The invention adopts the following technical scheme to achieve the purpose:
a hydraulic oil circuit structure of a rock drill for preventing drill sticking comprises a propulsion control oil circuit for connecting a pump and a propulsion oil cylinder, an impact control oil circuit for connecting the pump and the impact oil cylinder, and a rotation control oil circuit for connecting the pump and a rotation motor;
the propulsion control oil way is provided with a propulsion control valve group and an anti-seize valve group;
the impact control oil circuit is provided with an impact control valve group and an air-break prevention valve group;
the propulsion control oil way is also connected to the air-break prevention valve group through a first hydraulic feedback oil way;
the impact control oil path is also connected to the propulsion control valve group through a second hydraulic feedback oil path;
the rotation control oil path is also connected to the anti-seize valve bank through a third hydraulic feedback oil path;
the propulsion control valve group is used for switching the working state of the propulsion oil cylinder, and the impact control valve group is used for switching the working state of the impact oil cylinder;
the idle-beating-prevention valve group is used for receiving feedback of rock drilling propelling pressure and changing the working state of the impact oil cylinder;
the anti-seize drill valve group is used for receiving feedback of drill bit rotation pressure and changing the working state of the propulsion oil cylinder.
Further, the propulsion control valve group comprises a first hydraulic reversing valve, a first mechanical overflow valve and a first electromagnetic proportional overflow valve, wherein the first hydraulic reversing valve is used for receiving impact pressure fed back by the second hydraulic feedback oil way;
the impact control valve group comprises a first electromagnetic reversing valve, a second mechanical overflow valve and a second electromagnetic proportional overflow valve;
the air-break prevention valve group comprises a second hydraulic reversing valve, a third mechanical overflow valve and a fourth mechanical overflow valve, wherein the second hydraulic reversing valve is used for receiving the propelling pressure fed back by the first hydraulic feedback oil way;
the anti-seize valve bank comprises a third hydraulic reversing valve, a fourth hydraulic reversing valve and a one-way valve, wherein the third hydraulic reversing valve and the fourth hydraulic reversing valve are used for receiving the rotary pressure fed back by a third hydraulic feedback oil way, and the one-way valve is used for ensuring that the propulsion cylinder normally retreats when the working condition of the third hydraulic reversing valve is open.
Preferably, the air-break prevention valve group further comprises a second electromagnetic directional valve; the second electromagnetic directional valve is used for independently controlling the high-pressure impact state during low-pressure propulsion to shake the drill rod, and can shake loose and replace the clamped drill rod.
Furthermore, adjustable pressure springs are arranged in the third hydraulic reversing valve and the fourth hydraulic reversing valve, and the adjustable pressure springs are used for enabling the third hydraulic reversing valve and the fourth hydraulic reversing valve to act according to the rotating pressure fed back by the third hydraulic feedback oil way so as to change the working state of the thrust cylinder.
Optionally, the anti-seize valve group further comprises a fifth mechanical overflow valve and a sixth mechanical overflow valve, wherein the fifth mechanical overflow valve and the sixth mechanical overflow valve are used for changing the working state of the thrust cylinder according to the rotation pressure received and conducted by the third hydraulic reversing valve and the fourth hydraulic reversing valve.
The invention also provides a hydraulic control method of the rock drill for preventing the drill from being blocked according to the hydraulic oil circuit structure of the rock drill for preventing the drill from being blocked, which comprises the following steps:
s1, when drilling, starting a thrust cylinder to be in a forward state, and enabling a drill rod to be bound to a rock stratum;
s2, starting an impact oil cylinder and a rotary motor to enable the drill rod to rotate and conduct low-pressure impact hole opening on the rock stratum;
s3, enabling the first hydraulic reversing valve to be in a normal position, and performing low-flushing low-pushing propulsion to enable the drill rod to slowly enter a rock stratum;
s4, after the drill rod enters the rock stratum for a certain distance, the first electromagnetic directional valve is electrified, and high-pressure impact is carried out on the rock stratum;
s5, when high pressure impacts, the threshold value of the first hydraulic reversing valve is set, so that the feedback pressure value of the second hydraulic feedback oil way is higher than the threshold value, the first hydraulic reversing valve is closed, and the propulsion oil cylinder is in a high-impact high-propulsion state.
