CN117167369A

CN117167369A - Rock drill and control system thereof

Info

Publication number: CN117167369A
Application number: CN202311191228.9A
Authority: CN
Inventors: 杨光
Original assignee: Anbaituo Nanjing Construction Mining Equipment Co ltd
Current assignee: Anbaituo Nanjing Construction Mining Equipment Co ltd
Priority date: 2023-09-15
Filing date: 2023-09-15
Publication date: 2023-12-05

Abstract

The application discloses a rock drill and a control system thereof; the control system is used for controlling the drill bit of the rock drill and comprises an impact oil cylinder, a propulsion oil cylinder, an impact control valve, a propulsion sensor and a controller; wherein, the controller is electrically connected to the propulsion sensor; the impact control valve is hydraulically connected to the impact cylinder; the controller is electrically connected to the impact control valve to acquire the flow of the oil way where the impact oil cylinder is located, which is matched with the pressure of the oil way where the thrust oil cylinder is located when the pressure of the oil way where the thrust oil cylinder is located detected by the thrust sensor changes. The rock drill and the control system thereof have the beneficial effects that the rock drill with the impact frequency of the impact oil cylinder and the pressure of the oil way where the pushing oil cylinder is positioned are matched.

Description

Rock drill and control system thereof

Technical Field

The application belongs to the field of control, and particularly relates to a rock drill and a control system thereof.

Background

Rock drill is widely applied in the fields of mines, tunnels, hydropower, buildings and the like, and along with the continuous enhancement of the automation degree in the construction fields of mines, tunnels, hydropower and the like in China, the rock drill becomes more and more indispensable in rock drilling construction engineering. In the prior art, impact frequency is generally controlled by adopting two-stage flow control or two-stage pressure control, and the impact frequency cannot be matched with the propulsion speed.

In the related art, the chinese patent document CN204704173U provides a hydraulic check valve connected in series to a main hydraulic oil path, the hydraulic check valve is positively connected from a propulsion mechanism to a hydraulic pump, a control port of the hydraulic check valve is connected with a position between the hydraulic check valve and the hydraulic pump through a pilot control oil path, the pilot control oil path is connected in series with a first control valve for controlling whether the hydraulic check valve is reversely connected or not, the hydraulic check valve is connected in parallel with a speed control oil path, and the speed control oil path is connected in series with a speed regulating valve to realize the technical scheme of propulsion speed control of the hydraulic rock drill. The related art does not give any technical suggestion to solve the problem that the impact frequency cannot match the propulsion speed.

Disclosure of Invention

The summary of the application is provided to introduce a selection of concepts in a simplified form that are further described below in the detailed description. The summary of the application is not intended to identify key features or essential features of the claimed subject matter, nor is it intended to be used to limit the scope of the claimed subject matter.

To solve the technical problems mentioned in the background, as a first aspect of the present application, some embodiments of the present application provide a control system for controlling a drill bit of a rock drill, the control system including a percussion cylinder, a thrust cylinder, a percussion control valve, a thrust sensor and a controller. Wherein the percussion cylinder is used to provide power to impact the drill bit against the rock to be excavated. The thrust cylinder is used for providing power for propelling the drill bit. The impact control valve is used for controlling the flow of an oil way where the impact oil cylinder is located. The propulsion sensor is used for detecting the pressure of an oil way where the propulsion oil cylinder is located. The controller is electrically connected to the propulsion sensor. The shock control valve is hydraulically connected to the shock cylinder. The controller is electrically connected to the impact control valve to acquire the flow of the oil way where the impact oil cylinder is located, which is matched with the pressure of the oil way where the thrust oil cylinder is located when the pressure of the oil way where the thrust oil cylinder is located detected by the thrust sensor changes.

Further, the impact control valve is configured as a proportional flow valve.

Further, the control system also includes propulsion control, a rotary motor, and a rotary sensor. The propulsion control valve is used for controlling the pressure of an oil way where the propulsion oil cylinder is located. The rotary motor is used to provide power to rotate the drill bit. The rotation sensor is used for detecting the pressure of an oil way where the rotation motor is located. Wherein the propulsion control valve is hydraulically connected to the propulsion cylinder. The controller is electrically connected to the rotation sensor. The controller is electrically connected to the propulsion control valve so as to acquire the pressure of the oil way where the propulsion oil cylinder is located, which is matched with the pressure of the oil way where the rotary motor is located when the rotary sensor detects that the pressure of the oil way where the rotary motor is located changes.

Further, the propulsion control valve is configured as a proportional pressure reducing valve.

