CN110242628B - Anti-seizing hydraulic control system and rock drilling equipment - Google Patents
Anti-seizing hydraulic control system and rock drilling equipment Download PDFInfo
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- CN110242628B CN110242628B CN201910672103.5A CN201910672103A CN110242628B CN 110242628 B CN110242628 B CN 110242628B CN 201910672103 A CN201910672103 A CN 201910672103A CN 110242628 B CN110242628 B CN 110242628B
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- 239000011435 rock Substances 0.000 title claims abstract description 89
- 238000005553 drilling Methods 0.000 title claims abstract description 65
- 238000013016 damping Methods 0.000 claims description 10
- 230000008859 change Effects 0.000 description 13
- 230000000903 blocking effect Effects 0.000 description 11
- 230000008901 benefit Effects 0.000 description 7
- 238000010586 diagram Methods 0.000 description 6
- 230000000694 effects Effects 0.000 description 5
- 230000015572 biosynthetic process Effects 0.000 description 4
- 238000005755 formation reaction Methods 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 230000009471 action Effects 0.000 description 3
- 238000006073 displacement reaction Methods 0.000 description 3
- 238000009527 percussion Methods 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000009412 basement excavation Methods 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000011010 flushing procedure Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 238000010079 rubber tapping Methods 0.000 description 1
- 230000000087 stabilizing effect Effects 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
- 238000013024 troubleshooting Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 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
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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
-
- 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
- F15B13/024—Pressure relief valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- 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
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
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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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/001—Servomotor systems with fluidic control
-
- 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
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
- F15B2013/0448—Actuation by solenoid and permanent magnet
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20546—Type of pump variable capacity
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/6306—Electronic controllers using input signals representing a pressure
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/65—Methods of control of the load sensing pressure
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Earth Drilling (AREA)
Abstract
The invention relates to the technical field of rock drilling equipment, in particular to an anti-seizing hydraulic control system and rock drilling equipment. The anti-seize hydraulic control system comprises an impact control module, a propulsion pressure control module, a propulsion speed control module, a variable pump, a rotary motor and a propulsion oil cylinder; the impact control module comprises a load feedback port of the variable pump and a first proportional reversing valve of the oil tank, and a pilot control port of the impact control module is connected with an oil inlet of the thrust cylinder; the propulsion pressure control module comprises a third proportional reversing valve which is communicated with an oil inlet of the propulsion oil cylinder and the oil tank; the propulsion speed control module comprises a pilot proportional throttle valve connected between the oil tank and an oil inlet of the propulsion oil cylinder, and pilot control ports of the third proportional reversing valve and the pilot proportional throttle valve are both connected with the oil inlet of the rotary motor. The rock drilling equipment comprises the anti-seize hydraulic control system. The anti-seize hydraulic control system and the rock drilling equipment are matched with various rock strata in a self-adaptive manner, and reasonable impact pressure, propulsion pressure and propulsion speed are achieved.
Description
Technical Field
The invention relates to the technical field of rock drilling equipment, in particular to an anti-seizing hydraulic control system and rock drilling equipment.
Background
In the related art, in the tunnel rock drilling operation, the hydraulic rock drilling equipment is widely applied to occasions such as railway and highway tunnel and other mine excavation due to the advantages of high rock drilling efficiency, small pollution, high safety and the like.
The rock drilling principle of the hydraulic rock drill is generally approximately the same, impact energy generated by the rock drill is transmitted to the drill bit through the connecting device, impact energy acts on rock stratum to break rock, at the moment, the drill bit can drive the drill rod to rotate, then the rock is broken by utilizing the high-speed cutting action of the drill bit, the broken rock is brought out of a blast hole by utilizing water flushing and drill bit rotation, and meanwhile, the rock drill is driven by the rock drill propulsion oil cylinder to propel, so that the drill bit continuously acts on the rock stratum, and high-efficiency drilling speed is realized. However, because the rock stratum structure is complex, unpredictable rock stratum forms such as broken rock, cracks or dissolved rock can appear, so that drill rod deflection or drill sticking occurs in the drilling process of the rock drill. Under the serious circumstances, can lead to the fact the drilling rod to be difficult to pull out and produce the dead hole, extravagant drilling tools such as drilling rod, drill bit simultaneously have not only influenced the production efficiency of rock drilling construction, have increased construction cost moreover, consequently, general drill jumbo can all be equipped with a set of anti-sticking borer hydraulic control system and reduce the risk of sticking the drill.
The drill rod type is generally divided into a gradual change drill rod type, a crack drill rod type and a karst cave drill rod type, a two-stage anti-blocking hydraulic system is generally adopted for the current domestic hydraulic drill jumpers, the control of a pushing oil cylinder can be realized mainly aiming at gradual change drill rod type and crack drill rod type, when the feedback rotation pressure reaches a set anti-blocking drill rod value, the pushing oil cylinder stops pushing or reversely pushing, so that the effect of preventing drill rod blocking is realized, but the system only sets two-stage anti-blocking pressure control, can not effectively and continuously control the pushing pressure and impact power, namely, possible drill rod blocking accidents and low drill rod blocking risks can not be prevented in advance, and meanwhile, when the anti-blocking drill rod is started, the pushing oil cylinder stops or returns, so that the drilling efficiency is reduced; and aiming at the most complex karst cave drill rod, many control systems do not have the effect of preventing the drill rod from being blocked, and the conventional control mode is difficult to realize the effective anti-blocking effect.
