CN107620762B - Rock drill and hydraulic automatic control system thereof - Google Patents
Rock drill and hydraulic automatic control system thereof Download PDFInfo
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- CN107620762B CN107620762B CN201711022438.XA CN201711022438A CN107620762B CN 107620762 B CN107620762 B CN 107620762B CN 201711022438 A CN201711022438 A CN 201711022438A CN 107620762 B CN107620762 B CN 107620762B
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- 239000011435 rock Substances 0.000 title claims abstract description 78
- 239000003921 oil Substances 0.000 claims abstract description 196
- 230000008859 change Effects 0.000 claims abstract description 15
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 7
- 238000011010 flushing procedure Methods 0.000 claims description 7
- 238000009527 percussion Methods 0.000 claims description 4
- 238000005553 drilling Methods 0.000 description 25
- 238000000034 method Methods 0.000 description 5
- 230000009471 action Effects 0.000 description 3
- 230000000903 blocking effect Effects 0.000 description 3
- 238000010276 construction Methods 0.000 description 3
- 230000006837 decompression Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 230000006978 adaptation Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 238000005422 blasting Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000003116 impacting effect Effects 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
- 239000002893 slag Substances 0.000 description 1
- 230000000087 stabilizing effect Effects 0.000 description 1
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Abstract
The invention discloses a hydraulic automatic control system of a rock drill, which comprises a pilot control oil source, an impact oil source, a rotary oil source, a propulsion oil source, an impact device, a rotary motor and a propulsion oil cylinder, wherein a propulsion throttle valve is arranged between a rod cavity of the propulsion oil cylinder and the propulsion oil source, two hydraulic oil ports of a first hydraulic proportional reversing valve are respectively communicated with two ends of the propulsion throttle valve, one working oil port of the first hydraulic proportional reversing valve is communicated with a pipeline between the pilot control oil source and the impact power hydraulic proportional reversing valve, and the first hydraulic proportional reversing valve can switch working positions according to pressure changes at two ends of the propulsion throttle valve so as to change the on-off states of the first hydraulic proportional reversing valve and an oil tank. The geological state is accurately obtained through pressure change of hydraulic oil, corresponding change is further made by accurate and rapid control equipment, automatic control is realized through hydraulic control, and clamping can be stably and efficiently prevented. The invention also discloses a rock drill comprising the hydraulic automatic control system.
Description
Technical Field
The invention relates to the field of rock drilling equipment, in particular to a hydraulic automatic control system of a rock drill. In addition, the invention also relates to a rock drill comprising the hydraulic automatic control system.
Background
The hydraulic rock drill is important hard rock drilling equipment in the tunnel construction of the modern drilling and blasting method, and occupies the dominant position of the rock drill market due to the advantages of high rock drilling speed, high rock drilling power, high construction efficiency, small noise radiation, easy realization of automation and the like. The hydraulic rock drill is a rotary impact drilling rock drill, when the rock drill performs rock drilling operation, the rock drill has small pushing pressure to generate idle drilling, so that the rock drilling efficiency is reduced, and the service life of the rock drill is shortened; when the pushing pressure of the rock drill is too large, the drill bit is easy to deviate from the target position, and the abrasion of the drill bit is accelerated. In addition, the rock drill drives a plurality of drill rods to perform deep and long hole rock drilling operation, rock geological conditions are complex and changeable, such as uneven texture, cracks, dissolved rock and the like, the drill bit is easy to deviate from a drilling target track due to mechanical non-uniformity of the rock, so that the phenomenon of drill rod blocking is caused, meanwhile, the drill rod blocking is easy to occur due to unsmooth discharge of rock slag in drilling, and therefore, the randomness of the phenomenon of drill rod blocking is strong. In order to meet the rock drilling operation under various rock geological conditions, the hydraulic control system of the rock drill must have the capabilities of automatically drilling rock and preventing drill rod jamming according to geomechanical conditions, and particularly must have the capability of predicting and processing the condition of the drill rod jamming in advance.
In the prior art, a switch control method is adopted, and because of the switch control mode, the propelling force cannot be changed according to the change of the rotation resistance moment, the anti-jamming effect is poor, and particularly when the drilling operation is performed in the rock drilling in the rock stratum with poor geological conditions, the propelling reversing loop is always frequently reversed, and the drilling efficiency is low.
Therefore, how to provide a hydraulic automatic control system capable of stably and efficiently preventing the drill rod from being jammed is a technical problem that a person skilled in the art needs to solve at present.