Further, the control system further includes a hydraulic pump, a first switch, a second switch, and a pressure control valve. Wherein the hydraulic pump is hydraulically connected to the impact cylinder and the thrust cylinder. The first switch is electrically connected to the controller. The second switch is electrically connected to the controller. The pressure control valve has a first state in which the hydraulic pump is controlled to output hydraulic oil of a lower pressure and a second state in which the hydraulic pump is controlled to output hydraulic oil of a higher pressure. The controller is electrically connected to the pressure control valve to control the pressure control valve to switch to the first state when the first switch is closed and/or to control the pressure control valve to switch to the second state when the second switch is closed.

Further, the control system also comprises a pushing on-off valve. Wherein, impel the on-off valve hydraulic pressure and connect to impelling the hydro-cylinder. The controller is electrically connected to the propulsion on-off valve.

Further, the control system also includes a push reversing valve. Wherein, the propulsion reversing valve is hydraulically connected to the propulsion cylinder. The controller is electrically connected to the propulsion reversing valve.

Further, the control system also comprises a first speed regulating valve, a second speed regulating valve and a speed regulating reversing valve. Wherein, first governing valve one end hydraulic pressure is connected to rotary motor. One end of the second speed regulating valve is hydraulically connected to the rotary motor. The speed change valve has a third state hydraulically connected to the other end of the first speed valve and a fourth state hydraulically connected to the other end of the second speed valve. The upper limit value of the flow rate regulated by the first speed regulating valve is lower than the upper limit value of the flow rate regulated by the second speed regulating valve.

Further, the control system also comprises a safety valve group. The safety valve group is hydraulically connected to the rotary motor to release the oil path when the pressure of the oil path where the rotary motor is located exceeds a second preset threshold value.

As a second aspect of the application, some embodiments of the application claim a rock drill comprising a drill bit and the aforementioned control system.

The application has the beneficial effects that:

the control system comprises an impact oil cylinder, a propulsion oil cylinder, an impact control valve, a propulsion sensor and a controller, so that the impact frequency of the impact oil cylinder is matched with the pressure of an oil way where the propulsion oil cylinder is located.

More specifically, some embodiments of the present application may have the following specific benefits:

the control system further comprises a propulsion control valve, a rotary motor and a rotary sensor, so that the propulsion oil cylinder and the impact oil cylinder can be adjusted according to the real-time state of the rotary motor, the rock drilling machine can perform rock drilling work in a good state, the rock drilling efficiency is improved, and meanwhile the possibility of damage of a drilling tool is reduced.

The control system further comprises a pushing on-off valve, so that the controller judges that the pushing oil cylinder stops pushing when the pressure of the oil way where the rotary motor is located reaches a first preset threshold value, and the rock drill is prevented from being blocked.

The control system also comprises a first speed regulating valve, a second speed regulating valve and a speed regulating reversing valve, so that the rock drill is in a state of high rotating speed and low propelling speed when in hard rock stratum tunneling, and the loss of the drilling tool is effectively reduced.

Drawings

The accompanying drawings, which are included to provide a further understanding of the application, are incorporated in and constitute a part of this specification. The drawings and their description are illustrative of the application and are not to be construed as unduly limiting the application.

The same or similar reference numbers will be used throughout the drawings to refer to the same or like elements. It should be understood that the figures are schematic and that elements and components are not necessarily drawn to scale.

In the drawings:

fig. 1 is a schematic view of the overall structure of a rock drill according to an embodiment of the present application;

FIG. 2 is a block diagram of a control system according to the present application;

FIG. 3 is a schematic diagram of the control system in the embodiment of FIG. 1;

FIG. 4 is a schematic view of the configuration of the shock control valve of the embodiment of FIG. 1;

FIG. 5 is a schematic illustration of the configuration of the propulsion control valve in the embodiment of FIG. 1;

FIG. 6 is a schematic diagram showing the connection between the first shuttle valve and the rotary sensor in the embodiment shown in FIG. 1;

FIG. 7 is a schematic diagram showing the connection between the first shuttle valve and the shock reversing valve in the embodiment shown in FIG. 1;

FIG. 8 is a schematic diagram of the push on/off valve of the embodiment of FIG. 1;

FIG. 9 is a schematic illustration of the configuration of the thrust reverser valve of the embodiment of FIG. 1;

FIG. 10 is a schematic diagram showing the connection between the first speed valve and the speed/direction valve in the embodiment shown in FIG. 1;

FIG. 11 is a schematic view of the safety valve set in the embodiment shown in FIG. 1;

fig. 12 is a schematic diagram showing a connection relationship between each of the electronic control elements in the embodiment shown in fig. 1.