Therefore, it is highly desirable to provide an anti-blocking hydraulic control system, which can cope with three types of blocking of gradual blocking, crack blocking and karst cave blocking, and can perform effective continuous control on the propelling pressure, the impact pressure and the propelling speed so as to prevent possible blocking accidents and low blocking risks in advance.
Disclosure of Invention
The first objective of the present invention is to provide a hydraulic control system for preventing drill rod from being blocked, so as to solve the technical problems that the propulsion pressure and the impact power cannot be effectively and continuously controlled and the drill rod blocking of the karst cave cannot be dealt with in the related art to a certain extent.
A second object of the present invention is to provide a rock drilling apparatus, which solves the technical problems that the related art cannot effectively and continuously control the propelling pressure and the impact power, and cannot cope with the karst cave drill rod.
In order to achieve the above object, the present invention provides the following technical solutions;
Based on the first object, the anti-seize hydraulic control system provided by the invention is used for rock drilling equipment and comprises an impact control module, a propulsion pressure control module, a propulsion speed control module, a variable pump, a rotary motor and a propulsion cylinder;
the impact control module comprises a first proportional reversing valve, the first proportional reversing valve is communicated with a load feedback port of the variable pump and an oil tank, and a pilot control port of the first proportional reversing valve is connected with an oil inlet of the propulsion oil cylinder;
the propulsion pressure control module comprises a third proportional reversing valve, the third proportional reversing valve is communicated with an oil inlet of the propulsion oil cylinder and the oil tank, and a pilot control port of the third proportional reversing valve is connected with an oil inlet of the rotary motor;
The propulsion speed control module comprises a pilot proportional throttle valve, the pilot proportional throttle valve is connected between the oil tank and an oil inlet of the propulsion oil cylinder, and a pilot control port of the pilot proportional throttle valve is connected with the oil inlet of the rotary motor.
In any of the above solutions, optionally, the impact control module further includes a first low pressure overflow valve, an overflow port of the first low pressure overflow valve is connected to the oil tank, and an oil inlet of the first low pressure overflow valve is connected between the oil tank and an oil outlet of the first proportional reversing valve;
The propulsion pressure control module further comprises a third low-pressure overflow valve, the third proportional reversing valve is connected between an oil inlet of the propulsion oil cylinder and an oil inlet of the third low-pressure overflow valve, and an overflow port of the third low-pressure overflow valve is communicated with the oil tank.
In any of the above solutions, optionally, the impact control module further includes a first high-pressure relief valve, where the first high-pressure relief valve is connected between the oil tank and another oil outlet of the first proportional reversing valve;
The propulsion pressure control module further comprises a third high-pressure overflow valve, an oil inlet of the third high-pressure overflow valve is connected between the oil inlet of the propulsion oil cylinder and the third proportional reversing valve, and an overflow port of the third high-pressure overflow valve is communicated with the oil tank;
The propulsion pressure control module further comprises an electromagnetic directional valve III, wherein the electromagnetic directional valve III is connected between the third high-pressure overflow valve and the third low-pressure overflow valve so as to connect or disconnect an oil inlet of the third high-pressure overflow valve and an oil inlet of the third low-pressure overflow valve;
The anti-seizing hydraulic control system further comprises a second pressure sensor, the second pressure sensor is used for measuring the rotation pressure of the rotation motor, and the electromagnetic directional valve III is electrically connected with the second pressure sensor.
In any of the above solutions, optionally, the propulsion pressure control module further includes a pressure compensating valve and a check valve, the pressure compensating valve and the pilot proportional throttle valve being connected between the tank and the pilot proportional throttle valve;
an oil outlet of the one-way valve is connected with a valve port of the pressure compensation valve, which is close to the oil tank, and an oil inlet of the one-way valve is connected with a valve port of the pressure compensation valve, which is close to the oil inlet of the propulsion oil cylinder.
In any of the above technical solutions, optionally, the propulsion speed control module further includes a two-position four-way reversing valve, a control port of the two-position four-way reversing valve is connected to an oil inlet of the rotary motor, and the two-position four-way reversing valve can be reversed according to a rotation pressure of the rotary motor to control a cylinder rod of the propulsion cylinder to propel or retract;
And the set pressure of the two-position four-way reversing valve is larger than that of the pilot proportional throttle valve.
In any of the above technical solutions, optionally, the anti-seize hydraulic control system further includes a first pressure sensor, where the first pressure sensor is used to measure a thrust pressure of the thrust cylinder;
the impact control module further comprises a first electromagnetic directional valve and a second electromagnetic directional valve, and the first electromagnetic directional valve and the second electromagnetic directional valve are electrically connected with the first pressure sensor;
The first electromagnetic reversing valve can be communicated with a load feedback port of the variable pump and an oil inlet of the first proportional reversing valve before reversing, and the first electromagnetic reversing valve can be used for connecting the load feedback port of the variable pump between the first low-pressure overflow valve and the first proportional reversing valve after reversing;
The electromagnetic directional valve II can connect the control port of the pilot proportional throttle valve with the oil inlet of the rotary motor before reversing, and the control port of the pilot proportional throttle valve can be connected between the electromagnetic directional valve I and the load feedback port of the variable pump after reversing.
In any of the above technical solutions, optionally, the impact control module further includes a fourth electromagnetic directional valve and a hydraulic control directional valve, where the fourth electromagnetic directional valve is capable of communicating an oil inlet of the rotary motor with the second electromagnetic directional valve before direction change, the fourth electromagnetic directional valve is capable of communicating the second electromagnetic directional valve with the oil tank after direction change, and a control port of the two-position four-way directional valve is connected between the fourth electromagnetic directional valve and the second electromagnetic directional valve;
and a control port of the hydraulic control reversing valve is connected with a load feedback port of the variable pump so as to connect or disconnect the oil tank and an oil inlet of the first proportional reversing valve.
