Hydraulic control system and jumbo

Abstract

The application discloses a kind of hydraulic control system and rock drilling jumbo, including oil tank, hydraulic pump, rock drilling assembly, control valve group, first reversing valve, second reversing valve, logic valve, pressure compensation valve and feedback valve group, the oil outlet of oil tank is communicated with hydraulic pump, the oil outlet of hydraulic pump is respectively communicated with control valve group, first reversing valve and logic valve, rock drilling assembly is communicated with oil tank, the oil inlet of first reversing valve is respectively communicated with the liquid control port of logic valve, feedback valve group, second reversing valve and oil tank;Relative to prior art, through the seamless switching of constant pressure control and load sensitive control, the arbitrary combination of two working states and two control modes is matched, and the rock drilling impact pressure is ensured not to be affected by other load pressure during rock drilling, so that the rock drilling assembly cannot be overpressure, can be effectively protected, meets the working condition requirement of rock drilling jumbo in different occasions, different scenes, greatly improves the versatility of rock drilling jumbo, practicality is strong, is suitable for being widely promoted and application.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of rock drilling equipment, in particular, to a hydraulic control system. In addition, the present application also relates to a rock drilling jumbo comprising the above-mentioned hydraulic control system. BACKGROUND

[0002] The rock drilling jumbo is an important drilling equipment in modern drilling and blasting method tunnel construction, which has the advantages of high drilling efficiency, high safety factor, good working environment and low labor intensity, and is widely used in tunnel construction, mineral exploitation, water conservancy facility construction and other occasions. The working condition requirements of the rock drilling jumbo are different under different application occasions, and the working condition requirements of the rock drilling jumbo are also different under the same application occasion.

[0003] At present, there are two control modes of the existing hydraulic control system of the rock drilling jumbo. One is constant pressure control, which has high action response and low action operation delay, high pressure standby, low energy consumption under the working condition of small load change, and high energy consumption under the working condition of large load change, which is relatively not energy-saving. The other is load sensitive control, which is relatively energy-saving compared with constant pressure control, the outlet pressure and flow of the main pump change with the change of load demand, and the low pressure standby, but the action response of the load sensitive control is relatively low, and the action operation delay is relatively high.

[0004] In addition, there are two control modes of the rock drilling impact of the existing rock drilling jumbo. One is pump control rock drilling, the outlet pressure of the main system is determined by the rock drilling pressure when rock drilling, which is relatively energy-saving, but many working condition requirements need other actions when rock drilling. When the rock drilling impact is low, the outlet system pressure of the main pump is low, and the output pressure of the pump control rock drilling is low, which will cause the other actions to be unable to be executed, and when the pump control rock drilling is adopted, if the other actions adopt the load sensitive control system, the rock drilling machine will not be effectively protected. The other is valve control rock drilling, at this time, whether the main system adopts constant pressure control or load sensitive control, the pressure of the rock drilling impact is controlled by the rock drilling impact relief valve, the rock drilling pressure and the outlet pressure of the main system are controlled separately when rock drilling, which is suitable for most working conditions.

[0005] As disclosed in Chinese patent application CN113638943A, a hydraulic control system for impact includes a hydraulic pump, a first reversing valve, a second reversing valve, a non-balanced cone valve, a shuttle valve and a multi-way valve. The hydraulic pump is connected with the multi-way valve through an oil outlet pipeline. An actuator is connected to the oil outlet pipeline through the non-balanced cone valve. The load-sensitive oil way of the hydraulic pump is connected with the first reversing valve through the shuttle valve. The first reversing valve is connected with the second reversing valve. The second reversing valve is connected to the oil outlet pipeline. The second reversing valve is also connected with the non-balanced cone valve. Through the reversing of the first reversing valve and the second reversing valve, combined with the opening and closing action of the non-balanced cone valve, two different pressure level working modes of the boom mode and the rock drilling mode can be realized. When switching to the rock drilling mode, the actuator can start the hydraulic impact, and the pressure loss is small, reducing the system heating and improving the system efficiency. In the rock drilling mode, the actuator can impact while other auxiliary actions of the rock drilling jumbo are performed. However, the hydraulic system is essentially pump-controlled rock drilling. The boom and other actuators need constant pressure control of the main system. However, the pressure of the main system will be affected by the rock drilling pressure when rock drilling, which cannot meet all the working condition requirements.

[0006] In summary, the existing hydraulic control system of the rock drilling jumbo can only meet part of the working condition requirements, resulting in the need to make great changes to the hydraulic control system to meet the working condition requirements when the rock drilling jumbo works in different working conditions. The hydraulic system of the rock drilling jumbo has poor versatility. SUMMARY

[0007] The present application provides a hydraulic control system and a rock drilling jumbo to solve the technical problem that the existing hydraulic control system of the rock drilling jumbo can only meet part of the working condition requirements, and the hydraulic system of the rock drilling jumbo has poor versatility.

[0008] According to one aspect of the present application, a hydraulic control system is provided, comprising an oil tank, a hydraulic pump, a rock drilling assembly, a control valve group, a first directional valve, a second directional valve, a logic valve, a pressure compensation valve and a feedback valve group, an oil outlet of the oil tank being communicated with the hydraulic pump, an oil outlet of the hydraulic pump being communicated with the control valve group, the first directional valve and the logic valve respectively, the rock drilling assembly being communicated with the oil tank, an oil inlet of the first directional valve being communicated with the logic valve, the feedback valve group, the second directional valve and the oil tank respectively, an oil outlet of the logic valve being communicated with the pressure compensation valve, the pressure compensation valve being communicated with the rock drilling assembly and the feedback valve group respectively and being used for controlling the change of a rock drilling pressure of the rock drilling assembly, a load feedback port of the control valve group being communicated with an oil inlet of the second directional valve and being used for feeding the maximum load pressure oil of an actuator in a rock drilling jumbo, an oil inlet of the second directional valve being communicated with the feedback valve group, an oil outlet of the feedback valve group being communicated with a load port of the hydraulic pump, the first directional valve being used for cooperating with the logic valve to control the opening and closing of the rock drilling assembly, the second directional valve being used for controlling the on-off of the load feedback of the control valve group, the feedback valve group being used for cooperating with the first directional valve, the second directional valve and the pressure compensation valve to control the hydraulic oil delivered to the load port of the hydraulic pump, so as to realize the switching of the constant pressure control mode and the load sensitive control mode of the hydraulic control system during rock drilling and non-rock drilling, and avoid the influence of the load pressure on the rock drilling pressure.