Meaning of reference numerals:

100. a rock drill; 101. a drill bit;

200. a control system; 201. an impact cylinder; 202. a thrust cylinder; 202a, a rod cavity; 202b, a rodless cavity; 203. an impact control valve; 204. advancing the sensor; 205. a controller; 206. a propulsion control valve; 207. a rotary motor; 208. a rotation sensor; 209. a first shuttle valve; 209a, a first oil inlet; 209b, a second oil inlet; 209c, a first oil outlet;

210. a hydraulic pump; 211. a first switch; 212. a second switch; 213. a pressure control valve; 214. an impact reversing valve; 214a, a first control oil port; 214b, a second control oil port; 215. a second shuttle valve; 215a, a third oil inlet; 215b, a fourth oil inlet; 215c, a second oil outlet; 216. pushing the on-off valve; 216a, a fifth oil inlet; 216b, a first oil return port; 216c, a third control oil port; 216d, a first valve core; 216e, a first coil; 217. advancing the reversing valve; 217a, a sixth oil inlet; 217b, a second oil return port; 217c, a third oil return port; 217d, a fourth control oil port; 217e, a fifth control oil port; 217f, a second spool; 217g, second coil; 218. a first speed regulating valve; 219. a second speed regulating valve;

220. a speed-regulating reversing valve; 220a, a seventh oil inlet; 220b, a third oil outlet; 220c, a fourth oil outlet; 220d, a third valve core; 220e, a handle; 221. a safety valve group; 221a, an overflow valve; 222. impact buffering mechanism.

Detailed Description

Embodiments of the present disclosure will be described in more detail below with reference to the accompanying drawings. While embodiments of the present disclosure are illustrated in the drawings, it should be understood that the present disclosure may be embodied in various forms and should not be construed as limited to the embodiments set forth herein. Rather, the embodiments are provided so that this disclosure will be thorough and complete. It should be understood that the drawings and embodiments of the present disclosure are for illustration purposes only and are not intended to limit the scope of the present disclosure.

It should be further noted that, for convenience of description, only a portion related to the present application is shown in the drawings. Features in embodiments of the present disclosure may be combined with each other without conflict.

It should be noted that the terms "first," "second," and the like in this disclosure are merely used to distinguish between different devices, modules, or units and are not used to define an order or interdependence of functions performed by the devices, modules, or units.

It should be noted that references to "one", "a plurality" and "a plurality" in this disclosure are intended to be illustrative rather than limiting, and those of ordinary skill in the art will appreciate that "one or more" is intended to be understood as "one or more" unless the context clearly indicates otherwise.

The present disclosure will be described in detail below with reference to the accompanying drawings in conjunction with embodiments.

Referring to fig. 1 to 12, a rock drill 100 is provided in this embodiment. Rock drill 100 includes a drill bit 101 and a control system 200. Control system 200 is used to control drill bit 101, wherein control system 200 includes a ram 201, a thrust cylinder 202, a ram control valve 203, a thrust sensor 204, and a controller 205. The percussion cylinder 201 is used to provide power to impact the drill bit 101 against the rock to be excavated. Thrust cylinder 202 is used to provide power to propel drill bit 101. The impact control valve 203 is used for controlling the flow rate of the oil path where the impact cylinder 201 is located. The propulsion sensor 204 is used for detecting the pressure of an oil path where the propulsion cylinder 202 is located. The controller 205 is electrically connected to the propulsion sensor 204. The shock control valve 203 is hydraulically connected to the shock cylinder 201. The controller 205 is electrically connected to the impact control valve 203 to obtain the flow rate of the oil path of the impact cylinder 201, which is adapted to the pressure of the oil path of the propulsion cylinder 202, when the pressure of the oil path of the propulsion cylinder 202 detected by the propulsion sensor 204 changes. The specific connection between the various parts of the control system 200 will be described in detail later.

By adopting the technical scheme, the propulsion sensor 204 detects the pressure value of the oil path where the propulsion cylinder 202 is located and converts the pressure value into an electric signal to be transmitted to the controller 205. In this embodiment, the control system 200 further includes a proportional amplifier, and the controller 205 sends a control signal to the proportional amplifier according to the received electrical signal, and the proportional amplifier outputs a corresponding current signal to control the opening of the impact control valve 203 and further control the set flow rate of the impact control valve 203, so as to control the flow rate of the oil path where the impact control valve 203 is located, that is, indirectly control the impact frequency of the impact oil cylinder 201, so that the impact frequency of the impact oil cylinder 201 is matched with the pressure of the oil path where the propulsion oil cylinder 202 is located. The controller 205 includes a PLC, which is a programmable logic controller, and in addition, the controller 205 may be integrated into the ECU.