In any of the above technical solutions, optionally, the anti-seizing hydraulic control system further includes a damping hole, and the damping hole is provided between the bypass of the variable pump, the oil inlet of the thrust cylinder and the first proportional reversing valve, and between the oil inlet of the thrust cylinder and the third proportional reversing valve.
In any of the above solutions, optionally, the variable pump is a load-sensitive pump.
Based on the second object, the rock drilling equipment provided by the invention comprises the anti-seizing hydraulic control system according to any one of the technical schemes.
By adopting the technical scheme, the invention has the beneficial effects that:
According to the anti-seizing hydraulic control system provided by the invention, through the proportion adjusting function of the first proportion reversing valve of the impact control module and the third proportion reversing valve of the propulsion pressure control module, the rotation pressure of the rotary motor can be kept at a reasonable drilling pressure value, and the propulsion cylinder can be kept at a reasonable propulsion pressure value, so that the anti-seizing hydraulic control system can be in a self-adaptive matching state with various complex rock strata, thereby avoiding seizing accidents caused by high impact pressure, high propulsion pressure and high propulsion speed in the drilling process, further achieving the stable effect of self-adaptive control of the system, and improving the rock drilling efficiency. The rock drilling equipment provided by the invention comprises the anti-seizing hydraulic control system, and all the beneficial effects of the anti-seizing hydraulic control system can be realized.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings that are needed in the description of the embodiments or the prior art will be briefly described, and it is obvious that the drawings in the description below are some embodiments of the present invention, and other drawings can be obtained according to the drawings without inventive effort for a person skilled in the art.
FIG. 1 is a schematic diagram of a first structure of an anti-seize hydraulic control system according to an embodiment of the invention;
FIG. 2 is a schematic diagram of a second structure of an anti-seize hydraulic control system according to an embodiment of the invention;
Fig. 3 is a schematic diagram of a third structure of an anti-seizing hydraulic control system according to an embodiment of the invention.
Icon: 1-an impact control module; 11-a first high pressure overflow valve; 12-a first low pressure relief valve; 14-a first proportional reversing valve; 15-a hydraulically-controlled reversing valve; 16-an electromagnetic reversing valve I; 17-an electromagnetic reversing valve IV; 18-an electromagnetic reversing valve II; 2-a propulsion speed control module; 21-a pilot proportional throttle valve; 22-two-position four-way reversing valve; 3-a propulsion pressure control module; 31-a pressure compensating valve; 32-a third high pressure relief valve; 33-a third low pressure relief valve; 34-an electromagnetic reversing valve III; 35-a third proportional reversing valve; 4-a second pressure sensor; 5-a rotary motor; 6-damping holes; 7-a variable pump; 8-a first pressure sensor; 9-pushing an oil cylinder; 10-rock drill.
Detailed Description
The following description of the embodiments of the present invention will be made apparent and fully in view of the accompanying drawings, in which some, but not all embodiments of the invention are shown. 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.
In the description of the present invention, it should be noted that the directions or positional relationships indicated by the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. are based on the directions or positional relationships shown in the drawings, are merely for convenience of describing the present invention and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In the description of the present invention, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be either fixedly connected, detachably connected, or integrally connected, for example; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present invention will be understood in specific cases by those of ordinary skill in the art.
Example 1
Referring to fig. 1 to 3, the present embodiment provides an anti-seize hydraulic control system; FIG. 1 is a schematic diagram of a first structure of an anti-seize hydraulic control system according to the present embodiment; fig. 2 is a second schematic structural diagram of the anti-seizing hydraulic control system according to the present embodiment; fig. 3 is a third schematic structural diagram of the anti-seizing hydraulic control system according to the present embodiment.
The anti-seize hydraulic equipment provided by the embodiment is used for rock drilling equipment.
Referring to fig. 1 to 3, the anti-seize hydraulic control system comprises an impact control module 1, a propulsion pressure control module 3, a propulsion speed control module 2, a variable pump 7, a rotary motor 5 and a propulsion cylinder 9; wherein the variable pump 7 is used for driving the rock drill 10 to impact the rock, the rotary motor 5 is used for driving the drill bit of the rock drill 10 to rotate, and the thrust cylinder 9 is used for driving the drill bit of the rock drill 10 to drill deep into the rock.
The impact control module 1 comprises a first proportional reversing valve 14, wherein the first proportional reversing valve 14 is communicated with a load feedback port of the variable pump 7 and an oil tank, and a feedback port of the first proportional reversing valve 14 is connected with an oil inlet of the thrust cylinder 9; the valve core opening of the first proportional valve is determined by the propelling pressure of the propelling oil cylinder 9, the higher the propelling pressure of the propelling oil cylinder 9 is, the larger the valve core opening of the first proportional valve to the first high-pressure overflow valve is, the valve core opening of the first proportional valve to the first low-pressure overflow valve is reduced, and accordingly the pressure of the load feedback port of the variable pump 7 is larger.
