CN112983907B - Hydraulic control system for rock drilling impact - Google Patents

Hydraulic control system for rock drilling impact Download PDF

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Publication number
CN112983907B
CN112983907B CN202110460991.1A CN202110460991A CN112983907B CN 112983907 B CN112983907 B CN 112983907B CN 202110460991 A CN202110460991 A CN 202110460991A CN 112983907 B CN112983907 B CN 112983907B
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valve
overflow
port
pressure
control
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CN112983907A (en
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刘伟
康磊
柳得帅
张玉良
曾庆峰
胡鑫乐
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China Railway Construction Heavy Industry Group Co Ltd
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China Railway Construction Heavy Industry Group Co Ltd
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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
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B6/00—Drives for drilling with combined rotary and percussive action
    • 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
    • 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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/005—Leakage; Spillage; Hose burst
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/20—Hydro energy

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  • Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Physics & Mathematics (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mining & Mineral Resources (AREA)
  • Analytical Chemistry (AREA)
  • Chemical & Material Sciences (AREA)
  • Environmental & Geological Engineering (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Earth Drilling (AREA)

Abstract

The application discloses rock drilling impact hydraulic control system, including hydraulic pump, rock drill and overflow pressure adjustable overflow mechanism, the export of hydraulic pump and the access connection of rock drill, the control chamber of overflow mechanism's access connection hydraulic pump, overflow mechanism's exit linkage oil tank. The hydraulic control system for rock drilling impact provided by the application utilizes the overflow mechanism to directly adjust the outlet pressure of the hydraulic pump, the hydraulic control pressure reducing valve between the hydraulic pump and the rock drill is canceled, and the pressure loss of an impact oil way is reduced.

Description

Hydraulic control system for rock drilling impact
Technical Field
The present application relates to the technical field of engineering machinery, and more particularly, to a hydraulic control system for rock drilling impact.
Background
The drill jumbo is mainly applied to tunnel construction and mine construction, has the advantages of high drilling efficiency, high safety coefficient, less environmental pollution and the like, and is often required to match different impact pressure and propelling pressure according to different working conditions in the operation process, and low propelling and low impacting are required during perforating, so that the accuracy of perforating can be ensured; during normal drilling, high propulsion and high impact are needed to ensure the drilling speed and improve the construction efficiency.
In the conventional rock drilling impact hydraulic control system, as shown in fig. 1, an inlet of a hydraulic control pressure reducing valve 07 is connected with a hydraulic pump, P2A and P2B are connected with an impact control manual reversing valve, a P2 port is connected with control ports of the hydraulic control pressure reducing valve 07 and a logic valve 08, A1C and A2C are connected with a propulsion multi-way valve, and R1 is connected with a forward rotation port of a rotary motor of the rock drill. When the pressure oil exists in the P2A, the overflow pressure of the low-impact overflow valve 02 is controlled, and then fed back to the P2 port, the outlet pressure of the hydraulic control pressure reducing valve 07 and the opening of the logic valve 08 are controlled, and the rock drill 09 starts to impact low; when the pressure oil exists in the P2B, the overflow pressure of the high-impact overflow valve 03 is controlled, and then fed back to the P2 port, the outlet pressure of the hydraulic control pressure reducing valve 07 and the opening of the logic valve 08 are controlled, and the rock drill 09 starts high impact; different propelling pressures during high and low flushing are obtained by controlling the oil cylinder pressure reducing valve 05; when the propelling pressure of the propelling oil cylinder 01 is smaller than the set pressure of the pressure reducing valve V3, P2B pressure oil is connected with B through P of the pressure reducing valve V3, so that the low-flushing overflow valve 02 and the high-flushing overflow valve 03 are communicated, at the moment, the P2B pressure is controlled by the low-flushing overflow valve 02 and then fed back to the control hydraulic control pressure reducing valve 07 through P2, and the obtained impact pressure is low impact, so that air-defense is realized. When the R1 rotation pressure exceeds the set pressure of the sequence valve 04, the sequence valve 04 is opened, so that the hydraulic control reversing valve 06 reverses, the propulsion oil cylinder 01 automatically retreats, and the anti-seizing function is realized.
The design of the rock drilling impact hydraulic control system with the structure is complex, after the hydraulic pump outputs pressure, hydraulic oil can enter the rock drill 09 through the hydraulic control pressure reducing valve 07 and the logic valve 08, the impact pressure is controlled to be a valve control system, and the hydraulic control pressure reducing valve 07 has high pressure loss due to the valve port throttling effect, so that the impact oil way pressure loss is high, the system efficiency is low, the efficiency of the rock drill 09 cannot be exerted to the greatest extent under the condition that the hydraulic pump power is limited, and the problems of low construction efficiency and the like are caused.
In summary, how to provide a drilling impact hydraulic control system with a simple structure and small impact oil path pressure loss is a problem to be solved by those skilled in the art.
Disclosure of Invention
In view of the above, it is an object of the present application to provide a rock drilling impact hydraulic control system that directly adjusts the outlet pressure of a hydraulic pump using an overflow mechanism, eliminates a pilot operated relief valve between the hydraulic pump and the rock drill, and reduces the pressure loss of an impact oil path.
In order to achieve the above object, the present application provides the following technical solutions:
a rock drilling percussive hydraulic control system, comprising:
the hydraulic pump, rock drill and overflow pressure adjustable overflow mechanism, the export of hydraulic pump with the access connection of rock drill, overflow mechanism's access connection the control chamber of hydraulic pump, overflow mechanism's exit linkage oil tank.
Optionally, the overflow mechanism comprises a first overflow valve, a second overflow valve, a third overflow valve, a first reversing valve and a second reversing valve; the first overflow valve, the second overflow valve and the third overflow valve are arranged in parallel, the set pressures of the first overflow valve, the second overflow valve and the third overflow valve are sequentially reduced, and the outlets of the first overflow valve, the second overflow valve and the third overflow valve are respectively connected with an oil tank; an inlet of the first overflow valve is connected with a control cavity of the hydraulic pump; the two interfaces of the first reversing valve are respectively connected with the inlet of the first overflow valve and the inlet of the second overflow valve, and the two interfaces of the second reversing valve are respectively connected with the inlet of the second overflow valve and the inlet of the third overflow valve.