More specifically, referring to fig. 4, in the present embodiment, the shock control valve 203 is configured as a proportional flow valve. The proportional flow valve can change the opening degree of the valve according to the electric signal transmitted to the coil to adjust the flow rate, and can quickly respond according to the pressure signal detected by the propulsion sensor 204 to adjust the impact frequency of the impact cylinder 201 because the transmission speed of the electric signal is high.

More specifically, control system 200 also includes a propulsion control valve 206, a rotary motor 207, and a rotation sensor 208. The propulsion control valve 206 is used for controlling the pressure of the oil path where the propulsion cylinder 202 is located. Rotary motor 207 is used to provide power to rotate drill bit 101. The rotation sensor 208 detects the pressure of the oil passage in which the rotation motor 207 is located. Propulsion control valve 206 is hydraulically connected to propulsion cylinder 202. The controller 205 is electrically connected to the rotation sensor 208. The controller 205 is electrically connected to the propulsion control valve 206 to obtain the pressure of the oil path of the propulsion cylinder 202 adapted to the pressure of the oil path of the rotary motor 207 when the rotary sensor 208 detects that the pressure of the oil path of the rotary motor 207 changes. More specifically, referring to fig. 5, propulsion control valve 206 is configured as a proportional pressure reducing valve in the present embodiment.

By adopting the above technical scheme, the rotation sensor 208 detects the pressure of the oil path where the rotation motor 207 is located and converts the pressure into an electrical signal to be transmitted to the controller 205, in this embodiment, the controller 205 sends the electrical signal to the propulsion control valve 206 according to the received electrical signal to the proportional amplifier, and the proportional amplifier outputs a corresponding current signal to further control the set pressure of the propulsion control valve 206, so as to adjust the pressure of the oil path where the propulsion cylinder 202 is located, that is, indirectly control the propulsion speed of the propulsion cylinder 202, so that the propulsion speed of the propulsion cylinder 202 is matched with the pressure of the oil path where the rotation motor 207 is located. In this way, when the pressure of the oil path where the rotary motor 207 is located changes, the propulsion control valve 206 controls the propulsion speed of the propulsion cylinder 202 to match the rotation speed of the rotary motor 207, and at the same time, the propulsion sensor 204 detects the pressure of the oil path where the propulsion cylinder 202 is located and transmits the pressure to the controller 205, and then controls the impact control valve 203, and finally controls the impact frequency of the impact cylinder 201, so that the working states of the propulsion cylinder 202, the impact cylinder 201 and the rotary motor 207 are adapted in real time.

In this embodiment, the pressure of the oil path to be detected is detected by the sensor and then is converted into an electrical signal to be transmitted to the controller 205, and the controller 205 transmits a control signal to each control valve. In this way, it is ensured that the thrust cylinder 202 and the impact cylinder 201 can be adjusted according to the real-time state of the rotary motor 207, so that the rock drilling machine 100 performs a rock drilling operation in a good state, the rock drilling efficiency is improved, and the possibility of damage to the drilling tool is reduced.

In addition, the use of the proportional flow valve and the proportional pressure reducing valve in the embodiment enables the flow of the oil path where the impact oil cylinder 201 is located and the pressure of the oil path where the propulsion oil cylinder 202 is located to be matched with the pressure of the oil path where the rotary motor 207 is located, so that the hydraulic system can adapt to changeable complex working conditions, and the limitation that the impact oil cylinder 201 or the propulsion oil cylinder 202 in the traditional hydraulic system can only realize two-stage control is broken through.

More specifically, referring to fig. 6, the control system 200 further includes a first shuttle valve 209. The first shuttle valve 209 is provided with a first oil inlet 209a, a second oil inlet 209b, and a first oil outlet 209c, the first oil inlet 209a being hydraulically connected to one end of the rotary motor 207, the second oil inlet 209b being hydraulically connected to the other end of the rotary motor 207. The first oil outlet 209c is hydraulically connected to the rotation sensor 208.

By adopting the above technical scheme, the first shuttle valve 209 is hydraulically connected to two control oil ports of the rotary motor 207, and hydraulic oil with higher pressure is selected to flow to the first oil outlet 209c and then to flow to the rotary sensor 208, so as to ensure that the rotary sensor 208 can detect the maximum pressure of the oil path where the rotary motor 207 is located, and accurately reflect the real-time state of the rotary motor 207.

