WO2020119668A1 - 凿岩台车的冲击控制液压系统 - Google Patents

凿岩台车的冲击控制液压系统 Download PDF

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Publication number
WO2020119668A1
WO2020119668A1 PCT/CN2019/124223 CN2019124223W WO2020119668A1 WO 2020119668 A1 WO2020119668 A1 WO 2020119668A1 CN 2019124223 W CN2019124223 W CN 2019124223W WO 2020119668 A1 WO2020119668 A1 WO 2020119668A1
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Prior art keywords
valve
hydraulic
control
directional valve
oil
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PCT/CN2019/124223
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English (en)
French (fr)
Inventor
刘飞香
程永亮
郑大桥
刘伟
张廷寿
胡树伟
胡骞
柏泽楠
李晓星
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中国铁建重工集团股份有限公司
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Publication of WO2020119668A1 publication Critical patent/WO2020119668A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors

Definitions

  • the invention relates to the field of rock drilling equipment, in particular to an impact control hydraulic system of a rock drilling trolley.
  • the present invention also relates to a rock drilling vehicle including the above-mentioned impact control hydraulic system.
  • the hydraulic rock drilling trolley is an important hard rock drilling equipment for tunnel construction by drilling and blasting. It has the advantages of fast rock drilling speed, high power, high construction efficiency and easy automation. It is widely used in the rock drilling trolley market.
  • the hydraulic rock drilling rig is a rotary impact drilling rock drilling rig. During rock drilling, the impact energy requirements are different in different rock drilling stages. Generally, the impact pressure requirements are lower in the drilling stage, and the impact in the rock drilling stage The pressure is higher and the energy demand is greater. Rocks with different characteristics require that the impact energy of the rock drilling trolley is also very different.
  • the existing rock drilling vehicle impact hydraulic system does not have high-pressure and low-pressure pressure segmented control, which is not conducive to the control of hole drilling and increases the loss of the rock drilling machine.
  • a multi-way directional valve is used to directly perform impact control. Large-flow high-pressure impact oil directly enters the rock drill through the multi-way directional valve, which generates a large pressure loss on the multi-way directional valve and reduces the system efficiency; The multi-way valve directional valve always withstands high-pressure impact, which has a greater impact on the reliability of the system.
  • the existing impact hydraulic power source cannot automatically adapt to adjust the system pressure according to the impact conditions.
  • the hydraulic pump maintains a high working pressure to meet the requirements of two different conditions of high-pressure impact and low-pressure impact.
  • the system generates heat and affects the efficiency of the hydraulic control system.
  • the object of the present invention is to provide a shock control hydraulic system for rock drilling trolleys, a multi-way directional valve to control the high-stroke and low-stroke pilot control oil circuits, and a large flow of high-pressure shock oil directly controlled by the hydraulic control logic valve's breaking control Entering the rock drilling machine, avoiding the pressure loss generated by the valve control and improving the system efficiency; using the small flow multi-way directional valve as a pilot to achieve impact control, reducing the system cost, avoiding the high-pressure impact of the multi-way directional valve, and improving the System reliability.
  • Another object of the present invention is to provide a rock drilling trolley including the above-mentioned impact control hydraulic system.
  • the present invention provides an impact control hydraulic system of a rock drilling trolley, which includes a hydraulic pump, a rock drilling machine and a multi-way directional valve.
  • the two working ports of the multi-way directional valve communicate with the first The hydraulic control oil port of the hydraulic control directional valve and the hydraulic control oil port of the second hydraulic control directional valve, the output port of the hydraulic pump communicates with the rock drill through a hydraulic control logic valve, and the output port of the hydraulic pump passes through the first liquid
  • the directional control valve communicates with the first overflow valve, the output port of the hydraulic pump communicates with the second overflow valve through the second hydraulic control directional valve, and further includes a shuttle valve, and the two oil inlets of the shuttle valve communicate with each other The oil inlet of the first overflow valve and the oil inlet of the second overflow valve, the oil outlet of the shuttle valve communicates with the liquid control oil port of the hydraulic control logic valve, and the first overflow
  • the set pressure of the valve is less than the set pressure of the second relief valve;
  • both the first hydraulic control directional valve and the second hydraulic control directional valve are closed, the hydraulic control logic valve is closed, and the rock drilling machine stops working;
  • the first hydraulic control directional valve opens, the second hydraulic control directional valve closes, and hydraulic oil enters the fluid of the hydraulic control logic valve via the shuttle valve An oil control port, the hydraulic control logic valve is opened, and the rock drill is in an opening mode;
  • the second hydraulic control directional valve opens, the first hydraulic control directional valve closes, and hydraulic oil enters the fluid of the hydraulic control logic valve via the shuttle valve
  • the oil control port, the hydraulic logic valve is opened, and the rock drill is in rock drilling mode.
  • the multi-way directional valve is specifically a manual three-position six-way directional valve.
  • the hydraulic pump and the first hydraulic control are isolated The hydraulic control port of the directional valve and the hydraulic control port of the second hydraulic control directional valve; when the manual three-position six-way directional valve is in the second working position, hydraulic oil can enter the first hydraulic control directional valve Hydraulic control oil port; when the manual three-position six-way directional valve is in the third working position, hydraulic oil can enter the hydraulic control oil port of the second hydraulic control directional valve.