Optionally, the first reversing valve is a hydraulic control normally closed valve, and the second reversing valve is a hydraulic control normally open valve; further comprises:
the rodless cavity of the propulsion oil cylinder is connected with the control port of the second reversing valve;
the logic valve is a normally closed valve, and two interfaces of the logic valve are respectively connected with an outlet of the hydraulic pump and an inlet of the rock drill;
the first multi-way reversing valve is used for switching the action of the propulsion oil cylinder, the inlet of the first multi-way reversing valve is connected with the hydraulic pump, and the two working ports of the first multi-way reversing valve are respectively connected with a rod cavity and a rodless cavity of the propulsion oil cylinder;
the second multi-way reversing valve is used for switching the action of the rock drill, and the inlet of the second multi-way reversing valve is connected with the hydraulic pump;
and the two inlets of the shuttle valve are respectively connected with the two working ports of the second multi-way reversing valve, and the outlets of the shuttle valve are simultaneously connected with the control port of the logic valve and the control port of the first reversing valve.
Optionally, the method further comprises:
the oil inlet and the oil return port of the fourth hydraulic control reversing valve are respectively connected with the two working ports of the first multi-way reversing valve, the two working ports of the fourth hydraulic control reversing valve are respectively connected with a rod cavity and a rodless cavity of the propulsion oil cylinder,
the pressure reducing valve is arranged on a pipeline between one working port of the fourth hydraulic control reversing valve and the rodless cavity of the propulsion oil cylinder.
Optionally, the hydraulic control system further comprises a normally closed third hydraulic control reversing valve, wherein an inlet of the third hydraulic control reversing valve is connected with a pipeline between the pressure reducing valve and the rodless cavity of the propulsion oil cylinder, an outlet of the third hydraulic control reversing valve is connected with an oil tank, and a control port of the third hydraulic control reversing valve is connected with the rod-containing cavity of the propulsion oil cylinder.
Optionally, an oil inlet of the forward rotation of the motor of the rock drill is connected with a control port of the fourth hydraulic control reversing valve through a sequence valve.
Optionally, the hydraulic control system further comprises a normally closed fifth hydraulic control reversing valve, wherein an inlet of the fifth hydraulic control reversing valve is connected with a control port of the fourth hydraulic control reversing valve, an outlet of the fifth hydraulic control reversing valve is connected with an oil tank, and a control port of the fifth hydraulic control reversing valve is connected with a working port of the first multi-way reversing valve.
Optionally, the hydraulic pump further comprises an electromagnetic ball valve, wherein an inlet of the electromagnetic ball valve is connected with a control cavity of the hydraulic pump, and an outlet of the electromagnetic ball valve is connected with an oil tank.
Through above-mentioned scheme, the rock drilling impact hydraulic control system that this application provided's beneficial effect lies in:
the utility model provides a rock drilling impact hydraulic control system includes hydraulic pump, rock drill and overflow mechanism, and hydraulic pump's export and rock drill's access connection, overflow mechanism's access connection hydraulic pump's control chamber, overflow mechanism's exit linkage oil tank, overflow mechanism's overflow pressure can be adjusted.
During operation, hydraulic oil enters the rock drill through the outlet of the hydraulic pump. The outlet pressure of the hydraulic pump can be directly regulated by controlling the overflow pressure of the overflow mechanism, and the outlet pressure of the hydraulic pump is controlled in multiple stages to obtain different rock drilling impact pressures. The impact pressure of the rock drill is improved into pump control by the valve control in the prior art, hydraulic oil does not need to pass through the hydraulic control pressure reducing valve in the prior art in the process of entering the rock drill from the hydraulic pump, so that the impact oil way pressure loss is reduced, the heating of the system is reduced, and the efficiency of the whole system is improved.
Drawings
In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the drawings that are required to be used in the embodiments or the description of the prior art will be briefly described below, and it is obvious that the drawings in the following description are only embodiments of the present application, and that other drawings may be obtained according to the provided drawings without inventive effort to a person skilled in the art.
Fig. 1 is a schematic diagram of a prior art rock drilling impact hydraulic control system;
fig. 2 is a schematic structural diagram of a hydraulic control system for rock drilling impact according to an embodiment of the present application.
The reference numerals in the figures are:
01-propulsion oil cylinder, 02-low flushing overflow valve, 03-high flushing overflow valve, 04-sequence valve, 05-oil cylinder pressure reducing valve, 06-hydraulic control reversing valve, 07-hydraulic control pressure reducing valve, 08-logic valve, 09-rock drill and V3-pressure reducing valve;
1-motor, 2-hydraulic pump, 3-first damping, 4-electromagnetic ball valve, 5-first relief valve, 6-second relief valve, 7-third relief valve, 8-first reversing valve, 9-second reversing valve, 10-first one-way valve, 11-safety relief valve, 12-first multiple-way reversing valve, 13-second one-way valve, 14-second multiple-way reversing valve, 15-second damping, 16-third damping, 17-shuttle valve, 18-logic valve, 19-rock drill, 20-push cylinder, 21-third hydraulic-controlled reversing valve, 22-pressure reducing valve, 23-fourth hydraulic-controlled reversing valve, 24-hydraulic-controlled one-way valve, 25-fourth relief valve, 26-fifth relief valve, 27-fourth damping, 28-fifth hydraulic-controlled reversing valve, 29-fifth damping, 30-sequence valve, 31-oil tank.
Detailed Description
The following description of the embodiments of the present application will be made clearly and fully with reference to the accompanying drawings, in which it is evident that the embodiments described are only some, but not all, of the embodiments of the present application. All other embodiments, which can be made by one of ordinary skill in the art without undue burden from the present disclosure, are within the scope of the present disclosure.
Referring to fig. 2, the hydraulic control system for rock drilling impact provided in the present application is applicable to a rock drilling rig including a hydraulic pump 2, a rock drill 19 and an overflow mechanism.