Disclosure of Invention
The invention aims to provide a hydraulic automatic control system of a rock drill, which can stably and efficiently prevent drill rod clamping. Another object of the present invention is to provide a rock drill including the above hydraulic automatic control system, which is capable of stably and efficiently preventing seizing.
In order to solve the technical problems, the invention provides a hydraulic automatic control system of a rock drill, which comprises a pilot control oil source, an impact oil source, a rotary oil source, a propulsion oil source, an impact device, a rotary motor and a propulsion oil cylinder, wherein an impact power hydraulic control valve is arranged between an oil outlet of the impact oil source and an oil inlet of the impact device, a hydraulic control port of the impact power hydraulic control valve is communicated with the pilot control oil source, a propulsion throttle valve is arranged between a rod cavity of the propulsion oil cylinder and the propulsion oil source, two ends of the propulsion throttle valve are respectively communicated with two hydraulic control oil ports of a first hydraulic control proportional reversing valve, one working oil port of the first hydraulic control proportional reversing valve is communicated with a pipeline between the pilot control oil source and the impact power hydraulic control valve, the other working oil port of the first hydraulic control proportional reversing valve is communicated with an oil tank, and the first hydraulic control proportional reversing valve can switch working positions according to pressure changes at two ends of the propulsion throttle valve so as to change the on-off state of the first hydraulic control proportional reversing valve and the oil tank.
Preferably, a rotary throttle valve is arranged between an oil outlet of the rotary oil source and an oil inlet of the rotary motor, two ends of the rotary throttle valve are respectively communicated with two hydraulic control oil ports of a second hydraulic control proportional reversing valve, an oil inlet and an oil return port of the second hydraulic control proportional reversing valve are respectively communicated with the propulsion oil source, two working oil ports of the second hydraulic control proportional reversing valve are respectively communicated with a rod cavity and a rodless cavity of the propulsion oil cylinder, and the second hydraulic control proportional reversing valve can switch working positions according to pressure changes at two ends of the rotary throttle valve so as to change the working state of the propulsion oil cylinder.
Preferably, a pilot-started electric control reversing valve, a first three-way hydraulic control pressure reducing valve and a first throttle valve are further arranged between the pilot control oil source and the impact power hydraulic control valve in sequence, a hydraulic control port of the first three-way hydraulic control pressure reducing valve is communicated with a rodless cavity of the propulsion oil cylinder, a pilot pressure relief electric control reversing valve and a low-flushing opening overflow valve which are used for being communicated with an oil tank are further arranged at an outlet of the first throttle valve, and a low-pressure overflow valve is further arranged between the first hydraulic control proportional reversing valve and the oil tank.
Preferably, a second throttle valve, an auxiliary hydraulic control proportional reversing valve and a first auxiliary electric control reversing valve are sequentially arranged between a hydraulic control port at one end of the second hydraulic control proportional reversing valve and one end of the rotary throttle valve, and a second three-way hydraulic control pressure reducing valve and a second auxiliary electric control reversing valve are sequentially arranged between a hydraulic control port at the other end of the second hydraulic control proportional reversing valve and the other end of the rotary throttle valve.
Preferably, a third three-way hydraulic control pressure reducing valve is arranged between the rodless cavity of the propulsion oil cylinder and the second hydraulic control proportional reversing valve.
Preferably, the impact device comprises an impact cylinder, an impact reversing valve and an energy accumulator.
Preferably, the first hydraulic control proportional reversing valve is specifically a two-position two-way hydraulic control proportional reversing valve, the first hydraulic control proportional reversing valve is specifically a three-position four-way hydraulic control proportional reversing valve, the pilot starting electric control reversing valve is specifically a two-position three-way electric control reversing valve, the pilot pressure relief electric control reversing valve is specifically a two-position two-way electric control reversing valve, the auxiliary hydraulic control proportional reversing valve is specifically a two-position two-way hydraulic control proportional reversing valve, and the first auxiliary electric control reversing valve and the second auxiliary electric control reversing valve are specifically two-position three-way electric control reversing valves.
Preferably, the propulsion oil source is also communicated with the propulsion oil cylinder through an electric control proportional reversing valve.
Preferably, the electric control proportional reversing valve is specifically a three-position four-way electric control proportional reversing valve.
The invention also provides a rock drill, which comprises a hydraulic automatic control system and is characterized in that the hydraulic automatic control system is specifically any one of the hydraulic automatic control systems.