  • a safety check valve and a safety relief valve are provided between the manual three-position six-way directional valve and the hydraulic pump.
  • a pressure relief valve is provided between the hydraulic pump and the hydraulic logic valve.
  • a first damper is provided between the hydraulic pump, the first hydraulic directional valve and the second hydraulic directional valve; the first hydraulic directional valve and the first overflow valve
  • a fourth damper is provided between the second hydraulic control directional valve and a second relief valve.
  • the first hydraulic control directional valve and the second hydraulic control directional valve are specifically two-position three-way hydraulic control directional valves.
  • control chamber of the hydraulic pump further communicates with an electromagnetic ball valve, a third relief valve and a fourth relief valve arranged in parallel, the preset pressure of the third relief valve is greater than the preset pressure of the fourth relief valve ,
  • a hydraulic two-way directional valve is provided between the third overflow valve and the fourth overflow valve, and the hydraulic port of the hydraulic two-way directional valve communicates with the oil outlet of the shuttle valve.
  • the opening pressure of the hydraulically controlled two-way directional valve is between the preset pressure of the first relief valve and the preset pressure of the second relief valve;
  • the hydraulic pump control chamber can communicate with the oil tank through the electromagnetic ball valve
  • the multi-way directional valve When the multi-way directional valve is in the first working position, the hydraulic two-way directional valve is in the first working position, and the hydraulic pump communicates with the oil tank through the fourth relief valve; the multi-way directional valve When in the second working position, the hydraulic two-way directional valve is in the first working position, and the hydraulic pump communicates with the oil tank through the fourth overflow valve;
  • the hydraulic two-way directional valve When the multiple directional valve is in the third working position, the hydraulic two-way directional valve is in the second working position, and the hydraulic pump communicates with the oil tank through the third overflow valve.
  • the present invention provides a rock drilling trolley including an impact control hydraulic system.
  • the impact control hydraulic system is specifically any of the above-mentioned impact control hydraulic systems.
  • the invention provides an impact control hydraulic system of a rock drilling trolley, which includes a hydraulic pump, a rock drilling machine and a multi-way directional valve.
  • the two working oil ports of the multi-way directional valve are respectively connected to the liquid control oil ports of the first hydraulic control directional valve It is connected with the hydraulic control port of the second hydraulic control directional valve.
  • the output port of the hydraulic pump is connected to the rock drill through the hydraulic control logic valve.
  • the output port of the hydraulic pump is connected to the first overflow valve through the first hydraulic control directional valve.
  • the output port of the hydraulic pump is The second hydraulically controlled directional valve communicates with the second overflow valve, and further includes a shuttle valve.
  • the two oil inlets of the shuttle valve respectively communicate with the oil inlet of the first overflow valve and the oil inlet of the second overflow valve.
  • the shuttle valve The oil outlet is connected to the hydraulic control port of the hydraulic control logic valve.
  • the set pressure of the first relief valve is less than the set pressure of the second relief valve; when the multi-way directional valve is in the first working position, the first hydraulic control The directional valve and the second hydraulic control directional valve are closed, the hydraulic control logic valve is closed, and the rock drill stops working; when the multi-way directional valve is in the second working position, the first hydraulic control directional valve is opened, and the second hydraulic control directional valve is closed,
  • the hydraulic oil enters the hydraulic control oil port of the hydraulic control logic valve via the shuttle valve, the hydraulic control logic valve opens, and the rock drill is in the opening mode; when the multi-way directional valve is in the third working position, the second hydraulic control directional valve opens, and the first fluid
  • the directional control valve is closed, hydraulic oil enters the hydraulic control oil port of the hydraulic control
  • the system has two working modes of high impact and low impact to meet different working requirements.
  • the multi-way directional valve has a positioning function. It can be locked in three different positions. The upper position is the standby position and the impact does not work; the middle position is the opening control and the low impact pressure; the lower position is the rock drilling control and the high impact pressure; from standby to Opening holes, then rock drilling, the handles are operated in sequence, and the control is smooth.
  • High-pressure impact oil is connected in parallel with the oil inlet of the multi-way directional valve.
  • the multi-way directional valve is used as the impact pilot control.
  • the high and low rush pressures are set separately by the overflow valve.
  • the multi-way directional valve controls the hydraulic control directional valve. Connect the impact pilot control oil to enable the impact function.
  • the high-pressure impact oil is directly connected to the rock drill through the hydraulic control logic valve without passing through the multi-way directional valve.
  • High impact and low impact correspond to different impact control pilot pressures.
  • the pilot pressure is fed back to the hydraulic two-way directional valve.
  • Different relief valves are selected through the hydraulic two-way directional valve control.
  • the set pressure of the relief valve is controlled to be constant. Pressure variable pump outlet pressure, and then realize the adaptive control of hydraulic pump pressure and high impact and low impact control.
  • the multi-way reversing valve controls the high-stroke and low-stroke pilot control oil lines.
  • the high-flow high-pressure impact oil directly enters the rock drill through the valve's on-off control, which avoids the valve control from generating large pressure losses and improves the system efficiency.