Wherein the hydraulic pump 2 functions to power the entire hydraulic control system. The hydraulic pump 2 may be connected to the motor 1 and powered by the motor 1. The outlet of the hydraulic pump 2 is connected to the inlet of the rock drill 19. The inlet of the overflow mechanism is connected with the control cavity X of the hydraulic pump 2, the outlet of the overflow mechanism is connected with the oil tank 31, and the overflow pressure of the overflow mechanism can be adjusted so as to change the outlet pressure of the hydraulic pump 2.
The rock drilling impact hydraulic control system with the structure has the beneficial effects that: by controlling the overflow pressure of the overflow mechanism, the multistage control of the outlet pressure of the hydraulic pump 2 is realized, and different rock drilling impact pressures are obtained. The hydraulic oil does not need to pass through the hydraulic control pressure reducing valve 07 in the prior art in the process of entering the rock drill 19 from the hydraulic pump 2, so that the pressure loss of an impact oil way is reduced, the heating of the system is reduced, and the efficiency of the whole system is improved.
Further, in one embodiment, the relief mechanism comprises a first relief valve 5, a second relief valve 6, a third relief valve 7, a first reversing valve 8 and a second reversing valve 9.
The set pressures of the first relief valve 5, the second relief valve 6 and the third relief valve 7 are sequentially reduced, the first relief valve 5 is used for providing constant pressure for system standby or other actions, the second relief valve 6 is used for providing constant pressure for the high-impact state of the rock drill 19, and the third relief valve 7 is used for providing constant pressure for the low-impact state of the rock drill 19. Simultaneously, the three are arranged in parallel, and the outlets are all connected with the oil tank 31. The inlet of the first relief valve 5 is connected to the control chamber X of the hydraulic pump 2.
The first reversing valve 8 is used for switching the pressure of other actions and the state of the rock drilling action of the system, the pressure of the system is higher in normal position, the pressure is reduced after rock drilling is switched, and the energy consumption of the system is reduced. The first reversing valve 8 is provided with two interfaces, the on-off state of the two interfaces can be controlled through the adjustment of the valve position of the first reversing valve, one of the two interfaces is connected with the inlet of the first overflow valve 5, the other interface is connected with the inlet of the second overflow valve 6, and when the two interfaces are communicated, the first overflow valve 5 is connected with the second overflow valve 6 in parallel. The first reversing valve 8 may be an electrically controlled valve or a hydraulically controlled valve.
The second reversing valve 9 is used for switching between two different pressures, high and low, during rock drilling. The second reversing valve 9 comprises two interfaces, the on-off state of the two interfaces can be controlled through the adjustment of the valve position of the second reversing valve, one interface is connected with the inlet of the second overflow valve 6, the other interface is connected with the inlet of the third overflow valve 7, and when the two interfaces are communicated, the second overflow valve 6 is connected with the third overflow valve 7 in parallel. The second reversing valve 9 may be an electrically controlled valve or a hydraulically controlled valve.
Further, in one embodiment, the rock drilling impact hydraulic control system further comprises a thrust cylinder 20, a logic valve 18, a first multi-way directional valve 12, a second multi-way directional valve 14 and a shuttle valve 17. Correspondingly, the first reversing valve 8 is a hydraulic control normally closed valve, and the second reversing valve 9 is a hydraulic control normally open valve.
The thrust cylinder 20 has a rod-free chamber and a rod-free chamber, and the rod-free chamber is connected with a control port of the second reversing valve 9.
The logic valve 18 is used for controlling the on-off of the impact main oil way, namely the oil way of the inlet of the rock drill 19 and the oil way of the outlet of the hydraulic pump 2, so as to realize the starting and stopping of the rock drill 19. The logic valve 18 is a normally closed valve with two ports, one connected to the outlet of the hydraulic pump 2 and the other connected to the inlet of the rock drill 19.
The first multiple directional control valve 12 is used for switching the action of the thrust cylinder 20, and three gears are respectively set back, stopped and advanced.
The first multiple directional control valve 12 has an oil inlet, an oil return port and two working ports, wherein the oil inlet is connected with the outlet of the hydraulic pump 2, and the working ports A1 and B1 are connected with the rod cavity and the rodless cavity of the thrust cylinder 20.
The second multiple directional control valve 14 is used to switch the operation of the rock drill 19, and three gear positions are respectively a stop position, a low flushing position and a high flushing position. The second multiple directional valve 14 has an oil inlet connected to the outlet of the hydraulic pump 2 and two working ports a and B connected to the two inlets of the shuttle valve 17.
The shuttle valve 17 is used for switching the high and low flushing control oil. Shuttle valve 17 is a three-way valve having an inlet H, an inlet J and an outlet G; wherein, the inlet H is connected with the working port A of the second multi-way reversing valve 14, and the inlet J is connected with the working port B of the second multi-way reversing valve 14; the outlet G is connected with the control port of the logic valve 18, the outlet G is also connected with the control port of the first reversing valve 8, and when hydraulic oil exists in the outlet G, the logic valve 18 is controlled to be opened, and meanwhile the first reversing valve 8 is controlled to be opened.
Further, in an embodiment, the rock drilling percussion hydraulic control system further comprises a fourth pilot operated directional valve 23 and a pressure reducing valve 22.
The fourth hydraulic control reversing valve 23 is used for switching pressure oil in a rodless cavity and a rod cavity of the thrust cylinder 20 when the drill rod is clamped. The fourth pilot operated directional valve 23 may be a two-position four-way valve having an oil inlet, an oil return port and two working ports, i.e. P, T, A and B in fig. 2, where the oil inlet P is connected to the working port A1 of the first multiple directional valve 12, the oil return port T is connected to the working port B1 of the first multiple directional valve 12, the working port a is connected to the rodless chamber of the propulsion cylinder 20, and the working port B is connected to the rod-containing chamber of the propulsion cylinder 20.
The relief valve 22 is used to regulate the boost pressure of the rodless cavity of the boost cylinder 20. The pressure reducing valve 22 is arranged on a pipeline between the working port A of the fourth hydraulic control reversing valve 23 and the rodless cavity of the propulsion cylinder 20. Alternatively, the pressure relief valve 22 may be characterized by a control port pressure that is directly increased to the valve's own set point in a 1:1 ratio.