The invention provides a hydraulic automatic control system of a rock drill, which comprises a pilot control oil source, an impact oil source, a rotary oil source, a propulsion oil source, an impact device, a rotary motor and a propulsion oil cylinder, wherein an impact power hydraulic control valve is arranged between an oil outlet of the impact oil source and an oil inlet of the impact device, a hydraulic control port of the impact power hydraulic control valve is communicated with the pilot control oil source, a propulsion throttle valve is arranged between a rod cavity of the propulsion oil cylinder and the propulsion oil source, two ends of the propulsion throttle valve are respectively communicated with two hydraulic control oil ports of a first hydraulic control proportional reversing valve, one working oil port of the first hydraulic control proportional reversing valve is communicated with a pipeline between the pilot control oil source and the impact power hydraulic control valve, the other working oil port of the first hydraulic control proportional reversing valve is communicated with an oil tank, and the first hydraulic control proportional reversing valve can switch working positions according to pressure changes at two ends of the propulsion throttle valve so as to change the on-off state of the first hydraulic control proportional reversing valve and the oil tank.
When the hole geology is encountered in the rock drilling process, the extending speed of the pushing oil cylinder is far greater than the normal pushing extending speed, the pressure difference at two ends of the pushing throttle valve is increased, the first hydraulic control proportional reversing valve is controlled to open the communicating oil tank, hydraulic oil in the pilot control oil source flows back to the oil tank, the pressure at the hydraulic control port of the impact power hydraulic control valve is reduced, the oil supply to the impact device is reduced, the impact pressure is reduced, the rock drill is in a state of slightly opening a guide hole, the opening of the first hydraulic control proportional reversing valve is gradually reduced when the drill bit collides with the next wall surface, the impact pressure is increased, and the rock drill is restored to a normal drilling and rock drilling state.
The geological state is accurately obtained through pressure change of hydraulic oil, corresponding change is further made by accurate and rapid control equipment, automatic control is realized through hydraulic control, and clamping can be stably and efficiently prevented.
The invention also provides a rock drill comprising the hydraulic automatic control system, and the rock drill has the same technical effects as the hydraulic automatic control system, and the technical effects are not described in detail herein.
Drawings
Fig. 1 is a hydraulic schematic diagram of an embodiment of the hydraulic automatic control system provided by the present invention.
Detailed Description
The core of the invention is to provide a hydraulic automatic control system of a rock drill, which can stably and efficiently prevent drill rod clamping. Another core of the present invention is to provide a rock drill including the above hydraulic automatic control system, which can stably and efficiently prevent seizing.
In order to better understand the aspects of the present invention, the present invention will be described in further detail with reference to the accompanying drawings and detailed description.
Referring to fig. 1, fig. 1 is a hydraulic schematic diagram of an embodiment of a hydraulic automatic control system according to the present invention.
The invention provides a hydraulic automatic control system of a rock drill, which comprises a pilot control oil source 1, an impact oil source 2, a rotary oil source 3, a pushing oil source 4, an impact device 5, a rotary motor 6 and a pushing oil cylinder 7, wherein the impact device 5 comprises an impact oil cylinder, an impact reversing valve and an energy accumulator. A total hydraulic pump and tank may also be used as the source of oil.
An impact power hydraulic control valve 8 is arranged between an oil outlet of the impact oil source 2 and an oil inlet 5c of the impact device 5, a hydraulic control port 8c of the impact power hydraulic control valve 8 is communicated with a pilot control oil source 1, a propulsion throttle valve 9 is arranged between a rod cavity of a propulsion oil cylinder 7 and the propulsion oil source 4, two ends of the propulsion throttle valve 9 are respectively communicated with two hydraulic control ports of a first hydraulic control proportional reversing valve 10, one working port 10a of the first hydraulic control proportional reversing valve 10 is communicated with a pipeline between the pilot control oil source 1 and the impact power hydraulic control valve 8, the other working port 10b of the first hydraulic control proportional reversing valve 10 is communicated with an oil tank, and the first hydraulic control proportional reversing valve 10 can switch working positions according to pressure changes at two ends of the propulsion throttle valve 9 so as to change the on-off state of the first hydraulic control proportional reversing valve 10 and the oil tank.