  • the flow multi-way valve is used as a pilot to achieve impact control, which reduces system cost, avoids high-pressure impact of the multi-way directional valve, and improves system reliability.
  • the service life of the rock drill is improved; the pressure of the hydraulic pump is adjusted adaptively according to the impact control mode, which reduces the pressure loss and heat generation, and improves the reliability of the system.
  • the invention also provides a rock drilling trolley including the above impact control hydraulic system. Since the above impact control hydraulic system has the above technical effects, the above rock drilling trolley should also have the same technical effects, which will not be described in detail here.
  • FIG. 1 is a hydraulic principle diagram of an embodiment of an impact control hydraulic system provided by the present invention.
  • the core of the present invention is to provide an impact control hydraulic system for a rock drilling trolley, a multi-way reversing valve to control the high-stroke and low-stroke pilot control oil passages, and a large-flow high-pressure impact oil is directly controlled by the opening and closing control of the hydraulic control logic valve Entering the rock drilling machine, avoiding the pressure loss caused by the valve control and improving the efficiency of the system; adopting the small flow multi-way directional valve as a pilot to achieve impact control, reducing the system cost, avoiding the high-pressure impact of the multi-way directional valve, and improving the System reliability.
  • Another core of the present invention is to provide a rock drilling trolley including the above-mentioned impact control hydraulic system.
  • FIG. 1 is a hydraulic schematic diagram of a specific embodiment of an impact control hydraulic system provided by the present invention.
  • a specific embodiment of the present invention provides an impact control hydraulic system for a rock drilling trolley, including a hydraulic pump 2, a rock drill 22 and a multi-way directional valve 3, wherein the hydraulic pump 2 is driven by a motor 1 and the inlet of the multi-way directional valve 3 is
  • the oil port P is connected to the output port of the hydraulic pump 2
  • the oil return port T of the multi-way valve 3 is connected to the oil tank
  • the other oil inlet port P 1 of the multi-way valve 3 is connected to the output port of the hydraulic pump 2
  • One working oil port A of the check valve 3 communicates with the hydraulic control oil port of the first hydraulic control directional valve 14, and the other working oil port B of the multi-way valve 3 communicates with the hydraulic control oil port of the second hydraulic control directional valve 13.
  • a safety check valve 5 and a safety relief valve 4 can also be provided between the multi-way valve 3 and the hydraulic pump 2
  • the output port of the hydraulic pump 2 communicates with the rock drill 22 through the hydraulic control logic valve 12, the oil inlet P of the first hydraulic control directional valve 14 communicates with the output port of the hydraulic pump 2, the oil outlet T of the first hydraulic control directional valve 14
  • the oil tank is communicated with the working oil port A of the first hydraulic directional valve 14 communicating with the oil inlet of the first relief valve 20.
  • the oil inlet P of the second hydraulic directional valve 13 communicates with the output port of the hydraulic pump 2, the oil outlet T of the second hydraulic directional valve 13 communicates with the oil tank, and the working oil port A of the second hydraulic directional valve 13 communicates with the second The oil inlet of the relief valve 21.
  • the two oil inlets of the shuttle valve 19 are respectively connected to the oil inlet of the first relief valve 20 and the oil inlet of the second relief valve 21, and the oil outlet of the shuttle valve 19 is connected to the fluid control oil port of the hydraulic control logic valve 12
  • the set pressure of the first relief valve 20 is less than the set pressure of the second relief valve 21.
  • the multi-way directional valve 3 may be a manual three-position six-way directional valve.
  • the oil inlet P of the multi-way directional valve 3 isolates the first work
  • the oil port A and the second working oil port B isolate the hydraulic control oil port of the hydraulic pump 2 and the first hydraulic control directional valve 14 and the hydraulic control oil port of the second hydraulic control directional valve 13.
  • the oil inlet P of the multi-way directional valve 3 only communicates with the first working oil port A, and hydraulic oil can enter the hydraulic control port of the first hydraulic directional valve 14 ;
  • the oil inlet P of the multi-way directional valve 3 only communicates with the second working oil port B, and the hydraulic oil can enter the hydraulic control oil of the second hydraulic control valve 13 mouth.
  • the first hydraulically controlled directional valve 14 and the second hydraulically controlled directional valve 13 are specifically two-position three-way hydraulically-controlled directional valves. The type of valve, the number of channels and the number of working bits can be adjusted according to the situation, which are all within the scope of protection of the present invention. Inside.
  • a pressure relief valve 11 is provided between the hydraulic pump 2 and the hydraulic control logic valve 12.
  • a first damper 10 is provided between the hydraulic pump 2 and the first hydraulic directional valve 14 and the second hydraulic directional valve 13; a fourth is provided between the first hydraulic directional valve 14 and the first relief valve 20
  • the damper 17 is provided with a fifth damper 18 between the second hydraulically controlled directional valve 13 and the second relief valve 21.