The propulsion pressure control module 3 comprises a third proportional reversing valve 35, the third proportional reversing valve 35 is communicated with an oil inlet of the propulsion oil cylinder 9 and an oil tank, and a control port of the third proportional reversing valve 35 is connected with an oil inlet of the rotary motor 5. The valve opening of the third proportional directional valve 35 is determined by the rotation pressure of the rotation motor 5, the greater the valve opening of the third proportional directional valve 35 to the rotation motor 5, and the greater the valve opening of the third proportional directional valve 35 to the thrust cylinder 9, that is, the thrust pressure of the thrust cylinder 9 becomes smaller.
The propulsion speed control module 2 comprises a pilot proportional throttle valve 21, the pilot proportional throttle valve 21 is connected between the oil tank and an oil inlet of the propulsion oil cylinder 9, and a pilot control port of the pilot proportional throttle valve 21 is connected with an oil inlet of the rotary motor 5. Wherein, the valve core opening of the pilot proportional throttle valve 21 is determined by the rotation pressure of the rotation motor 5, the oil inlet flow rate of the propulsion cylinder 9 is related to the valve core opening of the pilot proportional throttle valve 21, and the propulsion speed of the propulsion cylinder 9 is related to the oil inlet flow rate of the propulsion cylinder 9. That is, if the rock formation is changed while the rock drill 10 is in a stable rotation and pushing state, the rotation pressure of the rotation motor 5 is also changed. If the rotation pressure is increased, the rotation pressure is fed back to the third proportional reversing valve 35, the valve core of the third proportional reversing valve 35 is pushed to be in proportional reversing, and at the moment, the pushing pressure proportion of the pushing oil cylinder 9 is reduced. Meanwhile, the propelling pressure of the propelling oil cylinder 9 is fed back to the first proportional reversing valve 14, the valve core of the first proportional reversing valve 14 is pushed to be in proportional reversing, the pressure of the load feedback port of the variable pump 7 is proportionally reduced, and therefore the impact pressure of the rock drill 10 is proportionally reduced.
Meanwhile, when the rotation pressure changes, the self-adaptive matching mode of rock drilling is firstly entered, if the rotation pressure continues to rise after adjustment, a higher rotation pressure value is fed back to the pilot proportional throttle valve 21, the valve core opening of the pilot proportional throttle valve 21 is adjusted according to the rotation pressure value to reduce the valve core opening proportion, the flow of oil supply to the oil inlet of the propulsion oil cylinder 9 can be reduced proportionally, and the propulsion speed of the propulsion oil cylinder 9 can be controlled to reduce. Further, as the rotational pressure continues to increase and is higher than the pressure set by the pilot proportional throttle 21, the rate of advancement of the ram 9 is minimized and the system will travel through the formation at a lower rate of advancement. At this point, the system enters a throttle deceleration mode.
It will be appreciated that if the rotational pressure of the rotary motor 5 becomes large, the boost pressure and the boost speed of the boost cylinder 9 can be controlled to increase, while the percussion pressure of the rock drill 10 is controlled to increase, according to the same principle as described above. Of course, if the rock formation is unchanged, i.e. the rotation pressure of the rotation motor 5 is stabilized within a reasonable range, the pushing pressure and the pushing speed of the pushing cylinder 9 are also stabilized within a reasonable range, and the percussion pressure of the rock drill 10 is also stabilized within a reasonable range.
Therefore, the cooperative work and the self-adaptive adjustment among the thrust cylinder 9, the variable pump 7 and the rotary motor 5 of the anti-seizing hydraulic control system are realized, and the anti-seizing hydraulic control system enters a rock drilling self-adaptive matching mode.
According to the anti-seizing hydraulic control system in the embodiment, through the proportion adjusting function of the first proportion reversing valve 14 of the impact control module 1 and the third proportion reversing valve 35 of the propulsion pressure control module 3, the rotation pressure of the rotation motor 5 can be kept at a reasonable drilling pressure value, the propulsion oil cylinder 9 is kept at a reasonable propulsion pressure value, the propulsion pressure, the propulsion speed and the impact pressure are continuously adjusted, the anti-seizing hydraulic control system can be in a self-adaptive matching state with various complex rock strata, so that seizing accidents caused by high impact pressure, high propulsion pressure and high propulsion speed in the drilling process are avoided, the stabilizing effect of the self-adaptive control of the system is further achieved, and the rock drilling efficiency is improved. In addition, the three kinds of clamping rods of gradual change clamping rods, crack clamping rods and karst cave clamping rods can be dealt with because the comprehensive adjustment of the propulsion pressure, the propulsion speed and the impact pressure can be realized. Compared with the technical scheme that the propelling pressure in the related art is a constant pressure value, the hydraulic control system does not have the technical scheme that the hydraulic control system continuously changes according to working conditions and the upcoming drill clamping risk cannot be prevented in advance by adopting a switch logic control mode, the hydraulic control system for preventing the drill clamping in the technical scheme has the advantage of reducing the drill clamping risk by self-adapting to different rock stratum working conditions, and has a preventing function for gradual change drill clamping working conditions.
In addition, the anti-seizing hydraulic control system has the advantages of simple structure, easy maintenance, high reliability and strong applicability and popularization compared with the anti-seizing hydraulic control system of full-computer rock drilling equipment on the premise of ensuring control precision and corresponding time.
In an alternative of this embodiment, referring to fig. 1, the impact control module 1 further includes a first low pressure relief valve 12, an overflow port of the first low pressure relief valve 12 is connected to the oil tank, and an oil inlet of the first low pressure relief valve 12 is connected between the oil tank and an oil outlet of the first proportional reversing valve 14;
The propulsion pressure control module 3 further comprises a third low pressure relief valve 33, and a third proportional reversing valve 35 is connected between the oil inlet of the propulsion cylinder 9 and the oil inlet of the third low pressure relief valve 33.