Preferably, when the propelling pressure is lower than the set pressure of the fourth mechanical overflow valve, the second hydraulic reversing valve is in a normal position, the impact pressure is the set pressure of the third mechanical overflow valve, and the impact oil cylinder is in a low-impact state;
when the propelling pressure is higher than the set pressure of the fourth mechanical overflow valve, the second hydraulic reversing valve is in a disconnected position, so that the first electromagnetic reversing valve and the second electromagnetic proportional overflow valve are electrified, and the impact oil cylinder is in a high-impact state;
when the first electromagnetic directional valve, the second electromagnetic directional valve and the second electromagnetic proportional overflow valve are powered on, the impact oil cylinder is in a high-impact state and a vibration drill rod state even if the propelling pressure is lower than the set pressure of the fourth mechanical overflow valve.
Further, in the conventional rock drilling working state, the second hydraulic reversing valve is closed, and the idle-beating-preventing valve group does not act; when the second hydraulic reversing valve senses that the propelling pressure value is rapidly reduced through the first hydraulic feedback oil circuit, the second hydraulic reversing valve is switched from a closed state to an open state, the fourth mechanical overflow valve acts, and the impact pressure is reduced.
Further, in the conventional rock drilling working state, if the rotation pressure is increased due to sudden abnormal working conditions, the rotation pressure is fed back to the anti-seize valve bank in real time through a third hydraulic feedback oil circuit, and when the rotation pressure rises to the spring pressure value of the third hydraulic reversing valve, the advancing speed of the pushing oil cylinder is slowed until the pushing oil cylinder is finally stopped; when the rotation pressure rises to the spring pressure value of the fourth hydraulic reversing valve, the thrust cylinder enters a retreating state, and the two states can be mutually switched at any time along with the change of the rotation pressure.
Optionally, the rotation pressure is fed back to the anti-seize valve group in real time through a third hydraulic feedback oil way, the rotation pressure is conducted to a fifth mechanical overflow valve and a sixth mechanical overflow valve through a third hydraulic reversing valve and a fourth hydraulic reversing valve, and when the rotation pressure rises to a set threshold value of the fifth mechanical overflow valve, the advancing speed of the pushing oil cylinder is slowed until the pushing oil cylinder is finally stopped; when the rotation pressure rises to the set threshold value of the sixth mechanical relief valve, the thrust cylinder enters a retreating state, and the two states are mutually switched at any time along with the change of the rotation pressure.
In summary, by adopting the technical scheme, the invention has the following beneficial effects:
compared with the method of electric control adopted in the prior art when the phenomenon of preventing the occurrence of the drill clamping phenomenon is faced, the hydraulic method is innovatively adopted to solve the problem; according to the hydraulic control method, in the aspect of key hydraulic action time sequence matching of the rock drill, through the redesigned hydraulic control oil way and hydraulic feedback oil way, the hydraulic pressure is directly fed back to the corresponding valve action by adopting a hydraulic control method, so that the drill is prevented from being blocked, and meanwhile, the control operation of normal production is more convenient; therefore, compared with electromagnetic drive control, the invention has the advantages that under the common control of a plurality of hydraulic feedback oil ways, the action of the rock drill is reliable and stable, meanwhile, the mechanical efficiency is high, the invention can adapt to the severe environment of the rock drilling site, the unnecessary power loss such as heating in an electric control mode is avoided, and the economic value brought by practical application is high.
Drawings
Fig. 1 is a schematic diagram of structural connection of a hydraulic circuit of a rock drill according to the present invention;
fig. 2 is a schematic diagram showing another structural connection of the hydraulic circuit of the rock drill according to the present invention.
The meaning of the symbols in the drawings is as follows:
the hydraulic control system comprises a 1-propulsion control valve bank, a 11-first hydraulic reversing valve, a 12-first mechanical overflow valve, a 13-first electromagnetic proportional overflow valve, a 2-impact control valve bank, a 21-first electromagnetic reversing valve, a 22-second mechanical overflow valve, a 23-second electromagnetic proportional overflow valve, a 3-air-break valve bank, a 31-second hydraulic reversing valve, a 32-third mechanical overflow valve, a 33-fourth mechanical overflow valve, a 4-anti-seize valve bank, a 41-third hydraulic reversing valve, a 42-fourth hydraulic reversing valve, a 43-check valve, a 44-orifice, a 45-fifth mechanical overflow valve, a 46-sixth mechanical overflow valve, a 5-pump, a 61-first hydraulic feedback oil path, a 62-second hydraulic feedback oil path, a 63-third hydraulic feedback oil path, a 71-propulsion oil cylinder, a 72-impact oil cylinder, a 73-rotary motor and an 8-electric proportional multi-way valve.