More specifically, control system 200 also includes a hydraulic pump 210, a first switch 211, a second switch 212, and a pressure control valve 213. The hydraulic pump 210 is hydraulically connected to the impact cylinder 201 and the thrust cylinder 202. The first switch 211 is electrically connected to the controller 205. The second switch 212 is electrically connected to the controller 205. The pressure control valve 213 has a first state that controls the hydraulic pump 210 to output the lower pressure hydraulic oil and a second state that controls the hydraulic pump 210 to output the higher pressure hydraulic oil. The controller 205 is electrically connected to the pressure control valve 213 to control the pressure control valve 213 to switch to the first state when the first switch 211 is closed and/or to control the pressure control valve 213 to switch to the second state when the second switch 212 is closed.

With the above technical solution, when the rock drill 100 is required to be in the low impact frequency and low propulsion pressure state during the cutting process, the first switch 211 is closed, the controller 205 transmits an electrical signal to the pressure control valve 213 and controls the pressure control valve 213 to switch to the first state, and at this time, the pressure of the hydraulic oil output by the hydraulic pump 210 is lower, so that the rock drill 100 is in the low impact frequency and low propulsion pressure state.

When the rock drill 100 is required to be in a high-impact frequency high-propulsion pressure state during the cutting process, the second switch 212 is closed, the controller 205 transmits an electric signal to the pressure control valve 213 and controls the pressure control valve 213 to switch to the second state, and at this time, the hydraulic pump 210 outputs a higher pressure of hydraulic oil, so that the rock drill 100 is in a high-impact frequency high-propulsion pressure state.

The user can control the hydraulic pump 210 to output the pressure of the hydraulic oil by controlling whether the first switch 211 and the second switch 212 are closed, so that the maximum pressure of the oil path where the propulsion cylinder 202 and the impact cylinder 201 are positioned is changed to adapt to different working conditions.

More specifically, referring to fig. 7, the first switch 211 is configured as a pressure switch. The second switch 212 is configured as a pressure switch. The pressure control valve 213 is configured as a pressure cut-off valve. The control system 200 also includes an impact reversing valve 214 and a second shuttle valve 215. The shock reversing valve 214 is provided with a first control port 214a and a second control port 214b. The second shuttle valve 215 is provided with a third oil inlet 215a, a fourth oil inlet 215b and a second oil outlet 215c. The first control port 214a is hydraulically connected to the first switch 211. The second control port 214b is hydraulically connected to the second switch 212. The first control port 214a is hydraulically connected to the first oil inlet 209a. The second control port 214b is hydraulically connected to the second oil inlet 209b. The first oil outlet 209c is hydraulically connected to the impact cylinder 201.

With the above technical solution, when the rock drill 100 is in the working condition of tapping, the rock drill 100 is required to drill rock in the low-impact frequency and low-propulsion pressure state, and at this time, the valve core position of the impact reversing valve 214 is manually controlled, so that hydraulic oil flows out from the first control port and flows to the third oil inlet 215a, and the second control port 214b has no hydraulic oil flowing out. Because of the existence of the second shuttle valve 215, hydraulic oil cannot flow to the second control oil port 214b and the fourth oil inlet 215b, hydraulic oil flows to the first switch 211 and flows to the impact cylinder 201 through the second shuttle valve 215, at this time, the first switch 211 is closed and transmits an electrical signal to the controller 205, the controller 205 sends a control signal to the pressure control valve 213 according to the received electrical signal, so that the pressure control valve 213 is powered down, in this embodiment, after the pressure control valve 213 is powered down, the pump head pressure of the hydraulic pump 210 is switched to 130bar, the upper pressure limit of the propulsion control valve 206 is adjusted to 40bar, and the rock drill 100 enters the tapping mode.

When the rock drill 100 is in the drilling condition, the rock drill 100 is required to drill rock in the high-impact frequency and high-propulsion pressure state, and at this time, the valve core position of the impact reversing valve 214 is manually controlled, so that hydraulic oil flows out from the second control port and flows to the fourth oil inlet 215b, and no hydraulic oil flows out from the first control port 214 a. Because of the presence of the second shuttle valve 215, hydraulic oil cannot flow to the first control port 214a and the third oil inlet 215a, hydraulic oil flows to the second switch 212 and flows to the percussion cylinder 201 via the second shuttle valve 215, at this time, the second switch 212 is closed and transmits an electrical signal to the controller 205, the controller 205 sends a control signal to the pressure control valve 213 according to the received electrical signal, so that the pressure control valve 213 is powered, in this embodiment, after the pressure control valve 213 is powered, the pump head pressure of the hydraulic pump 210 is switched to 210bar, the upper pressure limit of the propulsion control valve 206 is adjusted to 80bar, and the rock drill 100 enters the drilling mode.