When the rock drill 10 is started to rotate and advance, firstly, the drilling mode is entered, at this time, the rock drill 10 advances forwards, the advancing pressure is controlled by the third low-pressure overflow valve 33, and when the drill bit of the rock drill 10 is close to the rock face, the advancing pressure rises to reach the set pressure of the third low-pressure overflow valve 33; simultaneously, the pressure of the load feedback port of the variable pump 7 reaches the set pressure of the first low-pressure overflow valve 12, and the rock drill 10 starts low impact; at the same time, the rotation pressure rise stabilizes at the opening rotation pressure. So that the advancing pressure, the rotating pressure and the impact pressure can be stabilized within a range suitable for the opening mode under the restriction of the first low pressure relief valve 12 and the third low pressure relief valve 33.
In an alternative of this embodiment, referring to fig. 2, the impact control module 1 further includes a first high-pressure relief valve 11, the first high-pressure relief valve 11 being connected between the tank and the other oil outlet of the first proportional directional valve 14;
The propulsion pressure control module 3 further comprises a third high-pressure overflow valve 32, an oil inlet of the third high-pressure overflow valve 32 is connected between an oil inlet of the propulsion cylinder 9 and a third proportional reversing valve 35, and an overflow port of the third high-pressure overflow valve 32 is communicated with an oil tank;
the propulsion pressure control module 3 further comprises an electromagnetic directional valve III 34, and the electromagnetic directional valve III 34 is connected between the third high-pressure overflow valve 32 and the third low-pressure overflow valve 33 so as to connect or disconnect an oil inlet of the third high-pressure overflow valve 32 and an oil inlet of the third low-pressure overflow valve 33;
The anti-seize hydraulic control system further comprises a second pressure sensor 4, the second pressure sensor 4 is used for measuring the rotation pressure of the rotation motor 5, and the electromagnetic directional valve III 34 is electrically connected with the second pressure sensor 4.
When the second pressure sensor 4 measures that the rotation pressure of the rotation motor 5 reaches the opening unit, the electromagnetic directional valve III 34 is powered on, the electromagnetic directional valve III 34 breaks the connection relationship between the oil inlet of the third high-pressure relief valve 32 and the oil inlet of the third low-pressure relief valve 33, namely, breaks the connection between the third low-pressure relief valve 33 and the oil inlet of the pushing cylinder 9, so that the pushing pressure of the pushing cylinder 9 is controlled by the third high-pressure relief valve 32, the anti-seizing hydraulic control system enters a high-pushing state, at the moment, the first proportional directional valve 14 is fully switched under the action of the pushing pressure, the pressure of the load feedback port of the variable pump 7 is raised, the impact pressure reaches the set pressure of the first high-pressure relief valve 11, the rock drill 10 starts high impact, and the anti-seizing hydraulic control system can be converted into a normal drilling mode from the opening mode. The rotation pressure is then stabilized at the drilling rotation pressure.
By the cooperation of the three electromagnetic directional valves 34, the third high-pressure relief valve 32, the first high-pressure relief valve 11, the first proportional directional valve 14 and the like, the self-adaptive adjustment and continuous change of the impact pressure, the rotation pressure and the propelling pressure are realized, and the drilling mode is easily changed into the normal drilling mode.
In the open hole mode or the normal drilling mode, if the rotation pressure changes due to rock stratum changes, the self-adaptive matching mode of rock drilling can be entered, so that the self-adaptability of the rock drilling machine 10 to different rock strata is improved, and the production efficiency is improved.
The set pressures of the first low-pressure relief valve 12, the first high-pressure relief valve 11, the third high-pressure relief valve 32 and the third low-pressure relief valve 33 are all determined by the normal operating range of the rock drill 10. Obviously, the set pressure of the first high pressure relief valve 11 is higher than the set pressure of the first low pressure relief valve 12, and the set pressure of the third high pressure relief valve 32 is higher than the set pressure of the third low pressure relief valve 33.
Referring to fig. 3, in an alternative of this embodiment, the propulsion pressure control module 3 further includes a pressure compensating valve 31 and a check valve, the pressure compensating valve 31 being connected between the tank and the pilot proportional throttle 21;
the oil outlet of the one-way valve is connected with the valve port of the pressure compensation valve 31, which is close to the oil tank, and the oil inlet of the one-way valve is connected with the valve port of the pressure compensation valve 31, which is close to the oil inlet of the propulsion cylinder 9.
The oil inlet of the pilot proportional throttle valve 21 is pressure-compensated by the pressure compensation valve 31 so that the pressure difference between the front and rear of the pilot proportional throttle valve 21 tends to be a stable constant value.
Compared with the scheme that when the drill is prevented from being blocked and started, the pushing oil cylinder can be stopped or returned, the rock drilling efficiency can be improved maximally in a mode of reducing the pushing speed proportionally, and drill blocking caused by drill bit deflection due to too high pushing speed can be avoided effectively.
Wherein, by providing a one-way valve, when the push cylinder 9 is retracted, the one-way valve provides a passage for oil to flow back from the rodless cavity of the push cylinder 9 to the oil tank, and if the one-way valve is not present, the returned oil will be blocked at the oil outlet of the pressure compensating valve 31.