[0009] As a further improvement of the above technical solution:

[0010] Further, the feedback valve group comprises a first shuttle valve, a second shuttle valve, a first overflow valve, a second overflow valve and a proportional overflow valve, an oil inlet of the first shuttle valve being communicated with the first directional valve and the second directional valve respectively, an oil inlet of the second shuttle valve being communicated with the first shuttle valve and the pressure compensation valve respectively, an oil outlet of the second shuttle valve being communicated with the load port of the hydraulic pump, the first overflow valve being communicated with the oil inlet of the first directional valve and the oil tank respectively and being used for controlling the maximum oil pressure delivered by the first directional valve to the first shuttle valve, the second overflow valve being communicated with the pressure compensation valve and the oil tank respectively and being used for controlling the maximum rock drilling pressure of the rock drilling assembly, the proportional overflow valve being communicated with the pressure compensation valve and the oil tank respectively and being used for controlling the rock drilling pressure of the rock drilling assembly.

[0011] Further, a first damper is arranged between the first directional valve and the first shuttle valve.

[0012] Further, a second damper is arranged between the pressure compensation valve and the second shuttle valve, an oil outlet of the second damper being communicated with a control valve port of the pressure compensation valve.

[0013] Further, the second overflow valve and the proportional overflow valve are arranged in parallel.

[0014] Further, the first directional valve is an electromagnetic directional valve; and / or the second directional valve is an electromagnetic directional valve.

[0015] Further, a third overflow valve is arranged between the oil inlet of the second directional valve and the oil tank.

[0016] Further, the third damper is arranged between the first reversing valve and the second reversing valve.

[0017] Further, the hydraulic control system further comprises a prime mover connected with the hydraulic pump.

[0018] According to another aspect of the present application, there is also provided a rock drilling jumbo comprising the above-mentioned hydraulic control system.

[0019] The present application has the following beneficial effects:

[0020] The hydraulic control system of the present application, the hydraulic oil in the oil tank can be pumped by the hydraulic pump and output to the rock drilling assembly and the control valve group respectively, in the conveying process, the first reversing valve cooperates with the logic valve to control the opening and closing of the rock drilling assembly, so that the hydraulic control system has two working states of rock drilling and non-rock drilling, the pressure compensation valve controls the rock drilling pressure change of the rock drilling assembly, so that the rock drilling pressure is not affected by the load pressure, the second reversing valve controls the on-off of the load feedback of the control valve group, the feedback valve group cooperates with the first reversing valve, the second reversing valve and the pressure compensation valve to control the hydraulic oil conveyed to the load port of the hydraulic pump, so as to realize the switching of the constant pressure control mode and the load sensitive control mode of the hydraulic control system during rock drilling and non-rock drilling, and avoid the influence of rock drilling pressure on load pressure, through rock drilling and non-rock drilling, constant pressure control, load sensitive control, constant pressure control and load sensitive control during rock drilling are realized by the combination of constant pressure control and load sensitive control mode, and the switching of the four control modes can meet all working condition requirements: compared with the prior art, the present application realizes seamless switching of constant pressure control and load sensitive control, arbitrary combination of two working states and two control modes, and ensures that the rock drilling impact pressure is not affected by other load pressure during rock drilling, so that the rock drilling assembly is not over-pressured and can be effectively protected, meeting all working condition requirements of the rock drilling jumbo in different occasions and different scenes, greatly improving the versatility of the rock drilling jumbo, and being practical, suitable for wide promotion and application.

[0021] In addition to the objects, features, and advantages described above, the present application has other objects, features, and advantages. The present application will be described in further detail below with reference to the drawings. BRIEF DESCRIPTION OF DRAWINGS

[0022] The accompanying drawings, which form a part of this application, are included to provide a further understanding of the application, illustrate embodiments of the present application and assist in the explanation of the present application. In the drawings:

[0023] Figure 1 is the hydraulic control principle diagram of the hydraulic control system of the preferred embodiment of the present application.

[0024] Legend:

[0025] 11. Oil tank; 12. Hydraulic pump; 13. Rock drilling assembly; 14. Control valve group; 15. First directional valve; 16. Second directional valve; 17. First shuttle valve; 18. Second shuttle valve; 19. First relief valve; 20. Second relief valve; 21. Proportional relief valve; 22. First damper; 23. Pressure compensation valve; 24. Second damper; 25. Third relief valve; 26. Third damper; 27. Prime mover; 28. Logic valve. Detailed Implementation

[0026] The embodiments of the present invention will be described in detail below with reference to the accompanying drawings. However, the present invention can be implemented in many different ways as defined and covered below.

[0027] like Figure 1 As shown, the hydraulic control system of this embodiment includes an oil tank 11, a hydraulic pump 12, a rock drilling assembly 13, a control valve group 14, a first directional valve 15, a second directional valve 16, a logic valve 28, a pressure compensation valve 23, and a feedback valve group. The oil outlet of the oil tank 11 is connected to the hydraulic pump 12. The oil outlet of the hydraulic pump 12 is connected to the control valve group 14, the first directional valve 15, and the logic valve 28. The rock drilling assembly 13 is connected to the oil tank 11. The oil inlet of the first directional valve 15 is connected to the hydraulic control port of the logic valve 28, the feedback valve group, the second directional valve 16, and the oil tank 11. The oil outlet of the logic valve 28 is connected to the pressure compensation valve 23. The pressure compensation valve 23 is connected to the rock drilling assembly 13 and the feedback valve group and is used to control the rock drilling pressure change of the rock drilling assembly 13. The load feedback port of the control valve group 14 is connected to the oil inlet of the second directional valve 16 and is used to provide feedback on the maximum load pressure oil of the actuator in the rock drilling rig. The oil outlet of the second directional valve 16 is connected to the feedback valve group, and the oil outlet of the feedback valve group is connected to the load port of the hydraulic pump 12. The first directional valve 15 is used to cooperate with the logic valve 28 to control the opening and closing of the rock drilling assembly 13. The second directional valve 16 is used to control the on / off of the load feedback of the control valve group 14. The feedback valve group is used to cooperate with the first directional valve 15, the second directional valve 16 and the pressure compensation valve 23 to control the hydraulic oil delivered to the load port of the hydraulic pump 12, thereby realizing the switching between the constant pressure control mode and the load-sensitive control mode of the hydraulic control system during rock drilling and non-rock drilling, and avoiding the rock drilling pressure from being affected by the load pressure.

[0028] Optionally, the rock drilling assembly 13 is a rock drill.

[0029] Optionally, the oil inlet of the first directional valve 15 includes an oil inlet, an oil outlet, and two working oil ports.

[0030] Optionally, the oil inlet of the second directional valve 16 includes an oil inlet, an oil outlet, and two working oil ports.

[0031] Optionally, the hydraulic pump 12 is a variable displacement piston pump with load feedback.