In the prior art, as shown in fig. 1, because the oil cylinder pressure reducing valve 05 is positioned at the front side, when the anti-seizing drill rod is triggered, the back pressure of the pushing oil cylinder 01 is the outlet pressure of the oil cylinder pressure reducing valve 05, the back pressure is low, and the anti-seizing drill rod is insensitive. In this embodiment, as shown in fig. 2, the pressure reducing valve 22 is located at the rear side of the fourth pilot operated directional valve 23, and after the anti-seizing drill is triggered, the retraction pressure is the front side pressure of the pressure reducing valve 22, and the retraction pressure is high.
Further, in an embodiment, the rock drilling percussion hydraulic control system further comprises a third pilot operated directional valve 21. The third hydraulic control reversing valve 21 is used for enabling the rodless cavity of the propulsion cylinder 20 to return oil quickly. It may be a normally closed valve having two ports, one port connecting the line between the relief valve 22 and the rodless chamber of the thrust cylinder 20 and the other port connecting the tank 31 and the control port connecting the rod-containing chamber of the thrust cylinder 20. When the anti-seizing drill rod is triggered, hydraulic oil in a rod cavity of the propulsion oil cylinder 20 can push the third hydraulic control reversing valve 21 to be opened, the back pressure of oil return in a rodless cavity of the propulsion oil cylinder 20 is small, oil return is quick, and anti-seizing drill rod reaction is sensitive.
Further, in an embodiment, the rock drilling impact hydraulic control system further comprises a sequence valve 30, the sequence valve 30 being arranged to trigger the anti-seize drill rod when the forward rotation pressure of the motor of the rock drill 19 is high. The rock drill 19 rotates forward, the R port is connected with an oil inlet of the forward rotation of a motor of the rock drill 19, and the sequence valve 30 is arranged between the R port and a control port of the fourth hydraulic control reversing valve 23. When the sequence valve 30 is opened, the hydraulic oil pushes the valve core of the fourth hydraulic control reversing valve 23 to move, so as to switch the valve position of the fourth hydraulic control reversing valve 23, and further switch the forward and backward states of the thrust cylinder 20.
Further, in an embodiment, the rock drilling impact hydraulic control system further comprises a fifth pilot operated directional valve 28, and the fifth pilot operated directional valve 28 is configured to actively unload the control pressure of the fourth pilot operated directional valve 23. The fifth pilot operated directional valve 28 may be a normally closed valve, an inlet of which is connected to the control port of the fourth pilot operated directional valve 23, an outlet of which is connected to the tank 31, and a control port of which is connected to the working port B1 of the first multiple directional valve 12.
In the prior art, as shown in fig. 1, after the drill rod is completely clamped, the forward rotation pressure is always higher, then the hydraulic control reversing valve 06 is always at the reversing position, and when the drill rod is manually released, the multi-way valve is positioned at the retreating position A2C to feed oil, but after the drill rod is diverted through the hydraulic control reversing valve 06, the oil cylinder 01 is pushed to advance instead, so that the drill rod is further clamped deeper.
In this embodiment, as shown in fig. 2, when the drill rod is completely jammed, a manual disengagement is required, and at this time, the fifth hydraulic control directional valve 28 actively unloads the control oil of the fourth hydraulic control directional valve 23, so that the thrust cylinder 20 is switched from the forward state to the backward state, and the drill rod is prevented from being jammed deeper.
Further, in an embodiment, the hydraulic control system for rock drilling impact further comprises an electromagnetic ball valve 4, wherein the electromagnetic ball valve 4 is used for guaranteeing the unloading starting of the hydraulic pump 2 when the system is started, the inlet of the electromagnetic ball valve 4 is connected with the control cavity X of the hydraulic pump 2, and the outlet of the electromagnetic ball valve is connected with the oil tank 31.
Further, in an embodiment, the rock drilling impact hydraulic control system further comprises a one-way valve to protect the system. For example, the first check valve 10 may be disposed at an oil inlet of the first multiple directional valve 12, and the second check valve 13 may be disposed at an oil inlet of the second multiple directional valve 14.
Further, in an embodiment, the rock drilling percussion hydraulic control system further comprises a safety relief valve 11, the set pressure of which is larger than the set pressure of the first relief valve 5, for protecting the system.
Further, in an embodiment, the rock drilling percussion hydraulic control system further comprises damping. For example, a first damper 3 may be provided in the line between the outlet of the hydraulic pump 2 and the control chamber X of the hydraulic pump 2, which acts to control the pilot flow of the pressure feedback valve block, creating a pressure differential, reducing the influence of load fluctuations on the control chamber pressure of the hydraulic pump 2. A second damper 15 may be provided in a pipeline between the J port of the shuttle valve 17 and the working port B of the second multiple directional control valve 14, so that the control oil of the working port B of the second multiple directional control valve 14 can be smoothly unloaded when the low-flushing control oil does not work. A third damper 16 may be provided in a pipeline between the H port of the shuttle valve 17 and the working port a of the second multiple directional control valve 14, so that the control oil of the working port a of the second multiple directional control valve 14 can be smoothly unloaded when the high-flushing control oil does not work. The fourth damper 27 may be provided so that the pilot operated check valve 24 controls the smooth unloading of oil when the undershoot is not in operation. A fifth damper 29 may be provided in the pipeline between the sequence valve 30 and the control port of the fourth pilot operated directional valve 23, so that the control pressures of the third pilot operated directional valve 21 and the fourth pilot operated directional valve 23 are smoothly unloaded when the motor is operating normally.
Further, in an embodiment, the rock drilling percussion hydraulic control system further comprises a pilot operated check valve 24, a fourth relief valve 25 and a fifth relief valve 26. Wherein the pilot operated check valve 24 is used to control the switching of the propulsion pressure during high and low stroke. The fourth relief valve 25 is used to control the boost pressure at high impact and to control the boost pressure at no drilling action. The fifth relief valve 26 is used to control the boost pressure at low stroke.
The control principle of the rock drilling impact hydraulic control system with the structure is as follows:
for convenience of description, taking the state shown in fig. 2 as an example, when the valve is horizontally placed, the valve position is sequentially increased from left to right; when the valve is vertically placed, the valve position is sequentially increased from top to bottom. For example, for the first multiple directional control valve 12, the uppermost valve position is the first operating position, the middle is the second operating position, and the lowermost valve position is the third operating position; for the first reversing valve 8, the valve position on the left is the first working position, and the valve position on the right is the second working position.