In an alternative scheme of the embodiment, the propulsion speed control module 2 further comprises a two-position four-way reversing valve 22, a control port of the two-position four-way reversing valve 22 is connected with an oil inlet of the rotary motor 5, and the two-position four-way reversing valve 22 can be reversed according to the rotary pressure of the rotary motor 5 so as to control the cylinder rod of the propulsion cylinder 9 to propel or retract;
the set pressure of the two-position four-way reversing valve 22 is greater than the set pressure of the pilot proportional throttle valve 21.
When the rotation pressure continues to rise after the regulation by the throttling and speed reducing mode until the set pressure of the two-position four-way reversing valve 22 is reached, the system is proved to have great drill sticking risk, the two-position four-way reversing valve 22 is reversed under the action of the rotation pressure, and the propulsion cylinder 9 is retracted. After a period of time, after the rotation pressure is reduced, the two-position four-way reversing valve 22 is reset to the initial position, so that the propulsion cylinder 9 continues to propel, and the system automatically enters a drilling mode.
In an alternative of this embodiment, the anti-seize hydraulic control system further comprises a first pressure sensor 8, the first pressure sensor 8 being used for measuring the thrust pressure of the thrust cylinder 9;
the impact control module 1 further comprises a first electromagnetic directional valve 16 and a second electromagnetic directional valve 18, and the first electromagnetic directional valve 16 and the second electromagnetic directional valve 18 are electrically connected with the first pressure sensor 8;
the first electromagnetic directional valve 16 can be communicated with a load feedback port of the variable pump 7 and an oil inlet of the first proportional directional valve 14 before the reversing, and the first electromagnetic directional valve 16 can be used for connecting the load feedback port of the variable pump 7 between the first low-pressure overflow valve 12 and the first proportional directional valve 14 after the reversing;
the second electromagnetic directional valve 18 can connect the control port of the pilot proportional throttle valve 21 with the oil inlet of the rotary motor 5 before the direction change, and the second electromagnetic directional valve 18 can connect the control port of the pilot proportional throttle valve 21 between the first electromagnetic directional valve 16 and the load feedback port of the variable pump 7 after the direction change.
In a normal drilling mode, when a karst cave stratum is encountered, the propelling pressure is instantaneously reduced, the first pressure sensor 8 detects the condition of instantaneous drop of the propelling pressure and feeds back to the first electromagnetic directional valve 16, the second electromagnetic directional valve 18 and the third electromagnetic directional valve 34, the first electromagnetic directional valve 16 and the second electromagnetic directional valve 18 are simultaneously subjected to power supply and directional control, a load feedback port of the variable pump 7 is connected with the first low-pressure overflow valve 12 through the first electromagnetic directional valve 16, and the impact pressure is controlled by the first low-pressure overflow valve 12 and enters a low-impact pressure state. The pilot proportional throttle valve 21 is connected to the load feedback port of the variable pump 7 through the second electromagnetic directional valve 18, and the valve element opening of the pilot proportional throttle valve 21 is reduced accordingly, and the low propulsion speed state is entered. The electromagnetic reversing valve III 34 is reset after power failure, and the propelling pressure of the propelling oil cylinder 9 is controlled by the third low-pressure overflow valve 33 to enter a low propelling pressure state. That is, the system enters an operating state of low percussion pressure, low propulsion pressure and low propulsion speed until the rotation pressure rises to a steady state.
Similarly, the system judges that the rotation pressure rises to a stable state, after drilling is normal, the first electromagnetic directional valve 16 and the second electromagnetic directional valve 18 are simultaneously in power failure and direction change, the first proportional directional valve 14 and the first low-pressure overflow valve 12 are connected, and meanwhile, the pilot proportional throttle valve 21 is controlled by the rotation pressure of the rotation motor 5 in a recovery mode, namely, the anti-seizing hydraulic control system enters an opening mode. Further, if the top of the perforated mode plate is normal, the electromagnetic directional valve III 34 is electrified for direction change, and the system automatically enters a normal drilling mode.
When the drill tool needs to be replaced, the first electromagnetic reversing valve 16 is electrified to reverse, the rock drill 10 enters a low impact state, and the connecting sleeve and the drill bit can be vibrated loose, so that the efficiency of replacing the drill tool is improved.
In an alternative scheme of the embodiment, the impact control module 1 further comprises a fourth electromagnetic directional valve 17 and a hydraulic control directional valve 15, the fourth electromagnetic directional valve 17 can be communicated with an oil inlet of the rotary motor 5 and a second electromagnetic directional valve 18 before direction change, the fourth electromagnetic directional valve 17 can be communicated with the fourth electromagnetic directional valve and an oil tank after direction change, and a control port of the two-position four-way directional valve 22 is connected between the fourth electromagnetic directional valve 17 and the second electromagnetic directional valve 18. Therefore, the anti-blocking function can be started before the electromagnetic directional valve IV 17 is switched, and the anti-blocking function can be stopped after the electromagnetic directional valve IV 17 is switched, so that the starting or stopping of the anti-blocking function can be controlled by controlling the electromagnetic directional valve IV 17 to be powered on or powered off.
The control port of the pilot operated directional valve 15 is connected with the load feedback port of the variable pump 7 to connect or disconnect the oil tank and the oil inlet of the first proportional directional valve 14.
When the advancing pressure of the rock drill 10 does not reach the advancing pressure of the tapping mode, the valve core of the hydraulic control reversing valve 15 is in an initial state, namely the oil inlet of the first proportional reversing valve 14 is communicated with the oil tank, and the impact is not started because the pressure of the load feedback port of the variable pump 7 is zero at the moment. When the rock drilling operation is performed, the pressure of the load feedback port of the variable pump 7 is increased, and the hydraulic reversing valve can be controlled to reverse, namely, the hydraulic reversing valve cuts off the connection relationship between the oil tank and the oil inlet of the first proportional reversing valve 14, so that the impact control is started. This function is an idle strike prevention function, which prevents the influence of idle impact on the life of the internal components of the rock drill 10 and improves the life of the rock drill 10.