[0032] like Figure 1 As shown, specifically, in the hydraulic control system of the present invention, the hydraulic oil in the oil tank 11 is pumped by the hydraulic pump 12 and output to the rock drilling assembly 13 and the control valve group 14 respectively. During the delivery process, the opening and closing of the rock drilling assembly 13 is controlled by the first reversing valve 15 in cooperation with the logic valve 28, so that the hydraulic control system has two working states: rock drilling and non-rock drilling. The rock drilling pressure of the rock drilling assembly 13 is controlled by the pressure compensation valve 23 so that the rock drilling pressure is not affected by the load pressure. The load feedback of the control valve group 14 is controlled by the second reversing valve 16. The feedback valve group cooperates with the first reversing valve 15, the second reversing valve 16 and the pressure compensation valve 23 to control the hydraulic oil delivered to the load port of the hydraulic pump 12, thereby realizing the constant pressure control mode and the load sensitive control mode of the hydraulic control system during rock drilling and non-rock drilling. This solution allows for seamless switching between constant pressure and load-sensitive control modes, and avoids the impact of load pressure on drilling pressure. By combining drilling and non-drilling modes with constant pressure and load-sensitive control modes, it achieves constant pressure control for non-drilling, load-sensitive control for non-drilling, constant pressure control for drilling, and load-sensitive control for drilling. These four control modes can meet all working conditions. Compared to existing technologies, this solution seamlessly switches between constant pressure and load-sensitive control, allowing for arbitrary combinations of the two working states and control modes. Furthermore, it ensures that the drilling impact pressure is not affected by other load pressures during drilling, preventing overpressure on the drilling component 13 and providing effective protection. This meets all working conditions of the drilling rig in different occasions and scenarios, greatly improving the versatility and practicality of the drilling rig, making it suitable for widespread promotion and application.

[0033] It should be understood that the principle by which the pressure compensation valve 23 controls the change in drilling pressure of the rock drilling assembly 13 so that the drilling pressure is not affected by the load pressure is as follows: By controlling the change in drilling pressure of the rock drilling assembly 13 through the pressure compensation valve 23, even if the output pressure of the hydraulic pump 12 changes and the output pressure is greater than the drilling pressure required, the excess pressure will be lost at the pressure compensation valve 23, ensuring that the pressure flow of the rock drilling assembly 13 is not affected, thereby maintaining the stability of the impact force, improving the accuracy of the impact frequency, and protecting the life of the rock drilling assembly 13; and when adjusting the drilling pressure, even if other load pressures affect the output pressure of the hydraulic pump 12 and increase it, the drilling pressure will not be affected, so that the rock drilling assembly 13 will not be over-pressured, thus effectively protecting the rock drilling assembly 13.

[0034] It should be understood that the rock drilling pressure refers to the hydraulic oil pressure when the oil outlet of the pressure compensation valve 23 delivers hydraulic oil to the rock drilling assembly 13, the load pressure refers to the hydraulic oil pressure when the load feedback port of the control valve group 14 delivers hydraulic oil to the feedback valve group, and the output pressure refers to the output port pressure of the hydraulic pump 12.

[0035] It should be understood that the on-off of the control of the load feedback of the control valve group 14 refers to whether the hydraulic oil flowing out of the load feedback port of the control valve group 14 can flow into the feedback valve group.

[0036] It should be understood that the actuator is a working component other than the rock drilling mechanism on the rock drilling jumbo, such as the boom, and the load feedback port of the control valve group 14 feeds the hydraulic oil with the largest load pressure in the working component to the second directional valve 16.

[0037] As shown in Figure 1 In the embodiment, the feedback valve group includes a first shuttle valve 17, a second shuttle valve 18, a first overflow valve 19, a second overflow valve 20, and a proportional overflow valve 21. The oil inlet of the first shuttle valve 17 is in communication with the first directional valve 15 and the second directional valve 16, respectively. The oil inlet of the second shuttle valve 18 is in communication with the first shuttle valve 17 and the pressure compensation valve 23, respectively. The oil outlet of the second shuttle valve 18 is in communication with the load port of the hydraulic pump 12. The first overflow valve 19 is in communication with the oil tank 11 and the oil outlet of the first directional valve 15, respectively, and is used to control the maximum oil pressure delivered by the first directional valve 15 to the first shuttle valve 17. The second overflow valve 20 is in communication with the oil tank 11 and the pressure compensation valve 23, respectively, and is used to control the maximum rock drilling pressure of the rock drilling assembly 13. The proportional overflow valve 21 is in communication with the oil tank 11 and the pressure compensation valve 23, respectively, and is used to control the rock drilling pressure of the rock drilling assembly 13.

[0038] As shown in Figure 1As shown, specifically, by the oil inlet of the first spool valve 17 being communicated with the first reversing valve 15 and the second reversing valve 16 respectively, the oil outlet of the hydraulic pump 12 is communicated with the oil inlet of the first spool valve 17 through the first reversing valve 15, the load feedback port of the control valve group 14 is communicated with the oil inlet of the first spool valve 17 through the second reversing valve 16, the oil inlet of the second spool valve 18 is communicated with the oil outlet of the first spool valve 17 and the pressure compensation valve 23 respectively, the first spool valve 17 compares the set pressure of the first overflow valve 19 and the load pressure oil of the control valve group 14 when drilling, and delivers the pressure oil with the greater pressure to the second spool valve 18, the second spool valve 18 compares the drilling pressure oil of the drilling assembly 13 with the greater one of the set pressure of the first overflow valve 19 and the load feedback pressure oil of the control valve group 14, and delivers the pressure oil with the greater pressure to the load port of the hydraulic pump 12, so as to realize the constant pressure control or the load sensitive control when drilling; the first overflow valve 19 controls the maximum oil pressure delivered by the first reversing valve 15 to the first spool valve 17, so as to control whether the drilling pressure and the output pressure affect each other, the second overflow valve 20 controls the maximum drilling pressure of the drilling assembly 13, so as to control whether the drilling pressure and the output pressure affect each other; when the set pressure of the first overflow valve 19 is higher than the set pressure of the second overflow valve 20, the output pressure is not affected by the drilling pressure and is a constant value, and the hydraulic control system is in the constant pressure control mode when drilling; when the set pressure of the first overflow valve 19 is lower than the set pressure of the second overflow valve 20, the output pressure depends on the drilling pressure and is a variable value, and the hydraulic control system is in the load sensitive control mode when drilling.

[0039] Optionally, the first overflow valve 19 is a pilot overflow valve. Optionally, the second overflow valve 20 is a pilot overflow valve. Optionally, the proportional overflow valve 21 is an electric proportional overflow valve.