  • the pipeline between the multi-way directional valve 3 and the first hydraulic directional valve 14 is connected to the oil tank through the third damper 16, and between the multi-way directional valve 3 and the second hydraulic directional valve 13 is The oil tank is connected to the pipeline through the second damper 15
  • the control chamber of the hydraulic pump 2 is also connected to the electromagnetic ball valve 7, the third relief valve 8 and the fourth relief valve 9 and the third relief valve 8 provided in parallel
  • the preset pressure is greater than the preset pressure of the fourth relief valve 9
  • a hydraulic two-way directional valve 6 is provided between the third relief valve 8 and the fourth relief valve 9, the liquid of the hydraulic two-way directional valve 6
  • the oil control port communicates with the oil outlet of the shuttle valve 19, and the opening pressure of the hydraulic two-way directional valve 6 is between the preset pressure of the first relief valve 20 and the preset pressure of the second relief valve 21;
  • the control chamber of the hydraulic pump 2 can communicate with the oil tank through the electromagnetic ball valve 7; when the system is started, the electromagnetic ball valve 7 is in the second working position, and the control chamber of the hydraulic pump 2 can pass the second overflow
  • the flow valve 8 or the third overflow valve 9 communicates with the oil tank; when the multi-way directional valve 3 is in the first working position, the hydraulically controlled two-way directional valve 6 is in the first working position, and the control chamber of the hydraulic pump 2 passes through the fourth overflow valve 9 communicates with the oil tank; when the multi-way directional valve 3 is in the second working position, the hydraulically controlled two-way directional valve 6 is in the first working position, and the control chamber of the hydraulic pump 2 communicates with the oil tank through the fourth overflow valve 9; the multi-way directional valve When the 3 is in the third working position, the hydraulic two-way directional valve 6 is in the second working position, and the control chamber of the hydraulic pump 2 communicates with the oil tank through the
  • the specific working mode is: in the initial state, the electromagnetic ball valve 7 is not powered, the control chamber of the hydraulic pump 2 can communicate with the oil tank through the electromagnetic ball valve 7, the operating handle of the multi-way directional valve 3 is positioned in the first working position, and the control oil of the hydraulic pump 2 X is in the unloading state, the set value of the constant pressure is low, the motor 1 is started, the hydraulic pump 2 is unloaded and started, and the pump outlet pressure is maintained at a low constant pressure value.
  • the electromagnetic ball valve 7 is powered on, and the pressure at the control oil X of the hydraulic pump 2 is set by the fourth relief valve 9, that is, the hydraulic pump 2 communicates with the oil tank through the fourth relief valve 9, and the outlet pressure of the hydraulic pump 2 reaches a low pressure Pressure setting value, but the hydraulic control logic valve 12 is closed at this time, no shock action.
  • the handle controls the multi-way valve 3 to switch to the second working position for hole control, P-way A of the multi-way valve 3, the first hydraulic control valve 14 changes direction, the high-pressure oil at the outlet of the hydraulic pump 2 is damped 10 to the P port of the first hydraulic directional valve 14, P through A of the first hydraulic directional valve 14, high-pressure oil overflows through the damper 17 and the relief valve 20, and the pilot pressure of the outlet of the shuttle valve 19 is the first
  • the set pressure of the relief valve 20 the hydraulic control logic valve 12 is opened, the high-pressure oil at the outlet of the hydraulic pump 2 enters the rock drill 22 through the pressure reducing valve 11 and the hydraulic control logic valve 12, and operates at a low impact pressure.
  • the pilot pressure of 11 is related.
  • the spring set pressure of the hydraulic two-way directional valve 6 intervenes between the relief valve 20 and the relief valve 21. At this time, the pilot pressure of the outlet of the shuttle valve 19 cannot make it switch.
  • the pressure at the control chamber X of the hydraulic pump 2 is controlled by the The setting of the four relief valve 9 means that the control chamber of the hydraulic pump 2 communicates with the oil tank through the fourth relief valve 9, and the outlet pressure of the hydraulic pump 2 continues to work with the set value corresponding to the low impact pressure.
  • the handle controls the multi-way directional valve 3 to the third working position for rock drilling control, the P-way B of the multi-way directional valve 3, the second hydraulic control directional valve 13 directional, P-way A; multi-directional directional
  • the valve 3A port communicates with the oil tank through the damping 16, the first hydraulic directional valve 14 does not change direction, A through T.
  • the high-pressure oil at the outlet of the hydraulic pump 2 passes through the damping 10 to the P port of the second hydraulic control directional valve 13, and the P of the second hydraulic control directional valve 13 passes through A.
  • the high-pressure oil overflows through the damping 18 and the second relief valve 21 at this time
  • the pilot pressure at the outlet of the shuttle valve 19 is the set pressure of the relief valve 21
  • the hydraulic control logic valve 12 is opened, and the high-pressure oil at the outlet of the hydraulic pump 2 enters the rock drill 22 through the pressure relief valve 11 and the hydraulic control logic valve 12 and works at a high impact pressure
  • the low pressure is related to the pilot control pressure of the pressure reducing valve 11.
  • the spring set pressure of the hydraulic two-way directional valve 6 intervenes between the relief valve 20 and the relief valve 21, at this time the pilot pressure of the outlet of the shuttle valve 19 changes its direction, and the pressure at the control chamber X of the hydraulic pump 2 is controlled by the third
  • the relief valve 8 is set, the control chamber of the hydraulic pump 2 communicates with the oil tank through the third relief valve 8, and the outlet pressure of the hydraulic pump 2 works at the set value corresponding to the high impact pressure.