Detailed Description
For the purpose of making the objects, technical solutions and advantages of the embodiments of the present invention more apparent, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention, and it is apparent that the described embodiments are some embodiments of the present invention, but not all embodiments of the present invention. The components of the embodiments of the present invention generally described and illustrated in the figures herein may be arranged and designed in a wide variety of different configurations.
Thus, the following detailed description of the embodiments of the invention, as presented in the figures, is not intended to limit the scope of the invention, as claimed, but is merely representative of selected embodiments of the invention. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
Example 1
As shown in fig. 1 or 2, a hydraulic oil path structure of a rock drill for preventing seizing includes a propulsion control oil path connecting a pump 5 and a propulsion cylinder 71, an impact control oil path connecting the pump 5 and an impact cylinder 72, and a rotation control oil path connecting the pump 5 and a rotation motor 73; the propulsion control oil path, the impact control oil path and the rotation control oil path are all provided with electric proportional multi-way valves 8, which are used for common control of the propulsion oil cylinder 71, the impact oil cylinder 72 and the rotation motor 73, such as start-stop operation and the like, and serve as basic control devices.
The propulsion control oil path is provided with a propulsion control valve group 1 and an anti-seize valve group 4;
an impact control valve group 2 and an air-defense valve group 3 are arranged on the impact control oil path;
the propulsion control oil way is also connected to the air-break prevention valve group 3 through a first hydraulic feedback oil way 61;
the impact control oil path is also connected to the propulsion control valve group 1 through a second hydraulic feedback oil path 62;
the rotation control oil path is also connected to the anti-seize valve group 4 through a third hydraulic feedback oil path 63;
the propulsion control valve group 1 is used for switching the working state of the propulsion oil cylinder 71, and the impact control valve group 2 is used for switching the working state of the impact oil cylinder 72;
the air-break valve group 3 is used for receiving feedback of rock drilling propelling pressure and changing the working state of the impact oil cylinder 72;
the anti-seize valve group 4 is used for receiving feedback of the rotation pressure of the drill bit and changing the working state of the propulsion cylinder 71.
Wherein, the working state of the propulsion cylinder 71 comprises forward and backward, and the propulsion pressure comprises low-pressure propulsion and high-pressure propulsion; the operating states of the impact cylinder 72 include low pressure impact and high pressure impact; the operating state of the rotation motor 73 includes forward rotation and reverse rotation.
In this embodiment, the specific settings of each functional valve group are as follows:
the propulsion control valve group 1 comprises a first hydraulic reversing valve 11, a first mechanical overflow valve 12 and a first electromagnetic proportional overflow valve 13, wherein the first hydraulic reversing valve 11 is used for receiving impact pressure fed back by a second hydraulic feedback oil way 62;
the impact control valve group 2 comprises a first electromagnetic directional valve 21, a second mechanical overflow valve 22 and a second electromagnetic proportional overflow valve 23;
the air-break prevention valve group 3 comprises a second hydraulic reversing valve 31, a third mechanical overflow valve 32 and a fourth mechanical overflow valve 33, wherein the second hydraulic reversing valve 31 is used for receiving the propelling pressure fed back by the first hydraulic feedback oil way 61;
the anti-seize valve bank 4 comprises a third hydraulic reversing valve 41, a fourth hydraulic reversing valve 42 and a one-way valve 43, wherein the third hydraulic reversing valve 41 and the fourth hydraulic reversing valve 42 are used for receiving the rotating pressure fed back by a third hydraulic feedback oil circuit 63, and the one-way valve 43 is used for ensuring that the propulsion cylinder normally retreats when the working condition of the third hydraulic reversing valve 41 is open.
In the propulsion control valve group 1, the first mechanical relief valve 12 is used for controlling the low-pressure propulsion pressure of the propulsion oil cylinder 71, and the first electromagnetic proportional relief valve 13 is used for controlling the high-pressure propulsion pressure of the propulsion oil cylinder 71;
in the above-described impact control valve group 2, the low pressure impact state of the impact cylinder 72 is controlled by the second mechanical relief valve 22; the pressure in the high-pressure impact state is controlled by the second electromagnetic proportional relief valve 23.