A rotary throttle valve 11 is arranged between an oil outlet of the rotary oil source 3 and an oil inlet 6a of the rotary motor 6, two ends of the rotary throttle valve 11 are respectively communicated with two hydraulic oil ports of a second hydraulic control proportional reversing valve 12, an oil inlet 12p and an oil return port 12t of the second hydraulic control proportional reversing valve 12 are respectively communicated with the pushing oil source 4, one working oil port 12a of the second hydraulic control proportional reversing valve 12 is communicated with a rod cavity of the pushing oil cylinder 7, the other working oil port 12b of the second hydraulic control proportional reversing valve 12 is communicated with a rodless cavity of the pushing oil cylinder 7, and the second hydraulic control proportional reversing valve 12 can switch working positions according to pressure changes at two ends of the rotary throttle valve 11 so as to change the working state of the pushing oil cylinder 7.
In order to realize accurate control, a pilot-started electric control reversing valve 13, a first three-way hydraulic control pressure reducing valve 14 and a first throttle valve 15 are further arranged between the pilot control oil source 1 and the impact power hydraulic control valve 8 in sequence, a hydraulic control port 14c of the first three-way hydraulic control pressure reducing valve 14 is communicated with a rodless cavity of the propulsion cylinder 7, a pilot pressure relief electric control reversing valve 16 and a low-flushing opening overflow valve 17 which are used for communicating an oil tank are further arranged at an outlet 15b of the first throttle valve 15, and a low-pressure overflow valve 18 is further arranged between the first hydraulic control proportional reversing valve 10 and the oil tank.
A second throttle valve 19, an auxiliary hydraulic control proportional reversing valve 20 and a first auxiliary electric control reversing valve 21 are sequentially arranged between a hydraulic control port at one end of the second hydraulic control proportional reversing valve 12 and one end 11b of the rotary throttle valve 11, and a second three-way hydraulic control pressure reducing valve 22 and a second auxiliary electric control reversing valve 23 are sequentially arranged between a hydraulic control port at the other end of the second hydraulic control proportional reversing valve 12 and the other end 11a of the rotary throttle valve 11. A third three-way hydraulic control pressure reducing valve 24 is arranged between the rodless cavity of the propulsion cylinder 7 and the second hydraulic control proportional reversing valve 12.
The valves are to better realize the functions of the rock drill, the valves can be increased or decreased or changed according to the situation, specifically, the first hydraulic control proportional reversing valve 10 is a two-position two-way hydraulic control proportional reversing valve, the first hydraulic control proportional reversing valve 10 is a three-position four-way hydraulic control proportional reversing valve, the pilot starting electric control reversing valve 13 is a two-position three-way electric control reversing valve, the pilot pressure relief electric control reversing valve 16 is a two-position two-way electric control reversing valve, the auxiliary hydraulic control proportional reversing valve 20 is a two-position two-way hydraulic control proportional reversing valve, the first auxiliary electric control reversing valve 21 and the second auxiliary electric control reversing valve 23 are two-position three-way electric control reversing valves, and the types of the valves can be adjusted according to the situation.
On the basis of the hydraulic automatic control system provided by the specific embodiments, the propulsion oil source 4 is also communicated with the propulsion oil cylinder 7 through an electric control proportional reversing valve 25, and the propulsion oil cylinder is a three-position four-way electric control proportional reversing valve.
When the rock drill is in a non-working state, the pilot-started electric control reversing valve 13 is not electrified, pressure oil of a pilot control oil source cannot flow to the hydraulic control port 8c of the impact power hydraulic control valve 8 in a decompression way through the first three-way hydraulic control decompression valve 14, at the moment, the working oil port 13a of the pilot-started electric control reversing valve 13 is communicated with the oil return port 13t and returns to the oil tank, the pressure of the hydraulic control port 8c of the impact power hydraulic control valve 8 is close to zero, and the system is in a low-flushing state.
When the rock drill is in a drilling state, pressure oil of a pilot control oil source flows to the first three-way hydraulic control pressure reducing valve 14 after the pilot starts the electric control reversing valve 13, the pressure of the rodless cavity side of the propulsion cylinder 7 is fed back to the hydraulic control port 14c of the first three-way hydraulic control pressure reducing valve 14, and the output pressure of the first three-way hydraulic control pressure reducing valve 14 is determined by the pressure of the hydraulic control port 14 c. The pressure oil is depressurized by the first three-way pilot operated depressurization valve 14 and then flows to the pilot operated port 8c of the percussion power pilot operated valve 8 through the first throttle valve 15. The hydraulic control valve 8 of the impact power is opened, so that the pressure oil of the impact oil source enters the impact device 5, and the impact operation is realized.