  • the handle controls the multi-directional directional valve 3 to switch to the first working position, the A and B of the multi-directional valve 3 pass through the T return tank, the second hydraulic directional valve 13 and the first hydraulic directional valve 14 do not switch, so The output pilot pressure of the shuttle valve 19 is zero, the hydraulic control logic valve 12 is closed, and the impact does not work.
  • the rock drill 22 operates at a low impact pressure, the impact pressure is set by the first relief valve 20, and the outlet pressure of the hydraulic pump 2 is set by the fourth relief valve 9.
  • the rock drill 22 works at a high impact pressure, the impact pressure is set by the second relief valve 21, the hydraulic pump outlet pressure is set by the third relief valve 8, the rock drill 22 impact control pump outlet pressure at different working stages Adaptive adjustment.
  • the system has two working modes of high impact and low impact to meet different working requirements.
  • the multi-way directional valve 3 has a positioning function. It can be locked in three different positions. The upper position is the standby position and the impact is not working; the middle position is the opening control and the low impact pressure; the lower position is the rock drilling control and the high impact pressure; from standby To the hole, then to the rock, the handle control sequence operation, smooth control.
  • High-pressure impact oil is connected in parallel with the oil inlet of the multi-way directional valve 3.
  • the multi-way directional valve 3 is used as the impact pilot control.
  • the high and low rush pressures are set by the overflow valve respectively.
  • the multi-way directional valve 3 controls the hydraulic control.
  • the directional valve changes direction, connects the impact pilot control oil, and enables the impact function.
  • the high-pressure impact oil does not pass through the multi-way directional valve and is directly connected to the rock drill 22 through the hydraulic control logic valve 12.
  • High impact and low impact correspond to different impact control pilot pressures.
  • the pilot pressure is fed back to the hydraulic two-way directional valve 6.
  • Different relief valves are selected through the hydraulic two-way directional valve 6.
  • the set pressure of the relief valve Control the outlet pressure of the constant pressure variable pump, and then realize the adaptive control of the hydraulic pump 2 pressure and high impact and low impact control.