More specifically, control system 200 also includes a boost on-off valve 216. A propulsion on-off valve 216 is hydraulically connected to propulsion cylinder 202. The controller 205 is electrically connected to the boost on-off valve 216.

More specifically, referring to fig. 8, the propulsion on-off valve 216 is configured as a two-position three-way electromagnetic directional valve. The thrust cylinder 202 has a rod chamber 202a and a rodless chamber 202b. The two-position three-way electromagnetic directional valve is provided with a fifth oil inlet 216a, a first oil return port 216b and a third control oil port 216c. The two-position three-way electromagnetic directional valve includes a first spool 216d and a first coil 216e. A third control port 216c is hydraulically connected to the rodless chamber 202b. When the valve spool is in the first position, the fifth oil inlet 216a is communicated with the third control oil port 216c, and the propulsion cylinder 202 is in a propulsion state. When the valve element is located at the second position, the first oil return port 216b is communicated with the third control oil port 216c, and the propulsion cylinder 202 is in a stopped propulsion state.

By adopting the above technical scheme, the rotation sensor 208 transmits an electric signal to the controller 205, and the controller 205 determines that when the rotation sensor 208 detects that the pressure of the oil path where the rotation motor 207 is located reaches the first preset threshold value, the electric signal is transmitted to the first coil 216e, so that the first valve core 216d is switched from the first position to the second position, at this time, the third control oil port 216c is connected with the first oil return port 216b, the rodless cavity 202b of the pushing oil cylinder 202 is relieved, and the pushing oil cylinder 202 stops pushing, so that the rock drill 100 is prevented from continuing to push forward and then being blocked.

More specifically, control system 200 also includes a push diverter valve 217. A thrust reverser valve 217 is hydraulically connected to thrust cylinder 202. The controller 205 is electrically connected to the push diverter valve 217.

More specifically, referring to fig. 9, the push switch valve 217 is configured as a two-position five-way electromagnetic switch valve, and the push switch valve 217 is provided with a sixth oil inlet port 217a, a second oil return port 217b, a third oil return port 217c, a fourth control oil port 217d, and a fifth control oil port 217e. The fourth control port 217d is hydraulically connected to the rodless chamber 202b. The fifth control port 217e is hydraulically connected to the rod chamber 202a. The push switch valve 217 includes a second spool 217f and a second coil 217g. The second coil 217g is electrically connected to the controller 205.

With the above technical solution, when the second spool 217f is located at the third position, the sixth oil inlet 217a is communicated with the fourth control oil port 217d, the second oil return port 217b is communicated with the fifth control oil port 217e, and the propulsion cylinder 202 is in a propulsion state. When the second spool 217f is located at the fourth position, the sixth oil inlet 217a is communicated with the fifth control oil port 217e, the third oil return port 217c is communicated with the fourth control oil port 217d, and the thrust cylinder 202 is in a retracted state.

When the rotation sensor 208 detects that the pressure of the oil path where the rotation motor 207 is located reaches the first preset threshold, and the controller 205 controls the first oil return port 216b and the third control port 216c of the push-on/off valve 216 to be communicated, if the rotation sensor 208 detects that the pressure of the oil path where the rotation motor 207 is located continues to rise, the controller 205 sends an electrical signal to the second coil 217g to change the position of the second valve core 217f so as to switch from the third position to the fourth position, so that the impact cylinder 201 is switched to the retraction state.

More specifically, referring to fig. 10, the control system 200 further includes a first speed valve 218, a second speed valve 219, and a speed reversing valve 220. Wherein a first speed valve 218 is hydraulically connected at one end to the rotary motor 207. The second speed valve 219 is hydraulically connected at one end to the rotary motor 207. The speed change valve 220 has a third state hydraulically connected to the other end of the first speed valve 218 and a fourth state hydraulically connected to the other end of the second speed valve 219. The upper limit value of the flow rate regulated by the first speed valve 218 is lower than the upper limit value of the flow rate regulated by the second speed valve 219. In the present embodiment, the speed change valve 220 is configured as a two-position three-way manual change valve.

More specifically, the two-position three-way manual directional valve is provided with a seventh oil inlet 220a, a third oil outlet 220b, and a fourth oil outlet 220c. The two-position three-way manual diverter valve includes a third valve core 220d and a handle 220e. The third oil outlet 220b is hydraulically connected to the first speed valve 218. Fourth oil outlet 220c is hydraulically connected to second speed valve 219. When the third valve core 220d is located at the fifth position, the seventh oil inlet 220a and the third oil outlet 220b communicate, and when the third valve core 220d is located at the sixth position, the seventh oil inlet 220a and the fourth oil outlet 220c communicate.