When the rock drill is in a light opening stage, the impact pressure requirement is low, at the moment, the pilot pressure relief electric control reversing valve 16 is electrified, and the pressure oil of the pilot control oil source 1 flows back to the oil tank from the low-flushing opening overflow valve 17 after passing through the pilot starting electric control reversing valve 13, the first three-way hydraulic control reducing valve 14, the first throttle valve 15 and the pilot pressure relief electric control reversing valve 16, so that the rock drill is in a low-flushing guide hole state.
According to the rock drill impact system, the 10-a port of an electromagnetic directional valve 10 is connected to the 17-p port of an external control pressure reducing valve 17, the external control port 17-c of the external control pressure reducing valve 17 is connected to a rodless cavity oil way of a thrust cylinder, the 17-a port of the pressure reducing valve 17 is connected with the 18-a port of a throttle 18, the 18-b port of the throttle 18 is respectively connected with the 11-a port of the electromagnetic directional valve 11 and the 12-a port of a hydraulic control proportional directional valve 12, the 11-b port of the electromagnetic directional valve 11 is connected with the 4-a port of a low flushing overflow valve 4, the 12-b port of the hydraulic control proportional directional valve 12 is connected with the 5-a port of the low pressure overflow valve 5, and the 10-t port of the electromagnetic directional valve 10 is connected with the 11-t port of the electromagnetic directional valve 11 and the 12-t port of the hydraulic control proportional directional valve 12 and is connected with the oil tank together.
When the rock drill bit drills into a cavity, the drill bit is quickly pushed until the rock wall surface in the cavity is uneven due to small front load of the drill bit, a component force is generated in the radial direction after the drill bit collides with the rock wall surface of the cavity, and the slender drill rod with low structural rigidity is bent and deformed under the action of the radial load, so that the drill bit deviates from a preset drilling track. When the drill bit deviates from the preset track to drill for a certain depth, the bent drill rod is clamped and deformed, and at the moment, the drill rod cannot be pushed and cannot be retracted, namely, the clamping phenomenon is generated. When the hole geology is encountered, the extending speed of the pushing cylinder 7 is far greater than the normal pushing extending speed, at the moment, the pressure difference between the upper and the lower stream of the pushing throttle valve 9 is increased, the upper and the lower stream pressure are respectively fed back to the two ends of the first hydraulic control proportional reversing valve 10, the first hydraulic control proportional reversing valve 10 is driven to be opened gradually, at the moment, the pressure oil which originally flows to the hydraulic control port 8c of the impact power hydraulic control valve 8 flows back to the oil tank through the low pressure overflow valve 18, the opening degree of the impact power hydraulic control valve 8 is reduced, hydraulic oil cannot enter the impact device 5, the impact pressure is reduced, and the rock drill is in a state of slightly opening the guide hole. When the drill bit collides with the next wall surface, the load acting on the drill bit is restored to be larger, the pressure difference between the upper and the lower stream of the propelling throttle valve 9 is reduced, the first hydraulic control proportional reversing valve 10 is driven to be gradually closed, the pressure at the hydraulic control port 8c of the impact power hydraulic control valve 8 is restored to be normal, the impact pressure is gradually increased, and the rock drill is slowly restored to be in a normal drilling and rock drilling state.
The pressure oil supplied from the rotary oil source 3 flows through the rotary throttle 11 to the inlet 6a of the rotary motor 6 and directly flows to the oil tank through the outlet 6b of the rotary motor 6. The load of the rotary motor 6 is fed back to the second hydraulic control proportional reversing valve 12 through the pressure difference between the front and the rear of the rotary throttle valve 11, so that the second hydraulic control proportional reversing valve 12 automatically controls the opening of the second hydraulic control proportional reversing valve 12 according to the load of the rotary motor 6, and the control function of the inflow of the thrust cylinder 7 is realized.
An oil port 11a at one end of the rotary throttle valve 11 is connected with an oil inlet 23p of a second auxiliary electric control reversing valve 23, an oil return port 23t of the second auxiliary electric control reversing valve 23 is connected to an oil tank together with the oil return port 11t of the rotary throttle valve 11, a working oil port 23a of the second auxiliary electric control reversing valve 23 is connected to an oil inlet of a second three-way hydraulic control pressure reducing valve 22, an oil return port of the second three-way hydraulic control pressure reducing valve 22 is connected to the oil tank, and a working oil port of the second three-way hydraulic control pressure reducing valve 22 is connected to an end hydraulic control port 12 II of the second hydraulic control proportional reversing valve 12.