[0040] It should be understood that for the working condition that the hydraulic pump 12 needs to output pressure higher than the drilling pressure of the drilling assembly 13 (for example, the drilling assembly 13 needs to be connected with high-pressure buffer oil, or the control valve group 14 needs to work), at this time, the set pressure of the first overflow valve 19 in the feedback valve group is greater than the set pressure of the second overflow valve 20, and the hydraulic control system is in a constant pressure control mode during drilling; if the second reversing valve 16 is not powered, that is, the load feedback oil of the control valve group 14 enters the feedback valve group, then the hydraulic oil output by the hydraulic pump 12 and the hydraulic oil flowing out of the load feedback port of the control valve group 14 are controlled by the feedback valve group, that is, the control output pressure and the drilling pressure do not affect each other, and the hydraulic pump 12 outputs the hydraulic oil with greater pressure, which can also meet the requirement that the output pressure of the hydraulic pump 12 is higher than the drilling pressure, and under the action of the pressure compensation valve 23, the drilling assembly 13 is effectively protected; for the working condition that the hydraulic pump 12 does not need to output pressure higher than the drilling pressure of the drilling assembly 13 (for example, the drilling assembly 13 does not need to be connected with high-pressure buffer oil, or the control valve group 14 does not need to work), at this time, the set pressure of the first overflow valve 19 in the feedback valve group should be set to the minimum pressure, and the hydraulic oil flowing out of the pressure compensation valve 23 is controlled by the feedback valve group to be delivered to the load port of the hydraulic pump 12, that is, the load pressure depends on the drilling pressure, and the hydraulic control system is in a load-sensitive control mode during drilling, which reduces energy consumption and saves energy during the drilling process.

[0041] As shown in Figure 1 In the embodiment, when the first reversing valve 15 is in the first working position, the oil inlet and the oil outlet of the logic valve 28 are not connected, the drilling assembly 13 does not work, and the hydraulic control system is in a non-drilling working state; when the first reversing valve 15 is in the second working position, the oil inlet and the oil outlet of the logic valve 28 are connected, the drilling assembly 13 works, and the hydraulic control system is in a drilling working state.

[0042] As shown in Figure 1 In the embodiment, the first damping 22 is arranged between the first reversing valve 15 and the first shuttle valve 17. Specifically, when the first reversing valve 15 is in the second working position, the hydraulic oil flowing into the first reversing valve 15 flows to the first shuttle valve 17, and the maximum oil pressure of the oil path between the first reversing valve 15 and the first shuttle valve 17 depends on the first overflow valve 19, that is, the load feedback control oil path of the hydraulic pump 12, and the first damping 22 limits the flow of the load feedback control oil path of the hydraulic pump 12 during drilling, so as to adjust the response speed of the first overflow valve 19, and improve the stability, pressure regulating accuracy and reliability.

[0043] As shown in Figure 1As shown, in the embodiment, a second damper 24 is arranged between the pressure compensation valve 23 and the second shuttle valve 18, and an oil outlet of the second damper 24 is communicated with a control valve port of the pressure compensation valve 23. Specifically, when the first reversing valve 15 is in the second working position, the hydraulic oil flowing into the logic valve 28 flows to the pressure compensation valve 23, the hydraulic oil flowing out of the oil outlet of the pressure compensation valve 23 flows to the rock drilling assembly 13 and the second damper 24 respectively, and then flows to the second shuttle valve 18 and the control valve port of the pressure compensation valve 23 through the second damper 24, so as to perform pressure compensation when the rock drilling assembly 13 works, and then the rock drilling pressure is controlled through the second overflow valve 20 and the proportional overflow valve 21; the maximum oil pressure of the oil path between the pressure compensation valve 23 and the second shuttle valve 18 depends on the second overflow valve 20, and the oil pressure of the oil path between the pressure compensation valve 23 and the second shuttle valve 18 depends on the proportional overflow valve 21, which is essentially a rock drilling pressure feedback oil path when rock drilling, the flow of the oil path is limited through the second damper 24, and the pressure difference before and after the second damper 24 is constant, so as to adjust the response speed of the second overflow valve 20 and the proportional overflow valve 21, and improve the stability, pressure regulating accuracy and reliability.

[0044] As shown, Figure 1 In the embodiment, the second overflow valve 20 and the proportional overflow valve 21 are arranged in parallel. Specifically, the second overflow valve 20 and the proportional overflow valve 21 are arranged in parallel to realize the synergistic effect of safety protection and dynamic pressure regulation, and then to perform safety redundant protection on the work of the rock drilling assembly 13, to inhibit dynamic interference, and to reduce the burden of the proportional overflow valve 21.

[0045] It should be understood that when the second reversing valve 16 is in the first working position, the hydraulic oil fed back by the load feedback port of the control valve group 14 flows to the first shuttle valve 17 through the second reversing valve 16, and then flows to the second shuttle valve 18 through the first shuttle valve 17, and then flows to the load port of the hydraulic pump 12 through the second shuttle valve 18, which is a load feedback oil path of the control valve group 14.

[0046] In the embodiment, the first reversing valve 15 is an electromagnetic reversing valve. Specifically, when the first reversing valve 15 is in the first working position, the first reversing valve 15 is not powered; when the first reversing valve 15 is in the second working position, the first reversing valve 15 is powered; the electromagnetic reversing valve is used to realize quick reversing, and ensures compact structure and high reliability.

[0047] In the embodiment, the second reversing valve 16 is an electromagnetic reversing valve. Specifically, when the second reversing valve 16 is in the first working position, the second reversing valve 16 is not powered; when the second reversing valve 16 is in the second working position, the second reversing valve 16 is powered; the electromagnetic reversing valve is used to realize quick reversing, and ensures compact structure and high reliability.

[0048] As shown, Figure 1As shown in the figure, in the embodiment, a third overflow valve 25 is arranged between the oil inlet of the second reversing valve 16 and the oil tank 11. Specifically, when the second reversing valve 16 is in the first working position, the maximum oil pressure of the load feedback oil circuit of the control valve group 14 is controlled by the third overflow valve 25 to play a safety protection role on the hydraulic pump 12; when the second reversing valve 16 is in the second working position, the maximum pressure output by the hydraulic pump 12 is controlled by the third overflow valve 25 to prevent the pressure cut-off failure of the hydraulic pump 12 from playing a protection role on the entire hydraulic system.

[0049] As shown in the figure, in the embodiment, a third overflow valve 25 is arranged between the oil inlet of the second reversing valve 16 and the oil tank 11. Specifically, when the second reversing valve 16 is in the first working position, the maximum oil pressure of the load feedback oil circuit of the control valve group 14 is controlled by the third overflow valve 25 to play a safety protection role on the hydraulic pump 12; when the second reversing valve 16 is in the second working position, the maximum pressure output by the hydraulic pump 12 is controlled by the third overflow valve 25 to prevent the pressure cut-off failure of the hydraulic pump 12 from playing a protection role on the entire hydraulic system. Figure 1 As shown in the figure, in the embodiment, a third overflow valve 25 is arranged between the oil inlet of the second reversing valve 16 and the oil tank 11. Specifically, when the second reversing valve 16 is in the first working position, the maximum oil pressure of the load feedback oil circuit of the control valve group 14 is controlled by the third overflow valve 25 to play a safety protection role on the hydraulic pump 12; when the second reversing valve 16 is in the second working position, the maximum pressure output by the hydraulic pump 12 is controlled by the third overflow valve 25 to prevent the pressure cut-off failure of the hydraulic pump 12 from playing a protection role on the entire hydraulic system.