By adopting the technical scheme, the rock drill 100 generally requires high rotating speed and low propelling speed when tunneling a hard rock stratum, and the loss of a drilling tool can be effectively reduced by reducing the propelling process. When the rock drill 100 drills a soft rock stratum with lower hardness, the drilling with large penetration degree with lower rotating speed and larger propelling speed can be realized, and the drilling efficiency can be improved under the condition of ensuring less loss of a drilling tool. In the present embodiment, when the rock to be drilled is soft rock, the user controls the handle 220e so that the third valve core 220d is located at the fifth position, the rotation speed of the rotation motor 207 is low, and when the rock to be drilled is hard rock, the user controls the handle 220e so that the third valve core 220d is located at the sixth position, the rotation speed of the rotation motor 207 is high.

Thus, the control system 200 in this embodiment not only has the hole drilling mode of the hole drilling condition and the hole drilling mode for the hole drilling condition, but also has the soft rock mode and the hard rock mode for different rock types, so that the rock drill 100 can cope with more diversified conditions, if the rock drill 100 encounters a hard rock layer without the first speed regulating valve 218, the second speed regulating valve 219 and the speed regulating reversing valve 220, the speed of the drilling motor needs to be increased, but in the existing control system 200, not only the highest rotation speed of the rotation motor 207 does not reach the hole drilling requirement of the hard rock, but also the pushing speed of the corresponding pushing cylinder 202 is higher due to the higher rotation speed of the rotation motor 207, which is unfavorable for the drilling of the hard rock layer.

In this embodiment, the first speed regulating valve 218, the second speed regulating valve 219 and the speed regulating reversing valve 220 solve the problem, when hard rock is encountered, only the speed regulating reversing valve 220 needs to be manually adjusted to enable the second speed regulating valve 219 to be communicated, so that the rotary motor 207 can obtain a higher highest rotating speed, and meanwhile, the impact control valve 203 is controlled to enable the second switch 212 to be closed, so that the upper pressure limit of the propulsion control valve 206 is guaranteed to be adjusted to 40bar, the propulsion speed of the propulsion cylinder 202 is lower, and the rock drill 100 can reach the optimal state of cutting hard rock.

More specifically, referring to FIG. 11, control system 200 also includes a relief valve block 221. The relief valve block 221 is hydraulically connected to the rotary motor 207 to relieve the pressure of the oil line where the rotary motor 207 is located when the pressure exceeds a second preset threshold. In the present embodiment, the relief valve group 221 includes two relief valves 221a.

With the above technical solution, when unexpected conditions such as drill rod blocking occur in the rock drill 100, the pressure of the oil path where the rotary motor 207 is located is increased and the pushing device cannot retract, the pressure of the oil path where the rotary motor 207 is located is continuously increased, and when the second preset threshold is reached, the relief valve 221a in the relief valve group 221 is relieved, so as to protect the rotary motor 207 from damage.

The control system 200 further includes an impact buffering mechanism 222 hydraulically connected to the impact cylinder 201.

With the above-described technical solution, the impact buffering mechanism 222 buffers the vibration generated by the impact cylinder 201.

The proportional amplifier is not shown in the drawings, and serves as a signal matching function, specifically, the proportional amplifier receives a weak control signal sent by the controller 205, and outputs currents required by the proportional flow valve and the proportional pressure valve. Since the proportional amplifier can output any magnitude of current within the allowable range after receiving the electric signal transmitted by the controller 205, the flow rate of the impact control valve 203 is matched with the pressure of the propulsion control valve 206.

The proportional flow valve is formed by combining a proportional electromagnet and a flow valve, and the proportional electromagnet is used for replacing a manual regulating device of a throttle valve or a speed regulating valve so as to input an electric signal to change the opening of the throttle valve, thereby regulating the flow of the system.

The proportional pressure reducing valve is a control valve for controlling the opening of a valve core of the pressure reducing valve by utilizing the electrifying change of an electromagnetic coil, when the electromagnetic coil is electrified, the valve core is opened by electromagnetic force, hydraulic oil flows through a valve cavity to act on the surface of the valve core to generate pressure, and the pressure is balanced with spring force and electromagnetic force, so that the pressure of a hydraulic oil way is controlled.