The other end oil port 11b of the rotary throttle valve 11 is connected to an oil inlet 21p of a first auxiliary electric control reversing valve 21, a working oil port 21a of the first auxiliary electric control reversing valve 21 is connected with one working oil port 20a of an auxiliary hydraulic control proportional reversing valve 20, the other working oil port 20b of the auxiliary hydraulic control proportional reversing valve 20 is connected with one oil port 19a of a second throttle valve 19, and the other oil port 19b of the second throttle valve 19 is respectively connected with the other end hydraulic control port 12I of the rotary throttle valve 12 and one working oil port of a throttle, and the other working oil port of the throttle is connected with an oil tank. The components form a hydraulic bridge type loop and play a role in stabilizing the pressure of the hydraulic control port of the second hydraulic control proportional reversing valve 12.
When the load of the rotary motor 6 is reduced, the speed of the rotary motor is increased, the oil passing through the rotary throttle valve 11 generates a larger pressure difference in front and back of the rotary throttle valve, at this time, the pressure oil at the upstream port 11a of the rotary throttle valve 11 acts on the II-end pilot port of the second hydraulic control proportional reversing valve 12 through each valve, the pressure value of the pressure oil is larger than the pressure value of the I-end pilot port after throttling, the second hydraulic control proportional reversing valve 12 is in a II-end connection state, the oil in the propulsion loop flows into the oil inlet 24p of the third three-way hydraulic control reducing valve 24 through the oil inlet 12b after flowing into the oil inlet 12p of the second hydraulic control proportional reversing valve 12, the oil flows into the rodless cavity of the propulsion oil cylinder 7 through the 24a after being reduced in pressure, and the oil with the rod cavity flows into the other working oil inlet 12a of the second hydraulic control proportional reversing valve 12 after flowing into the propulsion throttle valve 9 in the oil return path, and flows back into the oil tank from the oil return port 12 t.
When the load of the rotary motor 6 is very large and the rotation speed is close to zero, the oil passing amount of the rotary throttle valve 11 is small, so that the front-rear pressure difference is small, at the moment, the pressure oil at the upstream interface 11a of the rotary throttle valve 11 is decompressed by each valve and acts on the II-end pilot port of the second hydraulic control proportional reversing valve 12, the value of the pressure oil is smaller than the pressure value of the I-end pilot port after throttling, the second hydraulic control proportional reversing valve 12 is in an I-end connection state, the oil in the propulsion loop flows to the rod cavity of the propulsion cylinder 7 through the other working oil port 12a port of the second hydraulic control proportional reversing valve 12, and the oil in the rodless cavity flows back to the 12b port of the second hydraulic control proportional reversing valve 12 after flowing through the one-way valve of the third three-way hydraulic control decompression valve 24 and flows back to the oil tank from the oil return port 12t of the second hydraulic control proportional reversing valve 12.
And the valve core of the second hydraulic control proportional reversing valve 12 is designed to have a certain overlapping degree, namely, no oil passes through a small section of the valve core deviated from the middle position. When the rock drill is fast stuck, the pushing cylinder 7 can not be pushed forward any more. But the drill bit is continuously impacting the rock wall surface, the rock wall surface in front of the drill bit of the rock drill is rigid, rock is continuously peeled off in the continuous impact process of the drill bit, the contact surface between the front end of the drill bit and the rock wall surface is continuously reduced after rock peeling, the rotary friction resistance moment of the rock drill is continuously reduced, and the rotary motor 6 of the rock drill is quickly rotated in a normal working state, so that the rock drill cannot be blocked.
In order to ensure that the pushing cylinder 7 can also realize telescopic action when the rotary motor of the rock drill does not rotate, an electric control proportional reversing valve 25 with a median function of O is connected in parallel in a pushing loop, one working oil port 25a of the electric control proportional reversing valve 25 is communicated with a rodless cavity of the pushing cylinder 7, the other working oil port 25b of the electric control proportional reversing valve 25 is communicated with a rod cavity of the pushing cylinder 7, and when the rock drill performs normal drilling operation, the electric control proportional reversing valve 25 is in the median position, and when other requirements exist, the electric control proportional reversing valve 25 is in other working positions.