In this embodiment, as a convenient arrangement in actual use, a second electromagnetic directional valve (not shown in the figure) controlled manually or by a program may be additionally provided at the air-break preventing valve group 3; the second electromagnetic directional valve is used for singly switching the impact oil cylinder 72 to be in a high-pressure impact state during low-pressure propulsion so as to shake the drill rod, and the clamped drill rod can be shaken loose and replaced; since the impact cylinder 72 is in a low pressure impact state in the conventional low pressure propulsion state, the second electromagnetic directional valve is implemented as a manual switch on the oil path structure.
In this embodiment, as shown in fig. 1, specifically, an adjustable pressure spring is disposed inside the third hydraulic reversing valve 41 and the fourth hydraulic reversing valve 42, and the adjustable pressure spring is used to make the third hydraulic reversing valve 41 and the fourth hydraulic reversing valve 42 act according to the rotation pressure fed back by the third hydraulic feedback oil path 63, so as to change the working state of the thrust cylinder 71.
Currently, the diameters of the rotary rods used for the rock drill in China can be divided into phi 45, phi 51, phi 76, phi 89 and phi 102, and the third hydraulic reversing valve 41 and the fourth hydraulic reversing valve 42 used in the embodiment are respectively used for changing the working state of the propulsion cylinder 71 into a state of stopping propulsion and reversing propulsion, namely stopping the propulsion and reversing when the fed-back rotation pressure reaches a set value; therefore, the embodiment provides a specific adjustable pressure spring set value (the set value is affected by various factors such as a specific rock layer, a drill bit style, smooth slag discharge, a rotation speed, a pushing speed, etc., and is not necessarily set according to the following pressure value, the following set value is only used as a reference), as follows:
for the rotating rods with diameter phi 45 and diameter phi 51, the spring pressure value of the third hydraulic reversing valve is adjusted to 6MPa, and the spring pressure value of the fourth hydraulic reversing valve is adjusted to 8MPa;
for the rotating rods with diameters phi 76 and phi 89, the spring pressure value of the third hydraulic reversing valve is regulated to 7MPa, and the spring pressure value of the fourth hydraulic reversing valve is regulated to 9MPa;
for the rotating rod with diameter phi 102, the spring pressure value of the third hydraulic reversing valve is regulated to 8MPa, and the spring pressure value of the fourth hydraulic reversing valve is regulated to 9MPa.
The spring pressures of the third hydraulic reversing valve 41 and the fourth hydraulic reversing valve 42 are directly regulated to be set, and the hydraulic reversing valve has the characteristic of simple regulation in the practical application process; the maximum regulating pressure of the valve is 10.5MPa, and the regulating pressure of each circle of the regulating screw is 2.1MPa (the regulating range of the valve is 5 circles), so that the regulating pressure can be more accurately regulated; through the control of the hydraulic load feedback oil circuit, different working condition requirements can be better met in time, the action of the hydraulic load feedback oil circuit has the advantages of timeliness, reliability, effectiveness, stability (compared with electromagnetic driving program control), high mechanical efficiency, less system heating and other unnecessary overflow, throttling and other power loss, strong pollution resistance, difficult blockage and low failure.
Example 2
On the basis of the embodiment 1, the embodiment specifically describes a hydraulic control method of the rock drill for preventing drill jams by adopting a hydraulic oil way structure of the rock drill.
The control method of the conventional rock drilling working state comprises the following steps:
s1, when drilling, starting the thrust cylinder 71 to be in a forward state, so that a drill rod is propped against a rock stratum;
s2, starting the impact oil cylinder 72 and the rotary motor 73 to enable the drill rod to rotate and conduct low-pressure impact drilling on the rock stratum;
s3, enabling the first hydraulic reversing valve 11 to be in a normal position, and performing low-flushing low-pushing propulsion to enable the drill rod to slowly enter a rock stratum;
s4, after the drill rod enters the rock stratum for a certain distance, the first electromagnetic directional valve 21 is electrified to perform high-pressure impact on the rock stratum;
s5, when high pressure impacts, the threshold value of the first hydraulic reversing valve 11 is set, so that the feedback pressure value of the second hydraulic feedback oil path 62 is higher than the threshold value, the first hydraulic reversing valve 11 is closed, and the propulsion oil cylinder 71 is in a high-impact high-propulsion state.