[0050] Optionally, the third overflow valve 25 is a pilot overflow valve.

[0051] As shown in the figure, in the embodiment, a third overflow valve 25 is arranged between the oil inlet of the second reversing valve 16 and the oil tank 11. Specifically, when the second reversing valve 16 is in the first working position, the maximum oil pressure of the load feedback oil circuit of the control valve group 14 is controlled by the third overflow valve 25 to play a safety protection role on the hydraulic pump 12; when the second reversing valve 16 is in the second working position, the maximum pressure output by the hydraulic pump 12 is controlled by the third overflow valve 25 to prevent the pressure cut-off failure of the hydraulic pump 12 from playing a protection role on the entire hydraulic system. Figure 1 As shown in the figure, in the embodiment, a third overflow valve 25 is arranged between the oil inlet of the second reversing valve 16 and the oil tank 11. Specifically, when the second reversing valve 16 is in the first working position, the maximum oil pressure of the load feedback oil circuit of the control valve group 14 is controlled by the third overflow valve 25 to play a safety protection role on the hydraulic pump 12; when the second reversing valve 16 is in the second working position, the maximum pressure output by the hydraulic pump 12 is controlled by the third overflow valve 25 to prevent the pressure cut-off failure of the hydraulic pump 12 from playing a protection role on the entire hydraulic system.

[0052] As shown in the figure, in the embodiment, a third overflow valve 25 is arranged between the oil inlet of the second reversing valve 16 and the oil tank 11. Specifically, when the second reversing valve 16 is in the first working position, the maximum oil pressure of the load feedback oil circuit of the control valve group 14 is controlled by the third overflow valve 25 to play a safety protection role on the hydraulic pump 12; when the second reversing valve 16 is in the second working position, the maximum pressure output by the hydraulic pump 12 is controlled by the third overflow valve 25 to prevent the pressure cut-off failure of the hydraulic pump 12 from playing a protection role on the entire hydraulic system. Figure 1 As shown in the figure, in the embodiment, a third overflow valve 25 is arranged between the oil inlet of the second reversing valve 16 and the oil tank 11. Specifically, when the second reversing valve 16 is in the first working position, the maximum oil pressure of the load feedback oil circuit of the control valve group 14 is controlled by the third overflow valve 25 to play a safety protection role on the hydraulic pump 12; when the second reversing valve 16 is in the second working position, the maximum pressure output by the hydraulic pump 12 is controlled by the third overflow valve 25 to prevent the pressure cut-off failure of the hydraulic pump 12 from playing a protection role on the entire hydraulic system.

[0053] Load-sensitive control mode when not drilling:

[0054] The first reversing valve 15 is in the first working position, the a port and the b port of the first reversing valve 15 are communicated, the c port and the d port are communicated, the second reversing valve 16 is in the first working position, the a port and the b port of the second reversing valve 16 are communicated, the c port and the d port are communicated; the prime mover 27 provides the hydraulic pump 12 with the prime power, the a port of the hydraulic pump 12 sucks the oil from the oil tank 11, and the high-pressure oil is output from the b port of the hydraulic pump 12 to provide the high pressure for the hydraulic control system; the high-pressure oil output from the b port of the hydraulic pump 12 flows to the a port of the logic valve 28, the a port of the first reversing valve 15 and the control valve group 14 respectively, because the a port and the b port of the first reversing valve 15 are communicated, the hydraulic oil flowing into the first reversing valve 15 flows to the c port of the logic valve 28 through the b port, the a port and the c port of the logic valve 28 are high-pressure oil, the a port and the b port of the logic valve 28 are not communicated, and the impact oil circuit is closed; the control valve group 14 delivers the hydraulic oil to each execution component to provide the high-pressure oil for the action of each execution component, and the pressure oil of the maximum load flows to the b port of the second reversing valve 16 through the load feedback port of the control valve group 14 after comparing the load pressures of each execution component, because the a port and the b port of the second reversing valve 16 are communicated, the hydraulic oil flowing to the second reversing valve 16 flows to the a port of the first shuttle valve 17 and the a port of the third overflow valve 25 through the a port of the second reversing valve 16 respectively, because the b port of the first shuttle valve 17 is communicated with the c port of the first reversing valve 15 through the first damper 22, the c port and the d port of the first reversing valve 15 are communicated, and the d port of the first reversing valve 15 is communicated with the oil tank 11, therefore, the b port pressure of the first shuttle valve 17 is basically zero, at this time, the a port of the first shuttle valve 17 is communicated with the c port, the c port of the first shuttle valve 17 is communicated with the a port of the second shuttle valve 18; the b port of the second shuttle valve 18 is communicated with the b port of the pressure compensation valve 23 through the second damper 24, the b port of the pressure compensation valve 23 is communicated with the rock drilling assembly 13, the rock drilling assembly 13 is communicated with the oil tank 11, the b port of the second shuttle valve 18 is low pressure, the a port and the c port of the second shuttle valve 18 are communicated, and the c port of the second shuttle valve 18 is communicated with the c port of the hydraulic pump 12, that is, the pressure oil of the maximum load in the control valve group 14 is directly fed back to the load port of the hydraulic pump 12, so that the high pressure output by the hydraulic pump 12 changes with the maximum demand pressure of the load. Among them, the third overflow valve 25 provides the maximum safety protection pressure, when the pressure of the maximum load exceeds the set pressure of the third overflow valve 25, the a port and the b port of the third overflow valve 25 are communicated, the b port is communicated with the oil tank 11, so that the hydraulic oil flows back to the oil tank 11, the set pressure of the third overflow valve 25 is greater than the pressure cut-off set pressure of the hydraulic pump 12, so as to protect the whole hydraulic system when the cut-off pressure of the hydraulic pump 12 fails, when the first reversing valve 15 and the second reversing valve 16 are both in the first working position, the hydraulic control system is in the load-sensitive control mode without rock drilling, the output pressure of the hydraulic pump 12 changes with the maximum load pressure demand feedback by the control valve group 14, and is suitable for the working condition with low requirements for action response and action operation delay and high requirements for energy saving.