The hydraulic automatic control system of the rock drill with the proportional function controls the opening of the second hydraulic proportional reversing valve 12 by utilizing the pressure difference generated when the rotary throttle valve 11 throttles, and when the rotary load is small, the rotating speed of the rotary motor 6 is high, the flow passing through the rotary throttle valve 11 is large, and the pressure difference before and after the rotary throttle valve 11 is also increased. The pressures at the front side and the rear side of the rotary throttle valve 11 in the oil way of the rotary motor 6 of the rock drill are fed back to the valve core of the second hydraulic control proportional reversing valve 12 and reach force balance with a linear spring in the second hydraulic control proportional reversing valve 12, so that the opening of the valve core is in proportional relation with the pressure difference at the front end and the rear end of the rotary throttle valve 11; the third three-way hydraulic control reducing valve 24 in the oil way of the non-cavity rod side of the propulsion oil cylinder 7 controls the pressure of the non-rod cavity of the propulsion oil cylinder 7 to be kept at a certain value, and under the condition that the front pressure of the second hydraulic control proportional reversing valve 12 is also fixed, the second hydraulic control proportional reversing valve 12 and the third three-way hydraulic control reducing valve 24 are made to act together to form a hydraulic control proportional reversing valve with a pressure compensation function, so that the function of proportionally controlling the propulsion speed according to the front-rear pressure difference of the rotary throttle valve 11 in the circuit of the rotary motor 6 is realized; in order to effectively avoid the situation that a rock drill rapidly advances in a cavity and collides with the wall surface of the cavity in the cavity to enable a drill bit to deviate from a target track under the action of radial external force, a pushing throttle valve 9 is additionally arranged in a pipeline on the side of a rod cavity of a pushing oil cylinder 7, pressure is fed back to a first hydraulic control proportional reversing valve 10 from the upper and lower streams of the pushing throttle valve 9, impact pressure change is continuously controlled according to the pushing speed, so that a guide hole is drilled on the wall surface of the cavity with low impact pressure when the drill bit collides with the wall surface of the cavity, and drill rods pass through the cavity and drill along the direction of the guide hole, thereby avoiding the phenomenon of drill bit jamming caused by deviation of the drill bit from the target track. In the specific embodiment of the invention, all the hydraulic valves are standard hydraulic valves, no special hydraulic valve is arranged, the system construction is easy to realize, and the cost is low.
In addition to the hydraulic automatic control system, the specific embodiment of the invention also provides a rock drill comprising the hydraulic automatic control system, and the structure of other parts of the rock drill is referred to the prior art, and is not repeated herein.
The rock drill and the hydraulic automatic control system thereof provided by the invention are described in detail above. The principles and embodiments of the present invention have been described herein with reference to specific examples, the description of which is intended only to facilitate an understanding of the method of the present invention and its core ideas. It should be noted that it will be apparent to those skilled in the art that various modifications and adaptations of the invention can be made without departing from the principles of the invention and these modifications and adaptations are intended to be within the scope of the invention as defined in the following claims.
Claims (9)
1. The hydraulic automatic control system of the rock drill comprises a pilot control oil source (1), an impact oil source (2), a rotary oil source (3), a propulsion oil source (4), an impact device (5), a rotary motor (6) and a propulsion oil cylinder (7), and is characterized in that an impact power hydraulic control valve (8) is arranged between an oil outlet of the impact oil source (2) and an oil inlet of the impact device (5), a hydraulic control port of the impact power hydraulic control valve (8) is communicated with the pilot control oil source (1), a propulsion throttle valve (9) is arranged between a rod cavity of the propulsion oil cylinder (7) and the propulsion oil source (4), two hydraulic control ports of a first hydraulic control proportional reversing valve (10) are respectively communicated at two ends of the propulsion throttle valve (9), one working port of the first hydraulic control proportional reversing valve (10) is communicated with a pipeline between the pilot control oil source (1) and the impact power hydraulic control valve (8), the other working port of the first hydraulic control proportional valve (10) is communicated with an oil tank, and the two ends of the first hydraulic control proportional reversing valve (10) can change the working state according to the change of the on-off state of the first hydraulic control reversing valve (10);
the hydraulic control system is characterized in that a pilot-started electric control reversing valve (13), a first three-way hydraulic control pressure reducing valve (14) and a first throttle valve (15) are further sequentially arranged between the pilot control oil source (1) and the impact power hydraulic control valve (8), a hydraulic control port of the first three-way hydraulic control pressure reducing valve (14) is communicated with a rodless cavity of the propulsion oil cylinder (7), a pilot pressure relief electric control reversing valve (16) and a low-flushing opening overflow valve (17) which are used for being communicated with an oil tank are further arranged at an outlet of the first throttle valve (15), and a low-pressure overflow valve (18) is further arranged between the first hydraulic control proportional reversing valve (10) and the oil tank.