Because of the hydraulic active mode, the high-pressure impact is performed by actively entering high pressure to push, the action is rapid and reliable, the working efficiency is improved, and the operation difficulty is reduced.
The working process of the air defense valve group 3 can comprise the following steps:
when the propelling pressure is lower than the set pressure of the fourth mechanical relief valve 33, the second hydraulic reversing valve 31 is in a normal position, the impact pressure is the set pressure of the third mechanical relief valve 32, and the impact oil cylinder 72 is in a low-impact state;
when the propulsion pressure is higher than the set pressure of the fourth mechanical overflow valve 33, the second hydraulic reversing valve 31 is in the off position, so that the first electromagnetic reversing valve 21 and the second electromagnetic proportional overflow valve 23 are powered on, and the impact oil cylinder 72 is in a high-impact state;
when the first electromagnetic directional valve 21, the second electromagnetic directional valve (not shown) and the second electromagnetic proportional relief valve 23 are energized, the impact cylinder 72 is in a high-impact state and a drill-shake state even if the advancing pressure is lower than the set pressure of the fourth mechanical relief valve 33; the control method is convenient to switch the working state of the impact cylinder 72 according to the situation when in actual use.
The following describes the principle of the control method when a sudden abnormal condition is encountered in the conventional drilling process.
During the rock drilling process, the following three clamping working conditions are met:
1. when the rock drilling is advanced, soft rock or a cavity is suddenly encountered;
2. when the drilling is advanced, the slag is not smooth due to the reasons of unsmooth waterway and the like, and the rotation resistance of the drill rod is gradually increased;
3. when the rock drilling is advanced, the drill rod suddenly encounters a crack, and the rotation resistance of the drill rod is suddenly increased.
When the first working condition is met, the first working condition needs to be controlled in time, so that the blank punching of the drill rod is avoided; in the normal rock drilling working state, the second hydraulic reversing valve 31 is closed, and the air-break preventing valve group 3 does not act; when the soft rock or the cavity is suddenly encountered, the propelling pressure is rapidly reduced, and at this time, the second hydraulic reversing valve 31 senses that the propelling pressure value is rapidly reduced through the first hydraulic feedback oil path 61, the second hydraulic reversing valve 31 is switched from the closed state to the open state, the fourth mechanical overflow valve 33 acts, and the impact pressure is reduced.
When the 2 nd working condition and the 3 rd working condition are met, the control is needed in time, and the blank punching of the card drill rod is avoided; in the conventional rock drilling working state, if the rotation pressure is increased due to sudden abnormal working conditions, the rotation pressure is fed back to the anti-seizing valve bank 4 in real time through the third hydraulic feedback oil path 63, and when the rotation pressure is increased to the spring pressure value of the third hydraulic reversing valve 41, the advancing speed of the pushing oil cylinder 71 is slowed down until the final stop; when the rotation pressure rises to the spring pressure value of the fourth hydraulic reversing valve 42, the thrust cylinder 71 enters a retreating state, and the two states are mutually switched at any time along with the change of the rotation pressure, so that the purpose of protecting the rotating rod and preventing the drill rod in a hydraulic manner in time and rapidly is realized.
Example 3
Based on embodiments 1 and 2, the following two kinds of three kinds of drill rod clamping conditions are encountered in the rock drilling process:
1. when the drilling is advanced, the slag is not smooth due to the reasons of unsmooth waterway and the like, and the rotation resistance of the drill rod is gradually increased;
2. when the rock drilling is advanced, the drill rod suddenly encounters a crack, and the rotation resistance of the drill rod is suddenly increased.
The embodiment realizes the control method based on the hydraulic oil circuit structure of embodiment 1 by adopting the following structure:
the anti-seize valve block 4 further comprises a fifth mechanical relief valve 45 and a sixth mechanical relief valve 46, wherein the fifth mechanical relief valve 45 and the sixth mechanical relief valve 46 are used for changing the working state of the thrust cylinder 71 according to the rotation pressure received and conducted by the third hydraulic directional valve 41 and the fourth hydraulic directional valve 42.