In the alternative scheme of this embodiment, the anti-seize control system further includes a damping hole 6, and a bypass of the variable pump 7, a damping hole 6 is provided between the oil inlet of the thrust cylinder 9 and the first proportional directional valve 14, and between the oil inlet of the thrust cylinder 9 and the third proportional directional valve 35. Through setting up damping hole 6, can effectively remove the fluctuation crest of system to make this anti-sticking borer control system's pressure more stable, in order to play the effect of steady voltage.
Optionally, a damping hole 6 is arranged between the electromagnetic directional valve IV 17 and the rotary motor 5; the control opening of the third proportional directional valve 35 is also provided with a damping orifice 6.
In an alternative to this embodiment, the variable displacement pump 7 is a load sensitive pump. The load-sensitive pump is able to provide only the necessary flow to maintain system operation at the operating pressure required by the load, and to respond correctly to changes in the flow pressure requirements. That is, the drill clamping risk of different rock formations can be aimed at, the load-sensitive pump can give out continuously-changed impact pressure to match different working conditions, so that drill clamping accidents can be prevented in advance, the characteristic advantages of the load-sensitive pump can be fully exerted, and overflow energy loss is reduced.
Alternatively, the variable displacement pump 7 is a variable displacement plunger type load sensitive pump.
Optionally, the oil inlet of the variable pump 7, the oil outlet of the variable pump 7, the oil inlet of the rotary motor 5, the oil outlet of the rotary motor 5, the oil inlet of the pressure compensating valve 31, the oil outlet of the one-way valve and the two-position four-way reversing valve 22 are respectively connected through a three-position six-way electric reversing valve, so that the relation of oil inlet, oil return or interruption between the components and the oil tank can be realized.
Example two
The second embodiment provides a rock drilling apparatus, the second embodiment includes the anti-seizing hydraulic control system provided in the first embodiment, and technical features of the anti-seizing hydraulic control system disclosed in the first embodiment are also applicable to the first embodiment, and technical features of the anti-seizing hydraulic control system disclosed in the first embodiment are not repeated.
The existing equipment is divided into three types of full hydraulic rock drilling equipment, electrohydraulic rock drilling equipment and full computerized rock drilling equipment, and almost all control elements of the full hydraulic rock drilling equipment adopt pure hydraulic control elements as the name implies, so that the equipment has low automation degree, a hydraulic system is relatively complex, the requirements on equipment users are extremely high, the realization of anti-seizing drill rods is controlled by the pure hydraulic system, and the anti-seizing drill rod system is relatively simple.
The basic control elements of the full-computerized rock drilling equipment are all electric control hydraulic elements, which are relatively simple and very high in requirements on the hydraulic system, the logic functions of the rock drilling process are realized by electric control, the severe environment of rock drilling has great influence on the electric control system, and once the electric fault occurs, professional technicians are required for maintenance to perform troubleshooting, and the existing electric control anti-seizing technology is still immature, and the electric control system has relatively quick response but relatively poor reliability.
In summary, the electro-hydraulic rock drilling apparatus may better accommodate the advantages of both full hydraulic rock drilling apparatus and full computerized rock drilling apparatus, and thus, optionally, the rock drilling apparatus is an electro-hydraulic rock drilling apparatus. Specifically, the electrohydraulic rock drilling equipment is a computer-guided rock drilling trolley.
The rock drilling apparatus according to this embodiment has the advantages of the anti-seize hydraulic control system according to embodiment one, and the advantages of the anti-seize hydraulic control system according to embodiment one disclosed herein are not repeated here.
Finally, it should be noted that: the above embodiments are only for illustrating the technical solution of the present invention, and not for limiting the same; although the invention has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical scheme described in the foregoing embodiments can be modified or some or all of the technical features thereof can be replaced by equivalents; such modifications and substitutions do not depart from the spirit of the invention. Furthermore, those skilled in the art will appreciate that while some embodiments described herein include some features but not others included in other embodiments, combinations of features of different embodiments are meant to be within the scope of the invention and form different embodiments. For example, any of the claimed embodiments can be used in any combination. The information disclosed in this background section is only for enhancement of understanding of the general background of the invention and should not be taken as an acknowledgement or any form of suggestion that this information forms the prior art already known to a person skilled in the art.
Claims (10)
1. The anti-seize hydraulic control system is used for rock drilling equipment and is characterized by comprising an impact control module, a propulsion pressure control module, a propulsion speed control module, a variable pump, a rotary motor and a propulsion oil cylinder;
the impact control module comprises a first proportional reversing valve, the first proportional reversing valve is communicated with a load feedback port of the variable pump and an oil tank, and a pilot control port of the first proportional reversing valve is connected with an oil inlet of the propulsion oil cylinder;
the propulsion pressure control module comprises a third proportional reversing valve, the third proportional reversing valve is communicated with an oil inlet of the propulsion oil cylinder and the oil tank, and a pilot control port of the third proportional reversing valve is connected with an oil inlet of the rotary motor;
The propulsion speed control module comprises a pilot proportional throttle valve, the pilot proportional throttle valve is connected between the oil tank and an oil inlet of the propulsion oil cylinder, and a pilot control port of the pilot proportional throttle valve is connected with the oil inlet of the rotary motor.