  • the multi-way reversing valve 3 controls the high-stroke and low-stroke pilot control oil lines.
  • the high-flow high-pressure impact oil directly enters the rock drill 22 through the valve's on-off control, which avoids the valve control from generating large pressure losses and improves the system efficiency;
  • the small flow multi-way valve is used as a pilot to realize the impact control, which reduces the system cost, avoids the high-pressure impact of the multi-way directional valve, and improves the system reliability.
  • the service life of the rock drill 22 is improved; the pressure of the hydraulic pump 2 is adaptively adjusted according to the impact control mode, reducing pressure loss, reducing heat generation, and improving the reliability of the system.
  • a specific embodiment of the present invention also provides a rock drilling trolley including the above-mentioned impact control hydraulic system.
  • a rock drilling trolley including the above-mentioned impact control hydraulic system.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Earth Drilling (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

一种凿岩台车的冲击控制液压系统，包括液压泵(2)、凿岩机(22)和多路换向阀(3)，多路换向阀(3)的两个工作油口分别连通第一液控方向阀(14)的液控油口和第二液控方向阀(13)的液控油口，液压泵(2)的输出口通过液控逻辑阀(12)连通凿岩机(22)，还包括梭阀(19)，梭阀(19)的两个进油口分别连通第一溢流阀(20)的进油口和第二溢流阀(21)的进油口，梭阀(19)的出油口连通液控逻辑阀(12)的液控油口。多路换向阀控制高冲和低冲的先导控制油路，大流量高压冲击油通过阀的开断控制直接进入凿岩机，避免了阀控产生较大的压力损失，提高了系统效率；采用小流量多路阀作为先导实现冲击控制，降低了系统成本，提高了系统可靠性，提高了凿岩台车的使用寿命。还公开一种包括上述冲击控制液压系统的凿岩台车。

Description

凿岩台车的冲击控制液压系统 技术领域
本发明涉及凿岩设备领域，特别是涉及一种凿岩台车的冲击控制液压系统。此外，本发明还涉及一种包括上述冲击控制液压系统的凿岩台车。
背景技术
液压凿岩台车是钻爆法隧道施工的重要硬岩钻孔设备，具有凿岩速度快、功率大、施工效率高及易实现自动化等优点，广泛应用于凿岩台车市场。液压凿岩台车是一种旋转冲击式钻孔凿岩台车，在进行凿岩作业时，不同凿岩阶段冲击能要求不一样，一般在开孔阶段冲击压力要求较低，凿岩阶段冲击压力较高，能量需求大。不同特性的岩石要求凿岩台车的冲击能也有着很大的不同，如果冲击能对所凿岩石来说过大的话，会在钎杆和钎头中形成过大的应力，而且岩石破碎后不可能全部吸收能量，部分能量会反射回凿岩机能，既浪费能量还会可能造成系统的损坏。因此需要对凿岩机冲击进行高冲压力和低冲压力控制。另一方面，由于液压凿岩机冲击压力高、流量大，系统能耗大，提高冲击液压控制效率显得尤为重要。
但是现有的凿岩台车冲击液压系统没有高冲压力和低冲压力分段控制，不利于开孔凿岩操控，增大凿岩机损耗。现有技术中采用多路换向阀直接进行冲击控制，大流量的高压冲击油直接通过多路换向进入凿岩机，在多路换向阀上产生较大的压力损失，降低了系统效率；同时多路阀换向阀始终承受高压冲击，给系统的可靠性带来较大影响。现有冲击液压动力源不能根据冲击工况自动适应调整系统压力，液压泵保持较高工作压力以满足高压冲击、低压冲击两种不同工况需求，系统发热大，影响液压控制系统效率。
因此，如何提供一种能够克服上述问题的冲击控制液压系统是本领域技术人员目前需要解决的技术问题。
发明内容
本发明的目的是提供一种凿岩台车的冲击控制液压系统，多路换向阀控制高冲和低冲的先导控制油路，大流量高压冲击油通过液控逻辑阀的开断控制直 接进入凿岩机，避免了阀控产生较大的压力损失，提高了系统效率；采用小流量多路换向阀作为先导实现冲击控制，降低了系统成本，避免了多路换向阀高压冲击，提高了系统可靠性。本发明的另一目的是提供一种包括上述冲击控制液压系统的凿岩台车。