The application has been described in detail hereinabove with reference to specific exemplary embodiments thereof. It will be understood that various modifications and changes may be made without departing from the scope of the application as defined by the appended claims. The detailed description and drawings are to be regarded in an illustrative rather than a restrictive sense, and if any such modifications and variations are desired to be included within the scope of the application described herein. Furthermore, the background art is intended to illustrate the state of the art and the meaning of the development and is not intended to limit the application or the field of application of the application.

More specifically, although exemplary embodiments of the present application have been described herein, the present application is not limited to these embodiments, but includes any and all embodiments that have been modified, omitted, e.g., combined, adapted, and/or substituted between the various embodiments, as would be recognized by those skilled in the art in light of the foregoing detailed description. The limitations in the claims are to be interpreted broadly based on the language employed in the claims and not limited to examples described in the foregoing detailed description or during the prosecution of the application, which examples are to be construed as non-exclusive. Any steps recited in any method or process claims may be executed in any order and are not limited to the order presented in the claims. The scope of the application should, therefore, be determined only by the appended claims and their legal equivalents, rather than by the descriptions and examples given above.

Claims

1. A control system for controlling a drill bit of a rock drill, said control system comprising:

a percussion cylinder for providing power to impact the drill bit against rock to be excavated;

a propulsion cylinder for providing power to propel the drill bit;

the method is characterized in that:

the control system further includes:

the impact control valve is used for controlling the flow of an oil way where the impact oil cylinder is positioned;

the propulsion sensor is used for detecting the pressure of an oil way where the propulsion oil cylinder is positioned;

a controller electrically connected to the propulsion sensor;

wherein the impact control valve is hydraulically connected to the impact cylinder; the controller is electrically connected to the impact control valve to acquire the flow of the oil way where the impact oil cylinder is located, which is matched with the pressure of the oil way where the thrust oil cylinder is located when the pressure of the oil way where the thrust oil cylinder is located, which is detected by the thrust sensor, is changed.

2. The control system of claim 1, wherein:

the impact control valve is configured as a proportional flow valve.

3. The control system of claim 1, wherein:

the control system further includes:

the propulsion control valve is used for controlling the pressure of an oil way where the propulsion oil cylinder is positioned;

a rotary motor for providing power to rotate the drill bit;

the rotary sensor is used for detecting the pressure of an oil way where the rotary motor is positioned;

wherein the propulsion control valve is hydraulically connected to the propulsion cylinder; the controller is electrically connected to the rotation sensor; the controller is electrically connected to the propulsion control valve so as to acquire the pressure of the oil way where the propulsion oil cylinder is located, which is matched with the pressure of the oil way where the rotary motor is located when the rotary sensor detects that the pressure of the oil way where the rotary motor is located changes.

4. A control system according to claim 3, characterized in that:

the propulsion control valve is configured as a proportional pressure reducing valve.

5. The control system of claim 4, wherein:

the control system further includes:

a hydraulic pump hydraulically connected to the impact cylinder and the thrust cylinder;

the first switch is electrically connected to the controller;

the second switch is electrically connected to the controller;

a pressure control valve having a first state controlling the hydraulic pump to output a lower pressure hydraulic oil and a second state controlling the hydraulic pump to output a higher pressure hydraulic oil.

The controller is electrically connected to the pressure control valve to control the pressure control valve to switch to the first state when the first switch is closed and/or to control the pressure control valve to switch to the second state when the second switch is closed.

6. The control system of claim 5, wherein:

the control system further includes:

a propulsion on-off valve hydraulically connected to the propulsion cylinder;

wherein, the controller is electrically connected to the propulsion on-off valve.

7. The control system of claim 6, wherein:

the control system further includes:

a propulsion reversing valve hydraulically connected to the propulsion cylinder;

wherein, the controller is electrically connected to the propulsion reversing valve.

8. The control system according to any one of claims 1 to 7, characterized in that:

the control system further includes:

a first speed control valve, one end of which is hydraulically connected to the rotary motor;

a second speed regulating valve, one end of which is hydraulically connected to the rotary motor;

a speed change valve having a third state hydraulically connected to the other end of the first speed valve and a fourth state hydraulically connected to the other end of the second speed valve;

the upper limit value of the flow speed regulated by the first speed regulating valve is lower than the upper limit value of the flow speed regulated by the second speed regulating valve.

9. The control system of claim 8, wherein:

the control system further includes:

and the safety valve group is hydraulically connected to the rotary motor so as to release the oil circuit when the pressure of the oil circuit where the rotary motor is positioned exceeds a second preset threshold value.

10. A rock drill, characterized in that: the rock drill comprising a drill bit and a control system according to any one of claims 1 to 9.