1. In the initial state, the first multiplex valve 12 is located at the push stop position, i.e., the second operating position. Therefore, the port A1 and the port B1 of the first multiple directional valve 12 are both free of pressurized oil, and the thrust cylinder 20 does not operate. Meanwhile, the second multiple directional valve 14 is located at the rock drilling stop position, i.e., the first working position. Therefore, the ports a and B of the second multiple directional valve 14 are not pressurized with oil, the outlet G of the shuttle valve 17 is not pressurized with oil, the logic valve 18 is in a closed state, and the rock drill 19 is not impacted.
(1) When the electromagnetic ball valve 4 is not electrified, the control cavity X of the hydraulic pump 2 is communicated with the oil tank 31 through the electromagnetic ball valve 4, and when the motor 1 is started, the hydraulic pump 2 can be started in an unloading mode, and the outlet pressure of the hydraulic pump 2 is lower because the pressure set by the hydraulic pump 2 is lower.
(2) When the electromagnetic ball valve 4 is powered on, the outlet G of the shuttle valve 17 is free of pressure oil, so that the control port of the first reversing valve 8 is free of pressure oil, the first reversing valve 8 is positioned at a normal position and is not reversed, the port I and the port II of the first reversing valve 8 are not communicated, the outlet pressure of the hydraulic pump 2 is determined by the set pressure of the first overflow valve 5, and at the moment, the system is in a standby state or other execution actions of the rock drilling trolley can be carried out. Wherein the setting values of the safety relief valve 11, the first relief valve 5, the second relief valve 6, and the third relief valve 7 are sequentially reduced.
2. When only the thrust cylinder 20 is operated:
(1) When the first multi-way reversing valve 12 is located at the retreating position, i.e. the first working position is shown in the drawing, at this moment, P1 is communicated with the port B1 of the first multi-way reversing valve 12 through the first one-way valve 10, the port B1 is connected with the rod cavity of the propulsion cylinder 20 through the port T and the port B of the fourth hydraulic control reversing valve 23, and at this moment, the port B of the fourth hydraulic control reversing valve 23 is connected with the control oil port of the third hydraulic control reversing valve 21, then the port i and the port ii of the third hydraulic control reversing valve 21 are communicated, and hydraulic oil in the rodless cavity of the propulsion cylinder 20 enters the oil tank 31 through the third hydraulic control reversing valve 21, so that the retreating back pressure of the propulsion cylinder 20 is small and quick response is achieved.
The port B1 of the first multiple directional valve 12 is also connected to the control port of the fifth pilot operated directional valve 28, so that the port i and the port ii of the fifth pilot operated directional valve 28 are communicated. Because the control port of the first reversing valve 8 is free from pressure oil, the first reversing valve 8 is positioned at a normal position under the action of spring force and is not reversed, the ports I and II of the first reversing valve 8 are not communicated, and at the moment, the pressure of the hydraulic pump 2 is determined by the first overflow valve 5.
(2) When the first multi-way reversing valve 12 is located at the forward position, i.e. the third working position, at this time, P1 is communicated with the port A1 of the first multi-way reversing valve 12 through the first one-way valve 10, the port A1 is connected with the inlet of the pressure reducing valve 22 through the port P and the port a of the fourth hydraulic control reversing valve 23, the outlet of the pressure reducing valve 22 is communicated with the rodless cavity of the push cylinder 20, the outlet of the pressure reducing valve 22 is connected with the port ii of the third hydraulic control reversing valve 21, the outlet of the pressure reducing valve 22 is also connected with the control port of the second reversing valve 9, and hydraulic oil with the rod cavity of the push cylinder 20 enters the oil tank 31 through the port B and the port T of the fourth hydraulic control reversing valve 23 and the first multi-way reversing valve 12. Since the propulsion cylinder 20 has a rod cavity connected to the oil tank 31, the third pilot operated directional valve 21 is controlled to zero in pressure, and is normally positioned under the action of spring force, and the ports I and II are not communicated. The control port of the first reversing valve 8 is free of pressure oil, so that the first reversing valve 8 is positioned at a normal position and is not reversed, the ports I and II of the first reversing valve 8 are not communicated, and the pressure of the hydraulic pump 2 is determined by the first overflow valve 5. Since the second multiple directional control valve 14 is in the stop position and the port K has no control oil, the pilot operated check valve 24 controls the oil pressure to be zero, and the fourth relief valve 25 and the fifth relief valve 26 are not connected, so that the boost pressure of the boost cylinder 20 is determined by the relief valve 22 and the fourth relief valve 25. In general, the set value of the relief valve 22 is a fixed value, and the outlet pressure of the relief valve 22 can be adjusted by adjusting the set value of the fourth relief valve 25, so as to adjust the propelling pressure of the rodless cavity of the propelling cylinder 20. Wherein the fourth relief valve 25 setting is higher than the fifth relief valve 26 setting, and the fifth relief valve 26 setting is typically a fixed value, the pressure relief valve 22 is characterized by a control port pressure of directly 1: the ratio of 1 increases to the set point of the valve itself.
3. When the rock drill 19 is in operation:
during normal drilling, the rock drill 19 rotates positively, the R port is connected with an oil inlet of the forward rotation of a motor of the rock drill 19, the forward rotation pressure is smaller than the set pressure of the sequence valve 30, the outlet of the sequence valve 30 is pressureless, and the fourth hydraulic control reversing valve 23 is positioned at a normal position under the action of spring force.
(1) When the second multi-way directional valve 14 is in the low-flushing working position, namely the second working position, the outlet pressure oil P1 of the hydraulic pump 2 is communicated with the port B of the second multi-way directional valve 14 through the second one-way valve 13, the port B pressure oil passes through the port J and the port G of the shuttle valve 17 and is communicated with the control port of the logic valve 18, so that the logic valve 18 is opened, and the rock drill 19 starts working. And meanwhile, the pressure oil at the outlet G of the shuttle valve 17 is connected with the control port of the first reversing valve 8, so that the first reversing valve 8 reverses, and the port I and the port II of the first reversing valve are communicated. And meanwhile, the port B of the second multi-way reversing valve 14 is connected with the control port of the hydraulic control one-way valve 24 and the inlet of the fourth damping 27, and the hydraulic control one-way valve 24 is opened.