In this embodiment, the spring pressures of the third hydraulic reversing valve 41 and the fourth hydraulic reversing valve 42 do not need to be adjusted according to the specific diameter of the rotating rod, but the set opening pressures of the fifth mechanical overflow valve 45 and the sixth mechanical overflow valve 46 are adopted, and the purposes of protecting the rotating rod and actively avoiding the drill rod are realized by matching with the throttle holes 44 arranged on the corresponding oil path structure; the third hydraulic direction valve 41 and the fourth hydraulic direction valve 42 have the feature of reducing the complexity of the structure operation and improving the reliability, and are advantageous compared with the embodiment 1.
The specific control method is based on example 2, with the following differences:
when meeting the two abnormal working conditions, the control needs to be timely carried out to avoid the blank punching of the card drill rod; the rotation pressure is fed back to the anti-seize valve group 4 in real time through a third hydraulic feedback oil way 63, the rotation pressure is conducted to the fifth mechanical overflow valve 45 and the sixth mechanical overflow valve 46 through a third hydraulic reversing valve 41 and a fourth hydraulic reversing valve 42, and when the rotation pressure rises to a set threshold value of the fifth mechanical overflow valve 45, the advancing speed of the pushing cylinder 71 is slowed until the pushing cylinder is finally stopped; when the rotation pressure rises to the set threshold value of the sixth mechanical relief valve 46, the thrust cylinder 71 enters a retreating state, and the two states are switched with each other at any time along with the change of the rotation pressure, so that the purpose of protecting the rotating rod and preventing the drill rod in a hydraulic manner in time and rapidly and effectively is also achieved.
Claims (10)
1. A rock drill hydraulic oil circuit structure of anti-sticking borer, its characterized in that: the hydraulic control system comprises a propulsion control oil circuit for connecting the pump and the propulsion oil cylinder, an impact control oil circuit for connecting the pump and the impact oil cylinder and a rotation control oil circuit for connecting the pump and the rotation motor;
the propulsion control oil way is provided with a propulsion control valve group and an anti-seize valve group;
the impact control oil circuit is provided with an impact control valve group and an air-break prevention valve group;
the propulsion control oil way is also connected to the air-break prevention valve group through a first hydraulic feedback oil way;
the impact control oil path is also connected to the propulsion control valve group through a second hydraulic feedback oil path;
the rotation control oil path is also connected to the anti-seize valve bank through a third hydraulic feedback oil path;
the propulsion control valve group is used for switching the working state of the propulsion oil cylinder, and the impact control valve group is used for switching the working state of the impact oil cylinder;
the idle-beating-prevention valve group is used for receiving feedback of rock drilling propelling pressure and changing the working state of the impact oil cylinder;
the anti-seize drill valve group is used for receiving feedback of drill bit rotation pressure and changing the working state of the propulsion oil cylinder.
2. The hydraulic oil path structure of a rock drill for preventing seizing according to claim 1, wherein:
the propulsion control valve group comprises a first hydraulic reversing valve, a first mechanical overflow valve and a first electromagnetic proportional overflow valve, wherein the first hydraulic reversing valve is used for receiving impact pressure fed back by a second hydraulic feedback oil way;
the impact control valve group comprises a first electromagnetic reversing valve, a second mechanical overflow valve and a second electromagnetic proportional overflow valve;
the air-break prevention valve group comprises a second hydraulic reversing valve, a third mechanical overflow valve and a fourth mechanical overflow valve, wherein the second hydraulic reversing valve is used for receiving the propelling pressure fed back by the first hydraulic feedback oil way;
the anti-seize valve bank comprises a third hydraulic reversing valve, a fourth hydraulic reversing valve and a one-way valve, wherein the third hydraulic reversing valve and the fourth hydraulic reversing valve are used for receiving the rotary pressure fed back by a third hydraulic feedback oil way, and the one-way valve is used for ensuring that the propulsion cylinder normally retreats when the working condition of the third hydraulic reversing valve is open.
3. The hydraulic oil path structure of a rock drill for preventing seizing according to claim 2, wherein: the air-break prevention valve group further comprises a second electromagnetic reversing valve; the second electromagnetic directional valve is used for independently controlling the high-pressure impact state during low-pressure propulsion.