[0055] Constant pressure control mode when not drilling:

[0056] The first reversing valve 15 is in the first working position, the a port and the b port of the first reversing valve 15 are communicated, the c port and the d port are communicated, the second reversing valve 16 is in the second working position, the b port and the d port of the second reversing valve 16 are communicated, the c port and the a port are communicated; the prime mover 27 provides the prime power for the hydraulic pump 12, the a port of the hydraulic pump 12 sucks the oil from the oil tank 11, the high pressure oil is output from the b port of the hydraulic pump 12 to provide the high pressure for the hydraulic control system; the high pressure oil output from the b port of the hydraulic pump 12 flows to the a port of the logic valve 28, the a port and the b port of the first reversing valve 15 and the control valve group 14, because the a port and the b port of the first reversing valve 15 are communicated, the hydraulic oil flowing into the first reversing valve 15 flows to the c port of the logic valve 28 through the b port, the a port and the c port of the logic valve 28 are high pressure oil, the a port and the b port of the logic valve 28 are not communicated, the impact oil path is closed; the control valve group 14 delivers the hydraulic oil to each execution component to provide the high pressure oil for the action of each execution component, by comparing the load pressure of each execution component, the pressure oil of the maximum load flows to the b port of the second reversing valve 16 through the load feedback port of the control valve group 14, and then flows to the d port of the second reversing valve 16, the d port of the second reversing valve 16 is blocked and does not communicate, so it will not affect other oil paths; the b port of the first reversing valve 15 is communicated with the c port of the first reversing valve 15 through the third damper 26, because the c port and the a port of the second reversing valve 16 are communicated, the a port of the second reversing valve 16 is communicated with the a port of the first shuttle valve 17, because the b port of the first shuttle valve 17 is communicated with the c port of the first reversing valve 15 through the first damper 22, the c port and the d port of the first reversing valve 15 are communicated, the d port of the first reversing valve 15 is communicated with the oil tank 11, therefore, the b port pressure of the first shuttle valve 17 is basically zero, at this time, the a port and the c port of the first shuttle valve 17 are communicated, the c port of the first shuttle valve 17 is communicated with the a port of the second shuttle valve 18; the b port of the second shuttle valve 18 is communicated with the b port of the pressure compensation valve 23 through the second damper 24, the b port of the pressure compensation valve 23 is communicated with the rock drilling assembly 13, the rock drilling assembly 13 is communicated with the oil tank 11, the b port of the second shuttle valve 18 is low pressure, the a port and the c port of the second shuttle valve 18 are communicated, the c port of the second shuttle valve 18 is communicated with the c port of the hydraulic pump 12, that is, the output pressure of the hydraulic pump 12 is directly fed back to the load port of the hydraulic pump 12, so that the output pressure of the hydraulic pump 12 is constant. The third overflow valve 25 provides the maximum safety protection pressure, when the output pressure of the hydraulic pump 12 exceeds the set pressure of the third overflow valve 25, the a port and the b port of the third overflow valve 25 are communicated, the b port is communicated with the oil tank 11, so that the hydraulic oil flows back to the oil tank 11, the set pressure of the third overflow valve 25 is greater than the pressure cut-off set pressure of the hydraulic pump 12, so as to protect the whole hydraulic system when the cut-off pressure of the hydraulic pump 12 fails. That is, when the first reversing valve 15 is in the first working position and the second reversing valve 16 is in the second working position, the hydraulic control system is in the non-rock drilling constant pressure control mode, the output pressure of the hydraulic pump 12 is constant, which is suitable for the working condition with high requirements for action response and action operation delay and low requirements for energy saving.

[0057] Load sensing control mode during rock drilling:

[0058] The first reversing valve 15 is in the second working position, the a port and the c port of the first reversing valve 15 are communicated, the b port and the d port are communicated, the set pressure of the first overflow valve 19 is lower than the rock drilling pressure of the rock drilling assembly 13; the prime mover 27 provides the prime power for the hydraulic pump 12, the a port of the hydraulic pump 12 sucks the oil from the oil tank 11, the high pressure oil is output from the b port of the hydraulic pump 12 to provide the high pressure for the hydraulic control system; the high pressure oil output from the b port of the hydraulic pump 12 flows to the a port of the logic valve 28, the a port and the c port of the first reversing valve 15 and the control valve group 14 respectively, because the b port and the d port of the first reversing valve 15 are communicated, the b port of the first reversing valve 15 and the c port of the logic valve 28 are communicated, the d port of the first reversing valve 15 is communicated with the oil tank 11, therefore, the c port of the logic valve 28 is communicated with the oil tank 11, the pressure is basically zero, the spool of the logic valve 28 is reversed under the condition that the a port is high pressure oil, the a port and the b port of the logic valve 28 are communicated, the impact oil path is communicated; the a port and the c port of the first reversing valve 15 are communicated, the c port of the first reversing valve 15 is communicated with the a port of the first overflow valve 19 and the b port of the first shuttle valve 17 through the first damping 22, the pressure of the oil path depends on the set pressure of the first overflow valve 19, the a port and the b port of the first overflow valve 19 are communicated, the b port is communicated with the oil tank 11; because the logic valve 28 is in the communicated state, the b port of the logic valve 28 is communicated with the a port of the pressure compensation valve 23, the spool of the pressure compensation valve 23 functions as always open, the a port is communicated with the rock drilling assembly 13 to provide the high pressure oil for the impact work of the rock drilling assembly 13; the b port of the pressure compensation valve 23 is communicated with the c port of the pressure compensation valve 23 through the second damping 24, the b port of the pressure compensation valve 23 is also communicated with the a port of the second overflow valve 20 and the proportional overflow valve 21 through the second damping 24, the pressure of the oil path depends on the set pressure of the second overflow valve 20 and the proportional overflow valve 21, wherein the second overflow valve 20 is set to the maximum rock drilling pressure to play a safety protection role, the proportional overflow valve 21 adjusts and controls the rock drilling pressure to set different rock drilling pressures according to the actual working conditions, the b ports of the second overflow valve 20 and the proportional overflow valve 21 are communicated with the oil tank 11, the pressure of the b port of the pressure compensation valve 23 (i.e. the impact port pressure of the rock drill) is determined by the control pressure of the c port and the spring force, the spring force is a fixed value, therefore the rock drilling pressure of the rock drilling assembly 13 is determined by the proportional overflow valve 21; the b port of the pressure compensation valve 23 is also communicated with the b port of the second shuttle valve 18 through the second damping 24.If other components on the drill jumbo except the drilling assembly 13 do not work, the first damping 22 of the c port of the second reversing valve 16 communicates with the b port of the first reversing valve 15, communicates with the oil tank 11 through the d port of the first reversing valve 15, the pressure of the c port of the second reversing valve 16 is basically zero, the b port of the second reversing valve 16 communicates with the load feedback port of the control valve group 14, the load feedback pressure of the control valve group 14 is zero, the b port of the second reversing valve 16 is low pressure, therefore, no matter which working position the second reversing valve 16 is in, the a port of the second reversing valve 16 can only output low pressure oil, so that the a port of the first shuttle valve 17 is low pressure oil, and the b port of the first shuttle valve 17 is high pressure oil, the b port of the first shuttle valve 17 communicates with the c port, the c port of the first shuttle valve 17 communicates with the a port of the second shuttle valve 18, since the set pressure of the first overflow valve 19 is lower than the drilling pressure of the drilling assembly 13, that is, the pressure of the a port of the second shuttle valve 18 is less than the pressure of the b port, the b port of the second shuttle valve 18 communicates with the c port, the c port of the second shuttle valve 18 communicates with the c port of the hydraulic pump 12, at this time, the high pressure oil output by the b port of the hydraulic pump 12 is determined by the set pressure of the proportional overflow valve 21, and the drilling pressure of the drilling assembly 13 is also determined by the set pressure of the proportional overflow valve 21, that is, the output pressure of the hydraulic pump 12 is the same as the drilling pressure demand of the drilling assembly 13, and the hydraulic control system is in the load sensitive control mode when drilling; if other components on the drill jumbo except the drilling assembly 13 work, and the second reversing valve 16 is in the second working position, the output pressure of the hydraulic pump 12 is the same as the drilling pressure demand of the drilling assembly 13; if other components on the drill jumbo except the drilling assembly 13 work, and the second reversing valve 16 is in the first working position, as can be seen from the above process analysis, the output pressure of the hydraulic pump 12 depends on the maximum pressure between the maximum load pressure feedback by the control valve group 14 and the set pressure of the proportional overflow valve 21, that is, the output pressure of the hydraulic pump 12 is not lower than the set pressure of the proportional overflow valve 21, and the drilling pressure of the drilling assembly 13 is not affected by the load pressure of the control valve group 14, and even if the output pressure of the hydraulic pump 12 is higher than the drilling pressure, the drilling assembly 13 can also be effectively protected.