(1) If the first multi-way reversing valve 12 is located at the stop position, namely the second working position, the rodless cavity pressure of the thrust cylinder 20 is zero, the control port pressure of the second reversing valve 9 is zero, the second reversing valve 9 does not reverse, and at the moment, the first overflow valve 5, the second overflow valve 6 and the third overflow valve 7 are in a parallel connection state.
(2) If the first multiple directional valve 12 is located in the forward position, i.e. the third working position, since the hydraulic control check valve 24 is opened by the hydraulic control oil with the pressure of K ports, at this time, the fourth relief valve 25 and the fifth relief valve 26 are connected in parallel, the boost pressure is determined by the relief valve 22 and the fifth relief valve 26 with lower pressure, at this time, the boost pressure is low, the rodless cavity of the boost cylinder 20 is connected to the control port of the second directional valve 9, where the spring setting value of the second directional valve 9 is between the high-impact boost pressure and the low-impact boost pressure, i.e. the setting value is greater than the low-impact boost pressure but less than the high-impact boost pressure, at this time, the low-impact boost pressure is less than the spring setting force of the second directional valve 9, and the second directional valve 9 is not yet commutated, and the first relief valve 5, the second relief valve 6 and the third relief valve 7 are in the parallel state.
(3) If the first multi-way reversing valve 12 is located at the retreating position, namely the first working position, the port B pressure oil of the fourth hydraulic control reversing valve 23 enables the third hydraulic control reversing valve 21 to reverse, so that the port I and the port II of the third hydraulic control reversing valve are communicated, the rodless cavity pressure of the propulsion oil cylinder 20 is zero, the control pressure of the second reversing valve 9 is zero, the second reversing valve 9 keeps normal position under the action of spring force and does not reverse, and at the moment, the first overflow valve 5, the second overflow valve 6 and the third overflow valve 7 are in a parallel connection state.
In summary, when the second multi-way reversing valve 14 is in the low-flushing working position, the propulsion cylinder 20 is in any one of the propulsion, stopping and retreating states, the pressure of the control cavity X of the hydraulic pump 2 is determined by the third overflow valve 7, and the outlet pressure of the hydraulic pump 2 outputs the pressure corresponding to the low-flushing state.
(2) When the second multi-way directional valve 14 is in the high-flushing working position, namely the third working position, the outlet pressure oil P1 of the hydraulic pump 2 is communicated with the port A of the second multi-way directional valve 14 through the second one-way valve 13, and the port A pressure oil is connected with the port G through the port H of the shuttle valve 17 to enable the logic valve 18 to be opened, so that the rock drill 19 starts working. And meanwhile, the pressure oil at the outlet G of the shuttle valve 17 reaches the control port of the first reversing valve 8, so that the first reversing valve 8 reverses, and the port I and the port II of the first reversing valve are communicated.
(1) If the first multi-way reversing valve 12 is located at the stop position, namely the second working position, the rodless cavity pressure of the propulsion oil cylinder 20 is zero, the control port pressure of the second reversing valve 9 is zero, the second reversing valve 9 does not reverse, and at the moment, the first overflow valve 5, the second overflow valve 6 and the third overflow valve 7 are in a parallel state; at this time, the pressure of the control chamber X of the hydraulic pump 2 is determined by the third relief valve 7, that is, the output pressure of the outlet pressure of the hydraulic pump 2 is the pressure corresponding to the undershoot state.
(2) If the first multiple directional control valve 12 is located in the forward position, i.e. the third working position, the push cylinder 20 starts to push, because the port B of the second multiple directional control valve 14 has no pressure oil, the pilot operated check valve 24 has zero control port pressure, the pilot operated check valve 24 is closed, the fourth relief valve 25 and the fifth relief valve 26 are not communicated, at this time, the push pressure of the push cylinder 20 is determined by the pressure reducing valve 22 and the fourth relief valve 25, the push pressure is high in operation, the high-impulse push pressure oil of the push cylinder 20 is fed back to the control port of the second directional control valve 9, the high-impulse push pressure is greater than the self spring setting force of the second directional control valve 9, so that the second directional control valve 9 is switched, at this time, the first relief valve 5 and the second relief valve 6 are in parallel connection, the pressure of the control chamber X of the hydraulic pump 2 is determined by the second relief valve 6, and the outlet pressure of the hydraulic pump 2 outputs the pressure corresponding to the high-impulse state.
(3) If the first multi-way reversing valve 12 is located at the retreating position, namely the first working position, the port I of the third hydraulic control reversing valve 21 is communicated with the port II, the rodless cavity of the propulsion cylinder 20 is communicated with the oil tank 31 through the third hydraulic control reversing valve 21, the pressure of the rodless cavity of the propulsion cylinder 20 is zero, the pressure of the control port of the second reversing valve 9 is zero, the second reversing valve 9 does not reverse, and at the moment, the first overflow valve 5, the second overflow valve 6 and the third overflow valve 7 are in a parallel connection state. At this time, the pressure of the control chamber X of the hydraulic pump 2 is determined by the third relief valve 7, that is, the output pressure of the outlet pressure of the hydraulic pump 2 is the pressure corresponding to the undershoot state.
In summary, when the second multiple directional control valve 14 is at the third working position, i.e., the high-impulse working position, the outlet pressure of the hydraulic pump 2 outputs the pressure corresponding to the high-impulse state when the propulsion cylinder 20 is normally propelled, and the outlet pressure of the hydraulic pump 2 outputs the pressure corresponding to the low-impulse state when the propulsion cylinder 20 is not propelled or retreated.