2. The hydraulic automatic control system according to claim 1, characterized in that a rotary throttle valve (11) is arranged between an oil outlet of the rotary oil source (3) and an oil inlet of the rotary motor (6), two hydraulic oil ports of a second hydraulic proportional reversing valve (12) are respectively communicated with two ends of the rotary throttle valve (11), an oil inlet and an oil return port of the second hydraulic proportional reversing valve (12) are respectively communicated with the propulsion oil source (4), two working oil ports of the second hydraulic proportional reversing valve (12) are respectively communicated with a rod cavity and a rodless cavity of the propulsion oil cylinder (7), and the second hydraulic proportional reversing valve (12) can switch working positions according to pressure changes at two ends of the rotary throttle valve (11) so as to change the working state of the propulsion oil cylinder (7).
3. The hydraulic automatic control system according to claim 2, wherein a second throttle valve (19), an auxiliary hydraulic control proportional reversing valve (20) and a first auxiliary electric control reversing valve (21) are sequentially arranged between a hydraulic control port at one end of the second hydraulic control proportional reversing valve (12) and one end of the rotary throttle valve (11), and a second three-way hydraulic control pressure reducing valve (22) and a second auxiliary electric control reversing valve (23) are sequentially arranged between a hydraulic control port at the other end of the second hydraulic control proportional reversing valve (12) and the other end of the rotary throttle valve (11).
4. A hydraulic automatic control system according to claim 3, characterized in that a third three-way pilot operated relief valve (24) is arranged between the rodless chamber of the propulsion cylinder (7) and the second pilot operated proportional reversing valve (12).
5. The hydraulic automatic control system according to claim 4, characterized in that the percussion device (5) comprises a percussion cylinder, a percussion reversing valve and an accumulator.
6. The hydraulic automatic control system according to claim 5, wherein the first pilot-operated proportional directional valve (10) is a two-position two-way pilot-operated proportional directional valve, the first pilot-operated proportional directional valve (10) is a three-position four-way pilot-operated proportional directional valve, the pilot-operated electrically controlled directional valve (13) is a two-position three-way electrically controlled directional valve, the pilot-operated pressure relief electrically controlled directional valve (16) is a two-position two-way electrically controlled directional valve, the auxiliary pilot-operated proportional directional valve (20) is a two-position two-way pilot-operated proportional directional valve, and the first auxiliary electrically controlled directional valve (21) and the second auxiliary electrically controlled directional valve (23) are two-position three-way electrically controlled directional valves.
7. The hydraulic automatic control system according to any one of claims 1 to 6, characterized in that said source of propulsion oil (4) is also connected to said propulsion cylinder (7) through an electronically controlled proportional reversing valve (25).
8. The hydraulic automatic control system according to claim 7, characterized in that said electronically controlled proportional directional valve (25) is in particular a three-position four-way electronically controlled proportional directional valve.
9. Rock drill comprising an automatic hydraulic control system, characterized in that the automatic hydraulic control system is in particular according to any one of claims 1 to 8.
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| CN109236764B (en) * | 2018-12-10 | 2019-03-22 | 中国铁建重工集团有限公司 | The impulsive control hydraulic system of drill jumbo |
| CN109541678B (en) * | 2018-12-21 | 2023-12-12 | 中国铁建重工集团股份有限公司 | Earthquake source device for continuously adjusting impact frequency by earthquake method |
| CN110242628B (en) * | 2019-07-24 | 2024-05-17 | 湖南五新隧道智能装备股份有限公司 | Anti-seizing hydraulic control system and rock drilling equipment |
| CN112727818B (en) * | 2020-12-25 | 2023-03-21 | 中铁工程装备集团隧道设备制造有限公司 | Hydraulic control system of rock drill |
| CN113356755B (en) * | 2021-06-03 | 2024-04-26 | 广东三水合肥工业大学研究院 | Hydraulic impact device and control system thereof |
| CN113494492B (en) * | 2021-08-03 | 2024-06-14 | 中国铁建重工集团股份有限公司 | Hydraulic system for preventing karst cave from being blocked and drilling trolley |
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