[0059] Constant pressure control mode when drilling:

[0060] The first reversing valve 15 is in the second working position, the a port and the c port of the first reversing valve 15 are communicated, the b port and the d port are communicated, the set pressure of the first overflow valve 19 is higher than that of the second overflow valve 20; the prime mover 27 provides the prime power for the hydraulic pump 12, the a port of the hydraulic pump 12 sucks the oil from the oil tank 11, the high pressure oil is output from the b port of the hydraulic pump 12 to provide the high pressure for the hydraulic control system; the high pressure oil output from the b port of the hydraulic pump 12 flows to the a port of the logic valve 28, the a port and the c port of the first reversing valve 15 and the control valve group 14 respectively, because the b port and the d port of the first reversing valve 15 are communicated, the b port of the first reversing valve 15 and the c port of the logic valve 28 are communicated, the d port of the first reversing valve 15 is communicated with the oil tank 11, therefore, the c port of the logic valve 28 is communicated with the oil tank 11 and the pressure is basically zero, the a port and the b port of the logic valve 28 are communicated under the condition that the a port is high pressure oil, the impact oil circuit is communicated; the a port and the c port of the first reversing valve 15 are communicated, the c port of the first reversing valve 15 is communicated with the a port of the first overflow valve 19 and the b port of the first shuttle valve 17 through the first damper 22, the pressure of the oil circuit depends on the set pressure of the first overflow valve 19, the a port and the b port of the first overflow valve 19 are communicated, the b port is communicated with the oil tank 11; because the logic valve 28 is in the communicated state, the b port of the logic valve 28 is communicated with the a port of the pressure compensation valve 23, the valve core of the pressure compensation valve 23 is always open, the a port is communicated with the rock drilling assembly 13 to provide the high pressure oil for the impact work of the rock drilling assembly 13; the b port of the pressure compensation valve 23 is communicated with the c port of the pressure compensation valve 23 through the second damper 24, the b port of the pressure compensation valve 23 is also communicated with the a port of the second overflow valve 20 and the proportional overflow valve 21 through the second damper 24, the pressure of the oil circuit depends on the set pressure of the second overflow valve 20 and the proportional overflow valve 21, wherein the second overflow valve 20 is set to the maximum rock drilling pressure to play a safety protection role, the proportional overflow valve 21 adjusts and controls the rock drilling pressure to set different rock drilling pressures according to the actual working conditions, the b ports of the second overflow valve 20 and the proportional overflow valve 21 are communicated with the oil tank 11, the pressure of the b port of the pressure compensation valve 23 (i.e. the impact port pressure of the rock drill) is determined by the control pressure of the c port and the spring force, the spring force is a fixed value, therefore the rock drilling pressure of the rock drilling assembly 13 is determined by the proportional overflow valve 21; the b port of the pressure compensation valve 23 is also communicated with the b port of the second shuttle valve 18 through the second damper 24.If other components on the drill jumbo except the drilling assembly 13 do not work, the first damping 22 of the c port of the second reversing valve 16 communicates with the b port of the first reversing valve 15, and communicates with the oil tank 11 through the d port of the first reversing valve 15, the pressure of the c port of the second reversing valve 16 is basically zero, the b port of the second reversing valve 16 communicates with the load feedback port of the control valve group 14, the load feedback pressure of the control valve group 14 is zero, the b port of the second reversing valve 16 is low pressure, therefore, no matter which working position the second reversing valve 16 is in, the a port of the second reversing valve 16 can only output low pressure oil, so that the a port of the first shuttle valve 17 is low pressure oil, and the b port of the first shuttle valve 17 is high pressure oil, the b port of the first shuttle valve 17 communicates with the c port, the c port of the first shuttle valve 17 communicates with the a port of the second shuttle valve 18, because the set pressure of the first overflow valve 19 is higher than that of the second overflow valve 20, the pressure of the a port of the second shuttle valve 18 is greater than that of the b port, the a port of the second shuttle valve 18 communicates with the c port, and the c port of the second shuttle valve 18 communicates with the c port of the hydraulic pump 12, at this time, the output pressure of the hydraulic pump 12 depends on the set pressure of the first overflow valve 19, the drilling pressure of the drilling assembly 13 depends on the second overflow valve 20 and the proportional overflow valve 21, the output pressure of the hydraulic pump 12 is a constant value, and the hydraulic control system is in a constant pressure control mode when drilling.