4. Air defense control:
when the drill bit is in a high-impact state during normal pushing of the rock drilling machine 19, when the drill bit encounters soft rock or karst cave, the pushing pressure of the pushing oil cylinder 20 is reduced due to low load, the pressure fed back to the control port of the second reversing valve 9 is reduced at the moment, when the pushing pressure is lower than the spring set value of the second reversing valve 9, the second reversing valve 9 is changed from the reversing position to an initial state at the moment, then the first overflow valve 5, the second overflow valve 6 and the third overflow valve 7 are in a parallel state at the moment, the pressure of the control cavity X of the hydraulic pump 2 is determined by the third overflow valve 7, and the outlet pressure of the hydraulic pump 2 is reduced from the corresponding high-impact set pressure to the low-impact set pressure, so that when the pushing pressure is insufficient, the impact pressure of the rock drilling machine 19 is automatically reduced from the high-impact pressure to the low-impact pressure, energy consumption is saved, the long-time idle-time drilling of the rock drilling machine 19 is prevented, and the rock drilling machine 19 and the drill tool are damaged.
When the karst cave disappears or the rock stratum becomes hard again, the propelling pressure of the propelling oil cylinder 20 is increased due to the load, the pressure of the control port of the second reversing valve 9 is increased, when the propelling pressure is higher than the spring set value of the second reversing valve 9, the second reversing valve 9 is reversed again, the first overflow valve 5 and the second overflow valve 6 are in a parallel state, the pressure of the control cavity X of the hydraulic pump 2 is determined by the second overflow valve 6 again, the outlet pressure of the hydraulic pump 2 is changed from the low-flushing set pressure to the high-flushing set pressure, the impact pressure of the rock drill 19 is increased, and the working efficiency is improved.
In summary, when the propelling pressure of the propelling cylinder 20 is insufficient, the outlet pressure of the hydraulic pump 2 is reduced, and the rock drill 19 and the drill tool are prevented from being damaged by wasteful high impact for a long time.
5. Anti-seize drill rod control:
during normal drilling, the rock drill 19 rotates positively, the R port is connected with an oil inlet of the forward rotation of a motor of the rock drill 19, the forward rotation pressure is smaller than the set pressure of the sequence valve 30, the outlet of the sequence valve 30 is pressureless, and the fourth hydraulic control reversing valve 23 is positioned at a normal position under the action of spring force. The first multiple directional valve 12 is in the forward position and the second multiple directional valve 14 is in the low-impulse or high-impulse operating position.
When the radial resistance of the drill bit is larger and the rotation speed is slower, the rotation pressure starts to rise, when the rotation pressure exceeds the set pressure of the sequence valve 30, the sequence valve 30 is opened, because the B1 of the first multi-way reversing valve 12 is connected with the oil tank 31, the fifth hydraulic reversing valve 28 is positioned at a normal position, the outlet pressure of the sequence valve 30 enables the fourth hydraulic reversing valve 23 to reverse, the P port of the fourth hydraulic reversing valve 23 is communicated with the B port, the high-pressure oil originally entering the rodless cavity of the propulsion cylinder 20 is changed and enters the rod cavity, the propulsion cylinder 20 is changed from propulsion to retreating, the high-pressure oil with the rod cavity at the moment enables the third hydraulic reversing valve 21 to reverse, and the I port and the II port of the third hydraulic reversing valve 21 are communicated, so that the rodless cavity of the propulsion cylinder 20 can return oil rapidly. Because the pressure oil at the port B of the fourth hydraulic control reversing valve 23 does not pass through the pressure reducing valve 22 and is directly connected with the rod cavity of the propulsion oil cylinder 20, the back pressure of the propulsion oil cylinder 20 is high when the drill rod is clamped, the back pressure of the return oil is low, and the quick release of the drill rod is facilitated. When the rotation pressure slowly becomes low, the sequence valve 30 is closed, the fourth hydraulic control reversing valve 23 becomes normal again under the unloading action of the fifth damping 29, the port P of the fourth hydraulic control reversing valve 23 is communicated with the port A, the port I and the port II of the third hydraulic control reversing valve 21 are closed, the thrust cylinder 20 is changed from backward to forward again, and the rock drill 19 works normally.
When the drill rod is completely clamped and cannot rotate, the drill rod is usually required to be pulled out manually, at this time, the first multiple directional valve 12 is located at a retreating position, at this time, the port P1 is communicated with the port B1 of the first multiple directional valve 12 through the first one-way valve 10, the port B1 is connected with the control port of the fifth pilot operated directional valve 28, the port i and the port ii of the fifth pilot operated directional valve 28 are communicated, the pressure oil at the outlet of the sequence valve 30 is unloaded, so that the fourth pilot operated directional valve 23 is located at a normal position, the port B1 of the first multiple directional valve 12 is connected with the rod cavity of the propulsion cylinder 20 through the port T and the port B of the fourth pilot operated directional valve 23, at this time, the port B of the fourth pilot operated directional valve 23 is connected with the control port of the third pilot operated directional valve 21, the port i and the port ii of the third pilot operated directional valve 21 are communicated, the rod cavity of the propulsion cylinder 20 is not provided with the oil return tank 31 through the third pilot operated directional valve 21, the rock drill 19 is retracted, and the drill rod is pulled out. The fourth hydraulic control reversing valve 23 is actively unloaded to control oil, so that the phenomenon that the fourth hydraulic control reversing valve 23 is positioned at a reversing position due to high rotation pressure can be avoided, and the defect that the drill tool is clamped deeper due to manual clamping-off operation is overcome.
In the present specification, each embodiment is described in a progressive manner, and each embodiment is mainly described in a different point from other embodiments, and identical and similar parts between the embodiments are all enough to refer to each other.
The rock drilling impact hydraulic control system provided by the present application is described in detail above. Specific examples are set forth herein to illustrate the principles and embodiments of the present application, and the description of the examples above is only intended to assist in understanding the methods of the present application and their core ideas. It should be noted that it would be obvious to those skilled in the art that various improvements and modifications can be made to the present application without departing from the principles of the present application, and such improvements and modifications fall within the scope of the claims of the present application.