为解决上述技术问题，本发明提供一种凿岩台车的冲击控制液压系统，包括液压泵、凿岩机和多路换向阀，所述多路换向阀的两个工作油口分别连通第一液控方向阀的液控油口和第二液控方向阀的液控油口，所述液压泵的输出口通过液控逻辑阀连通所述凿岩机，所述液压泵的输出口通过所述第一液控方向阀连通第一溢流阀，所述液压泵的输出口通过所述第二液控方向阀连通第二溢流阀，还包括梭阀，所述梭阀的两个进油口分别连通所述第一溢流阀的进油口和所述第二溢流阀的进油口，所述梭阀的出油口连通所述液控逻辑阀的液控油口，所述第一溢流阀的设定压力小于所述第二溢流阀的设定压力；
所述多路换向阀处于第一工作位时，所述第一液控方向阀和所述第二液控方向阀均关闭，所述液控逻辑阀关闭，所述凿岩机停止工作；
所述多路换向阀处于第二工作位时，所述第一液控方向阀打开，所述第二液控方向阀关闭，液压油经由所述梭阀进入所述液控逻辑阀的液控油口，所述液控逻辑阀打开，所述凿岩机处于开孔模式；
所述多路换向阀处于第三工作位时，所述第二液控方向阀打开，所述第一液控方向阀关闭，液压油经由所述梭阀进入所述液控逻辑阀的液控油口，所述液控逻辑阀打开，所述凿岩机处于凿岩模式。
优选地，所述多路换向阀具体为手动三位六通换向阀，所述手动三位六通换向阀处于第一工作位时，隔绝所述液压泵和所述第一液控方向阀的液控油口及所述第二液控方向阀的液控油口；所述手动三位六通换向阀处于第二工作位时，液压油能够进入所述第一液控方向阀的液控油口；所述手动三位六通换向阀处于第三工作位时，液压油能够进入所述第二液控方向阀的液控油口。
优选地，所述手动三位六通换向阀和所述液压泵之间设置有安全单向阀和安全溢流阀。
优选地，所述液压泵和所述液控逻辑阀之间设置有减压阀。
优选地，所述液压泵和所述第一液控方向阀及所述第二液控方向阀之间设 置有第一阻尼；所述第一液控方向阀和所述第一溢流阀之间设置有第四阻尼，所述第二液控方向阀和所述第二溢流阀之间设置有第五阻尼。
优选地，所述第一液控方向阀及所述第二液控方向阀具体为二位三通液控方向阀。
优选地，所述液压泵控制腔还连通并联设置的电磁球阀、第三溢流阀和第四溢流阀，所述第三溢流阀的预设压力大于第四溢流阀的预设压力，所述第三溢流阀和所述第四溢流阀之间设置有液控二通方向阀，所述液控二通方向阀的液控油口连通所述梭阀的出油口，所述液控二通方向阀的开启压力介于所述第一溢流阀的预设压力与所述第二溢流阀的预设压力之间；
系统启动时，所述电磁球阀处于第一工作位时，所述液压泵控制腔能够通过所述电磁球阀连通油箱；
所述多路换向阀处于第一工作位时，所述液控二通方向阀处于第一工作位，所述液压泵通过所述第四溢流阀连通油箱；所述多路换向阀处于第二工作位时，所述液控二通方向阀处于第一工作位，所述液压泵通过所述第四溢流阀连通油箱；
所述多路换向阀处于第三工作位时，所述液控二通方向阀处于第二工作位，所述液压泵通过所述第三溢流阀连通油箱。
本发明提供一种凿岩台车，包括冲击控制液压系统，所述冲击控制液压系统具体为上述任意一项所述的冲击控制液压系统。
本发明提供一种凿岩台车的冲击控制液压系统，包括液压泵、凿岩机和多路换向阀，多路换向阀的两个工作油口分别连通第一液控方向阀的液控油口和第二液控方向阀的液控油口，液压泵的输出口通过液控逻辑阀连通凿岩机，液压泵的输出口通过第一液控方向阀连通第一溢流阀，液压泵的输出口通过第二液控方向阀连通第二溢流阀，还包括梭阀，梭阀的两个进油口分别连通第一溢流阀的进油口和第二溢流阀的进油口，梭阀的出油口连通液控逻辑阀的液控油口，第一溢流阀的设定压力小于第二溢流阀的设定压力；多路换向阀处于第一工作位时，第一液控方向阀和第二液控方向阀均关闭，液控逻辑阀关闭，凿岩机停止工作；多路换向阀处于第二工作位时，第一液控方向阀打开，第二液控方向阀关闭，液压油经由梭阀进入液控逻辑阀的液控油口，液控逻辑阀打开， 凿岩机处于开孔模式；多路换向阀处于第三工作位时，第二液控方向阀打开，第一液控方向阀关闭，液压油经由梭阀进入液控逻辑阀的液控油口，液控逻辑阀打开，凿岩机处于凿岩模式。
系统具有高冲击和低冲击两种工作方式，以适应不同工作要求。多路换向阀具有定位功能，三个不同位置都能锁定，上位是待机位，冲击不工作；中位是开孔控制，低冲击压力；下位是凿岩控制，高冲击压力；从待机到开孔，再到凿岩，手柄控制顺序操作，操控流畅。
高压冲击油与多路换向阀的进油并联，多路换向阀作为冲击先导控制，高冲压力和低冲压力通过溢流阀分别设定，多路换向阀控制液控方向阀换向，接通冲击先导控制油，使能冲击功能，高压冲击油不经过多路换向阀而直接通过液控逻辑阀接入凿岩机。
高冲击和低冲击对应不同的冲击控制先导压力，将该先导压力反馈到液控二通方向阀，通过液控二通方向阀控制选择不同的溢流阀，溢流阀的设定压力控制恒压变量泵出口压力，进而实现液压泵压力与高冲击、低冲击控制的自适应控制。
多路换向阀控制高冲和低冲的先导控制油路，大流量高压冲击油通过阀的开断控制直接进入凿岩机，避免了阀控产生较大的压力损失，提高了系统效率；采用小流量多路阀作为先导实现冲击控制，降低了系统成本，避免了多路换向阀高压冲击，提高了系统可靠性。提高了凿岩机的使用寿命；液压泵压力根据冲击控制方式自适应调整压力，降低了压力损失，减小发热，提高了系统的可靠性。
本发明还提供一种包括上述冲击控制液压系统的凿岩台车，由于上述冲击控制液压系统具有上述技术效果，上述凿岩台车也应具有同样的技术效果，在此不再详细介绍。
附图说明
图1为本发明所提供的冲击控制液压系统的一种具体实施方式的液压原理图。
具体实施方式
本发明的核心是提供一种凿岩台车的冲击控制液压系统，多路换向阀控制 高冲和低冲的先导控制油路，大流量高压冲击油通过液控逻辑阀的开断控制直接进入凿岩机，避免了阀控产生较大的压力损失，提高了系统效率；采用小流量多路换向阀作为先导实现冲击控制，降低了系统成本，避免了多路换向阀高压冲击，提高了系统可靠性。本发明的另一核心是提供一种包括上述冲击控制液压系统的凿岩台车。