4. The hydraulic oil path structure of a rock drill for preventing seizing according to claim 2, wherein: the third hydraulic reversing valve and the fourth hydraulic reversing valve are internally provided with adjustable pressure springs, and the adjustable pressure springs are used for enabling the third hydraulic reversing valve and the fourth hydraulic reversing valve to act according to the rotating pressure fed back by the third hydraulic feedback oil way so as to change the working state of the thrust cylinder.
5. The hydraulic oil path structure of a rock drill for preventing seizing according to claim 2, wherein: the anti-seize valve bank further comprises a fifth mechanical overflow valve and a sixth mechanical overflow valve, wherein the fifth mechanical overflow valve and the sixth mechanical overflow valve are used for changing the working state of the propulsion oil cylinder according to the rotation pressure received and conducted by the third hydraulic reversing valve and the fourth hydraulic reversing valve.
6. A hydraulic control method of a rock drill based on an anti-seize rock drill according to any one of claims 3 to 5, characterized by the steps of:
s1, when drilling, starting a thrust cylinder to be in a forward state, and enabling a drill rod to be bound to a rock stratum;
s2, starting an impact oil cylinder and a rotary motor to enable the drill rod to rotate and conduct low-pressure impact hole opening on the rock stratum;
s3, enabling the first hydraulic reversing valve to be in a normal position, and performing low-flushing low-pushing propulsion to enable the drill rod to slowly enter a rock stratum;
s4, after the drill rod enters the rock stratum for a certain distance, the first electromagnetic directional valve is electrified, and high-pressure impact is carried out on the rock stratum;
s5, when high pressure impacts, the threshold value of the first hydraulic reversing valve is set, so that the feedback pressure value of the second hydraulic feedback oil way is higher than the threshold value, the first hydraulic reversing valve is closed, and the propulsion oil cylinder is in a high-impact high-propulsion state.
7. The hydraulic control method of the drill rod preventing drill rod according to claim 6, wherein the hydraulic control method comprises the following steps:
when the propelling pressure is lower than the set pressure of the fourth mechanical overflow valve, the second hydraulic reversing valve is in a normal position, the impact pressure is the set pressure of the third mechanical overflow valve, and the impact oil cylinder is in a low-impact state;
when the propelling pressure is higher than the set pressure of the fourth mechanical overflow valve, the second hydraulic reversing valve is in a disconnected position, so that the first electromagnetic reversing valve and the second electromagnetic proportional overflow valve are electrified, and the impact oil cylinder is in a high-impact state;
when the first electromagnetic directional valve, the second electromagnetic directional valve and the second electromagnetic proportional overflow valve are powered on, the impact oil cylinder is in a high-impact state and a vibration drill rod state even if the propelling pressure is lower than the set pressure of the fourth mechanical overflow valve.
8. The hydraulic control method of the drill rod preventing drill rod according to claim 6, wherein the hydraulic control method comprises the following steps: when the second hydraulic reversing valve senses that the propelling pressure value is rapidly reduced through the first hydraulic feedback oil way, the second hydraulic reversing valve is switched from a closed state to an open state, the fourth mechanical overflow valve acts, and the impact pressure is reduced.
9. The hydraulic control method of the drill rod preventing drill rod according to claim 6, wherein the hydraulic control method comprises the following steps: the rotation pressure is fed back to the anti-seize valve bank in real time through a third hydraulic feedback oil way, and when the rotation pressure rises to the spring pressure value of the third hydraulic reversing valve, the advancing speed of the thrust cylinder is slowed down until the thrust cylinder is finally stopped; when the rotation pressure rises to the spring pressure value of the fourth hydraulic reversing valve, the thrust cylinder enters a retreating state.
10. The hydraulic control method of the drill rod preventing drill rod according to claim 6, wherein the hydraulic control method comprises the following steps: the rotary pressure is fed back to the anti-seize valve bank in real time through a third hydraulic feedback oil way, the rotary pressure is conducted to a fifth mechanical overflow valve and a sixth mechanical overflow valve through a third hydraulic reversing valve and a fourth hydraulic reversing valve, and when the rotary pressure rises to a set threshold value of the fifth mechanical overflow valve, the advancing speed of the pushing oil cylinder is slowed down until the pushing oil cylinder is finally stopped; when the rotation pressure rises to the set threshold value of the sixth mechanical relief valve, the thrust cylinder enters a retreating state.
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