2. The anti-seize hydraulic control system of claim 1, wherein said impact control module further comprises a first low pressure relief valve, an overflow port of said first low pressure relief valve communicating with said tank, an oil inlet of said first low pressure relief valve communicating between said tank and an oil outlet of said first proportional reversing valve;
The propulsion pressure control module further comprises a third low-pressure overflow valve, the third proportional reversing valve is connected between an oil inlet of the propulsion oil cylinder and an oil inlet of the third low-pressure overflow valve, and an overflow port of the third low-pressure overflow valve is communicated with the oil tank.
3. The anti-seize hydraulic control system as defined in claim 2, wherein,
The impact control module further comprises a first high-pressure overflow valve, and the first high-pressure overflow valve is connected between the oil tank and the other oil outlet of the first proportional reversing valve;
The propulsion pressure control module further comprises a third high-pressure overflow valve, an oil inlet of the third high-pressure overflow valve is connected between the oil inlet of the propulsion oil cylinder and the third proportional reversing valve, and an overflow port of the third high-pressure overflow valve is communicated with the oil tank;
The propulsion pressure control module further comprises an electromagnetic directional valve III, wherein the electromagnetic directional valve III is connected between the third high-pressure overflow valve and the third low-pressure overflow valve so as to connect or disconnect an oil inlet of the third high-pressure overflow valve and an oil inlet of the third low-pressure overflow valve;
The anti-seizing hydraulic control system further comprises a second pressure sensor, the second pressure sensor is used for measuring the rotation pressure of the rotation motor, and the electromagnetic directional valve III is electrically connected with the second pressure sensor.
4. The anti-seize hydraulic control system as defined in claim 2, wherein,
The propulsion pressure control module further comprises a pressure compensation valve and a one-way valve, wherein the pressure compensation valve is connected between the oil tank and the pilot proportional throttle valve;
an oil outlet of the one-way valve is connected with a valve port of the pressure compensation valve, which is close to the oil tank, and an oil inlet of the one-way valve is connected with a valve port of the pressure compensation valve, which is close to the oil inlet of the propulsion oil cylinder.
5. The anti-seize hydraulic control system of claim 4, wherein said propulsion speed control module further comprises a two-position four-way reversing valve, a control port of said two-position four-way reversing valve being connected to an oil inlet of said rotary motor, said two-position four-way reversing valve being capable of reversing according to a rotary pressure of said rotary motor to control a cylinder rod of said propulsion cylinder to propel or retract;
And the set pressure of the two-position four-way reversing valve is larger than that of the pilot proportional throttle valve.
6. The anti-seize hydraulic control system of claim 5, further comprising a first pressure sensor for measuring a thrust pressure of the thrust cylinder;
the impact control module further comprises a first electromagnetic directional valve and a second electromagnetic directional valve, and the first electromagnetic directional valve and the second electromagnetic directional valve are electrically connected with the first pressure sensor;
The first electromagnetic reversing valve can be communicated with a load feedback port of the variable pump and an oil inlet of the first proportional reversing valve before reversing, and the first electromagnetic reversing valve can be used for connecting the load feedback port of the variable pump between the first low-pressure overflow valve and the first proportional reversing valve after reversing;
The electromagnetic directional valve II can connect the control port of the pilot proportional throttle valve with the oil inlet of the rotary motor before reversing, and the control port of the pilot proportional throttle valve can be connected between the electromagnetic directional valve I and the load feedback port of the variable pump after reversing.
7. The anti-seize hydraulic control system of claim 6, wherein,
The impact control module further comprises a fourth electromagnetic reversing valve and a hydraulic control reversing valve, the fourth electromagnetic reversing valve can be communicated with an oil inlet of the rotary motor and the second electromagnetic reversing valve before reversing, the fourth electromagnetic reversing valve can be communicated with the second electromagnetic reversing valve and the oil tank after reversing, and a control port of the two-position four-way reversing valve is connected between the fourth electromagnetic reversing valve and the second electromagnetic reversing valve;
and a control port of the hydraulic control reversing valve is connected with a load feedback port of the variable pump so as to connect or disconnect the oil tank and an oil inlet of the first proportional reversing valve.
8. The anti-seize hydraulic control system of claim 1, further comprising a damping hole, wherein the damping hole is provided in the bypass of the variable pump, between the oil inlet of the thrust cylinder and the first proportional directional valve, and between the oil inlet of the thrust cylinder and the third proportional directional valve.
9. The anti-seize hydraulic control system as defined in claim 1, wherein,
The variable pump is a load-sensitive pump.
10. A rock drilling apparatus comprising an anti-seize hydraulic control system as claimed in any one of claims 1 to 9.
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| CN113153200A (en) * | 2021-04-01 | 2021-07-23 | 湖南创远智能发展有限责任公司 | Hydraulic rock drill electrohydraulic control system and method |
| CN114321060B (en) * | 2021-12-15 | 2024-05-24 | 中铁工程装备集团有限公司 | Automatic control valve group and control system for rock drilling |
| CN115559953B (en) * | 2022-10-20 | 2023-09-08 | 四川蓝海智能装备制造有限公司 | Drill rod-blocking-preventing hydraulic oil circuit structure of rock drill and hydraulic control method |
| CN116025330B (en) * | 2022-12-14 | 2023-09-22 | 四川蓝海智能装备制造有限公司 | Electric control type rock drill hydraulic control structure and control method for preventing drill rod from being blocked |
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