Claims (5)

1. A rock drilling percussive hydraulic control system, comprising:
the hydraulic system comprises a hydraulic pump (2), a rock drill (19) and an overflow mechanism with adjustable overflow pressure, wherein an outlet of the hydraulic pump (2) is connected with an inlet of the rock drill (19), an inlet of the overflow mechanism is connected with a control cavity of the hydraulic pump (2), and an outlet of the overflow mechanism is connected with an oil tank (31);
the overflow mechanism comprises a first overflow valve (5), a second overflow valve (6), a third overflow valve (7), a first reversing valve (8) and a second reversing valve (9); the first overflow valve (5), the second overflow valve (6) and the third overflow valve (7) are arranged in parallel, the set pressures of the first overflow valve, the second overflow valve and the third overflow valve are sequentially reduced, and the outlets of the first overflow valve, the second overflow valve and the third overflow valve are respectively connected with the oil tank (31); an inlet of the first overflow valve (5) is connected with a control cavity of the hydraulic pump (2); two interfaces of the first reversing valve (8) are respectively connected with an inlet of the first overflow valve (5) and an inlet of the second overflow valve (6), and two interfaces of the second reversing valve (9) are respectively connected with an inlet of the second overflow valve (6) and an inlet of the third overflow valve (7);
the first reversing valve (8) is a normally closed hydraulic control valve, and the second reversing valve (9) is a normally open hydraulic control valve; further comprises:
a propulsion cylinder (20) with a rodless cavity connected with a control port of the second reversing valve (9);
the logic valve (18) is a normally closed valve, and two interfaces of the logic valve are respectively connected with the outlet of the hydraulic pump (2) and the inlet of the rock drill (19);
the first multi-way reversing valve (12) is used for switching the action of the propulsion oil cylinder (20), an inlet of the first multi-way reversing valve is connected with the hydraulic pump (2), and two working ports of the first multi-way reversing valve are respectively connected with a rod cavity and a rodless cavity of the propulsion oil cylinder (20);
a second multi-way reversing valve (14) for switching the action of the rock drill (19), the inlet of which is connected with the hydraulic pump (2);
the two inlets of the shuttle valve (17) are respectively connected with the two working ports of the second multi-way reversing valve (14), and the outlets of the shuttle valve are simultaneously connected with the control port of the logic valve (18) and the control port of the first reversing valve (8);
the oil inlet and the oil return port of the fourth hydraulic control reversing valve (23) are respectively connected with the two working ports of the first multi-way reversing valve (12), and the two working ports of the fourth hydraulic control reversing valve are respectively connected with a rod cavity and a rodless cavity of the propulsion oil cylinder (20);
the pressure reducing valve (22) is arranged on a pipeline between one working port of the fourth hydraulic control reversing valve (23) and the rodless cavity of the propulsion oil cylinder (20);
the hydraulic control one-way valve (24), the fourth overflow valve (25) and the fifth overflow valve (26) are arranged in parallel, the set pressures of the fourth overflow valve (25) and the fifth overflow valve (26) are sequentially reduced, and the outlets of the fourth overflow valve and the fifth overflow valve are both connected with the oil tank (31); the inlet of the hydraulic control one-way valve (24) is connected with the inlet of the fifth overflow valve (26), the outlet of the hydraulic control one-way valve (24) is connected with the oil port of the fourth overflow valve (25) and the control oil port of the pressure reducing valve (22), and the control port of the hydraulic control one-way valve (24) is connected with one working port of the second multi-way reversing valve (14) so as to control the switching of the propelling pressure during high and low flushing.
2. A rock drilling impact hydraulic control system according to claim 1, characterized in that it further comprises a normally closed third pilot operated directional valve (21), the inlet of which is connected to the line between the pressure reducing valve (22) and the rodless chamber of the propulsion cylinder (20), the outlet of which is connected to an oil tank (31), the control port of which is connected to the rod-containing chamber of the propulsion cylinder (20).
3. A rock drilling percussive hydraulic control system according to claim 1, characterized in that the oil inlet of the motor of the rock drill (19) is connected to the control port of the fourth hydraulically controlled reversing valve (23) via a sequence valve (30).
4. A rock drilling percussive hydraulic control system as claimed in claim 3, characterized in that it further comprises a normally closed fifth pilot operated directional valve (28), the inlet of which is connected to the control port of the fourth pilot operated directional valve (23), the outlet of which is connected to an oil tank (31), the control port of which is connected to one of the working ports of the first multi-way directional valve (12).
5. A rock drilling percussive hydraulic control system as claimed in claim 1, characterized in that it further comprises an electromagnetic ball valve (4), the inlet of which is connected to the control chamber of the hydraulic pump (2) and the outlet of which is connected to an oil tank (31).
CN202110460991.1A 2021-04-27 2021-04-27 Hydraulic control system for rock drilling impact Active CN112983907B (en)

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CN113638943B (en) * 2021-08-12 2024-06-14 中国铁建重工集团股份有限公司 Impact hydraulic control system and drilling jumbo
CN114060326B (en) * 2021-12-02 2023-04-18 上海中车艾森迪海洋装备有限公司 Constant tension winch hydraulic system
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

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE515204C2 (en) * 1999-11-03 2001-06-25 Atlas Copco Rock Drills Ab Method and apparatus for controlling a rock drill
CN102561937B (en) * 2012-01-20 2013-11-06 中船重工中南装备有限责任公司 Adjustable rock drilling control system of hydraulic rock drilling machine
CN102758585B (en) * 2012-07-26 2015-03-11 徐州徐工铁路装备有限公司 Idle-preventing system of hydraulic drill jumbo
CN103556943B (en) * 2013-11-08 2016-05-11 阿特拉斯科普柯(南京)建筑矿山设备有限公司 According to the method for the ballistic work of feeding force control rock drilling system and device
CN203716837U (en) * 2014-02-28 2014-07-16 金川集团股份有限公司 Anti-clamping bit hydraulic control system for rock drill
CN204512026U (en) * 2015-02-11 2015-07-29 阿特拉斯科普柯(南京)建筑矿山设备有限公司 The anti-solution cavity card pricker system of drill jumbo
CN107906084B (en) * 2017-10-27 2024-07-12 中国铁建重工集团股份有限公司 Rock drill and hydraulic drilling control system thereof
CN207673634U (en) * 2017-12-29 2018-07-31 徐州徐工铁路装备有限公司 The rock drilling control system of drill jumbo
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

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