[0061] The rock drilling jumbo of the embodiment comprises the hydraulic control system described above. Specifically, by adopting the hydraulic control system described above in the rock drilling jumbo, the hydraulic control system seamlessly switches between the constant pressure control mode and the load-sensitive control mode when the rock drilling jumbo is not drilling, so that different control modes can be selected according to different working condition requirements. If the hydraulic control system needs to respond quickly and the handle operation arm action has low delay, the constant pressure control mode is selected. If the output pressure and flow of the hydraulic pump 12 need to change with the actual load, the load-sensitive control mode is selected. When the modes are switched, no additional changes need to be made to the hydraulic control system, and the versatility is high. The rock drilling impact uses valve control drilling, and the outlet pressure of the hydraulic pump 12 is controlled separately when drilling and when not drilling. The outlet pressure of the hydraulic pump 12 can be independently set according to the working condition requirements. Even if the load-sensitive control mode is used, the rock drilling assembly 13 can be effectively protected and is not affected by the pressure of other loads. When drilling, the rock drilling pressure constant pressure control and the load-sensitive control of the control valve group 14 can exist at the same time and do not affect each other. When the output pressure of the hydraulic pump 12 is affected by the rock drilling pressure and not affected by the rock drilling pressure, the output pressure of the hydraulic pump 12 is also controlled separately, the pressure is independently set, and they do not affect each other. For the working condition in which the feedback pressure of the control valve group 14 needs to be higher than the rock drilling pressure when drilling (such as the rock drilling assembly 13 needs to be externally connected to high-pressure buffer oil, or other actions need to be operated when drilling), the set pressure of the first overflow valve 19 is greater than the rock drilling pressure, so that the output pressure of the hydraulic pump 12 is increased to meet the working condition requirements. The output pressure of the hydraulic pump 12 is the set pressure of the first overflow valve 19, and the rock drilling pressure is constant pressure control when drilling. For the working condition in which the feedback pressure of the control valve group 14 does not need to be higher than the rock drilling pressure when drilling (such as the rock drilling assembly 13 does not need to be externally connected to high-pressure buffer oil or other actions do not need to be operated during drilling), the set pressure of the first overflow valve 19 is reduced to be lower than the rock drilling pressure or the minimum pressure is set, so that the rock drilling pressure load is fed back to the hydraulic pump 12. The output pressure of the hydraulic pump 12 changes with the change of the rock drilling pressure, and the rock drilling pressure of the rock drilling assembly 13 is load-sensitive control when drilling, so that the energy consumption is reduced during the entire rock drilling process and the energy saving is improved.

[0062] The above only describes the preferred embodiments of the present application and is not intended to limit the present application. Those skilled in the art can make various changes and modifications to the present application. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principles of the present application shall be included in the protection scope of the present application.

Claims

1. A hydraulic control system, characterized in that, The system includes an oil tank (11), a hydraulic pump (12), a rock drilling assembly (13), a control valve group (14), a first directional valve (15), a second directional valve (16), a logic valve (28), a pressure compensation valve (23), and a feedback valve group. The feedback valve group includes a first shuttle valve (17), a second shuttle valve (18), a first relief valve (19), a second relief valve (20), and a proportional relief valve (21). The first directional valve (15) and the second directional valve (16) are both two-position four-way solenoid valves. Both of the two two-position four-way solenoid valves include port a, port b, port c, and port d. Under normal conditions, port a is connected to port b, and port d is connected to port c. When the electromagnet is energized, port a is connected to port c, and port d is connected to port b.One inlet of the first shuttle valve (17) is connected to port c of the first directional valve (15), and the other inlet of the first shuttle valve (17) is connected to port a of the second directional valve (16). One inlet of the second shuttle valve (18) is connected to the outlet of the first shuttle valve (17), and the other inlet of the second shuttle valve (18) is connected to the outlet of the pressure compensation valve (23). The outlet of the second shuttle valve (18) is connected to the load port of the hydraulic pump (12). The inlet of the first relief valve (19) is connected to port c of the first directional valve (15), and the outlet of the first relief valve (19) is connected to the oil tank (11) and used to control the maximum output from the first directional valve (15) to the first shuttle valve (17). The oil pressure is controlled by the following: the inlet of the second relief valve (20) is connected to the outlet of the pressure compensation valve (23), the outlet of the second relief valve (20) is connected to the oil tank (11) and used to control the maximum drilling pressure of the rock drilling assembly (13); the inlet of the proportional relief valve (21) is connected to the outlet of the pressure compensation valve (23), the outlet of the proportional relief valve (21) is connected to the oil tank (11) and used to control the drilling pressure of the rock drilling assembly (13); the outlet of the oil tank (11) is connected to the hydraulic pump (12), the outlet of the hydraulic pump (12) is connected to the control valve group (14), the oil port a of the first directional valve (15), and the inlet of the logic valve (28); and the rock drilling assembly (13) is connected to the oil tank (11). The oil port b of the first directional valve (15) is connected to the hydraulic control port on one side of the logic valve (28) and the oil port c of the second directional valve (16). The oil port d of the first directional valve (15) is connected to the oil tank (11). The oil outlet of the logic valve (28) is connected to the oil inlet of the pressure compensation valve (23) and the hydraulic control port on the other side of the logic valve. The oil inlet of the logic valve (28) is connected to the hydraulic control port on the other side of the logic valve. The oil outlet of the pressure compensation valve (23) is connected to the rock drilling assembly (13) and the control valve port of the pressure compensation valve (23) and is used to control the rock drilling pressure change of the rock drilling assembly (13). The load feedback port of the control valve group (14) is connected to the oil port b of the second directional valve (16). The maximum load pressure oil of the actuators in the rock drilling rig (excluding the rock drilling mechanism) is connected and used for feedback. The oil port d of the second directional valve (16) is blocked. The first directional valve (15) is used to cooperate with the logic valve (28) to control the opening and closing of the rock drilling assembly (13). The second directional valve (16) is used to control the on / off of the load feedback of the control valve group (14). The feedback valve group is used to cooperate with the first directional valve (15), the second directional valve (16) and the pressure compensation valve (23) to control the hydraulic oil delivered to the load port of the hydraulic pump (12), thereby realizing the switching between the constant pressure control mode and the load-sensitive control mode of the hydraulic control system during rock drilling and non-rock drilling, and avoiding the rock drilling pressure from being affected by the load pressure.

2. The hydraulic control system according to claim 1, characterized in that, A first damper (22) is provided between the oil port c of the first directional valve (15) and one oil inlet of the first shuttle valve (17).

3. The hydraulic control system according to claim 1, characterized in that, A second damper (24) is provided between the oil outlet of the pressure compensation valve (23) and the other oil inlet of the second shuttle valve (18), and the oil outlet of the second damper (24) is connected to the control valve port of the pressure compensation valve (23).

4. The hydraulic control system according to any one of claims 1-3, characterized in that, A third relief valve (25) is provided between the oil port a of the second reversing valve (16) and the oil tank (11).

5. The hydraulic control system according to any one of claims 1-3, characterized in that, A third damper (26) is provided between the oil port b of the first reversing valve (15) and the oil port c of the second reversing valve (16).

6. The hydraulic control system according to any one of claims 1-3, characterized in that, The hydraulic control system also includes a prime mover (27) connected to the hydraulic pump (12).

7. A rock drilling rig, characterized in that, The hydraulic control system includes any one of claims 1-6.

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