为了使本技术领域的人员更好地理解本发明方案，下面结合附图和具体实施方式对本发明作进一步的详细说明。
请参考图1，图1为本发明所提供的冲击控制液压系统的一种具体实施方式的液压原理图。
本发明具体实施方式提供一种凿岩台车的冲击控制液压系统，包括液压泵2、凿岩机22和多路换向阀3，其中液压泵2通过电机1驱动，多路换向阀3的进油口P连通液压泵2的输出口，多路换向阀3的回油口T连通油箱，多路换向阀3的另一个进油口P 1连通液压泵2的输出口，多路换向阀3的一个工作油口A连通第一液控方向阀14的液控油口，多路换向阀3的另一个工作油口B连通第二液控方向阀13的液控油口。为了提高安全性还可以在多路换向阀3和液压泵2之间设置安全单向阀5和安全溢流阀4
同时，液压泵2的输出口通过液控逻辑阀12连通凿岩机22，第一液控方向阀14的进油口P连通液压泵2的输出口，第一液控方向阀14的出油口T连通油箱，第一液控方向阀14的工作油口A连通第一溢流阀20的进油口。第二液控方向阀13的进油口P连通液压泵2的输出口，第二液控方向阀13的出油口T连通油箱，第二液控方向阀13的工作油口A连通第二溢流阀21的进油口。
梭阀19的两个进油口分别连通第一溢流阀20的进油口和第二溢流阀21的进油口，梭阀19的出油口连通液控逻辑阀12的液控油口，第一溢流阀20的设定压力小于第二溢流阀21的设定压力。
多路换向阀3处于第一工作位时，液压油无法经由多路换向阀3流向第一液控方向阀14的液控油口和第二液控方向阀13的液控油口，两者均处于关闭状态，因此液压油也就无法通过两者流向液控逻辑阀12的液控油口，液控逻辑阀12关闭，液压油无法进入凿岩机22，凿岩机22停止冲击工作。
多路换向阀3处于第二工作位时，液压油经由多路换向阀3进入第一液控方向阀14的液控油口，第一液控方向阀14打开，同时液压油无法进入第二液控方向阀13的液控油口，第二液控方向阀13关闭，液压油经由第一液控方向阀14后到达第一溢流阀20处，只要此处压力小于第一溢流阀20的设定压力，液压即可通过梭阀19进入液控逻辑阀12的液控油口，此时的压力可以打开液控逻辑阀12，液压油通过液控逻辑阀12进入凿岩机22，凿岩机22处于开孔模式。
多路换向阀3处于第三工作位时，液压油经由多路换向阀3进入第二液控方向阀13的液控油口，第二液控方向阀13打开，同时液压油无法进入第一液控方向阀14的液控油口，第一液控方向阀14关闭，液压油经由第二液控方向阀13后到达第二溢流阀21处，只要此处压力小于第二溢流阀21的设定压力，液压即可通过梭阀19进入液控逻辑阀12的液控油口，此时的压力可以打开液控逻辑阀12，液压油通过液控逻辑阀12进入凿岩机22，凿岩机22处于凿岩模式。
具体地，多路换向阀3可以为手动三位六通换向阀，手动三位六通换向阀处于第一工作位时，多路换向阀3的进油口P隔绝第一工作油口A和第二工作油口B，隔绝液压泵2和第一液控方向阀14的液控油口及第二液控方向阀13的液控油口。手动三位六通换向阀处于第二工作位时，多路换向阀3的进油口P仅连通第一工作油口A，液压油能够进入第一液控方向阀14的液控油口；手动三位六通换向阀处于第三工作位时，多路换向阀3的进油口P仅连通第二工作油口B，液压油能够进入第二液控方向阀13的液控油口。第一液控方向阀14及第二液控方向阀13具体为二位三通液控方向阀，可以根据情况调整阀门的类型、通道数量及工作位数等，均在本发明的保护范围之内。
在本发明具体实施方式提供的冲击控制液压系统中，液压泵2和液控逻辑阀12之间设置有减压阀11。同时，液压泵2和第一液控方向阀14及第二液控方向阀13之间设置有第一阻尼10；第一液控方向阀14和第一溢流阀20之间设置有第四阻尼17，第二液控方向阀13和第二溢流阀21之间设置有第五阻尼18。多路换向阀3和第一液控方向阀14液控油口之间的管路上通过第三阻尼16连通油箱，多路换向阀3和第二控换向阀13液控油口之间的管路上通 过第二阻尼15连通油箱
在上述各具体实施方式提供的冲击控制液压系统的基础上，液压泵2控制腔还连通并联设置的电磁球阀7、第三溢流阀8和第四溢流阀9，第三溢流阀8的预设压力大于第四溢流阀9的预设压力，第三溢流阀8和第四溢流阀9之间设置有液控二通方向阀6，液控二通方向阀6的液控油口连通梭阀19的出油口，液控二通方向阀6的开启压力介于第一溢流阀20的预设压力与第二溢流阀21的预设压力之间；
系统启动时，电磁球阀7处于第一工作位时，液压泵2控制腔能够通过电磁球阀7连通油箱；系统启动完成，电磁球阀7处于第二工作位，液压泵2控制腔能够通过第二溢流阀8或第三溢流阀9连通油箱；多路换向阀3处于第一工作位时，液控二通方向阀6处于第一工作位，液压泵2控制腔通过第四溢流阀9连通油箱；多路换向阀3处于第二工作位时，液控二通方向阀6处于第一工作位，液压泵2控制腔通过第四溢流阀9连通油箱；多路换向阀3处于第三工作位时，液控二通方向阀6处于第二工作位，液压泵2控制腔通过第三溢流阀8连通油箱。
具体工作方式为：初始状态时，电磁球阀7未上电，液压泵2控制腔能够通过电磁球阀7连通油箱，多路换向阀3操作手柄定位在第一工作位，液压泵2的控制油X处于卸荷状态，恒压压力设定值较低，启动电机1，液压泵2卸载启动，泵出口压力维持较低的恒定压力值。然后电磁球阀7上电，液压泵2的控制油X处压力由第四溢流阀9设定，即此时液压泵2通过第四溢流阀9连通油箱，液压泵2出口压力达到低冲压力设定值，但是此时液控逻辑阀12关闭，无冲击动作。
手柄控制多路换向阀3换向到第二工作位，进行开孔控制，多路换向阀3的P通A，第一液控方向阀14换向，液压泵2出口高压油经过阻尼10到第一液控方向阀14的P口，第一液控方向阀14的P通A，高压油经过阻尼17和溢流阀20溢流，此时梭阀19的出口先导压力为第一溢流阀20的设定压力，液控逻辑阀12打开，液压泵2出口高压油经过减压阀11和液控逻辑阀12进入凿岩机22，以低冲压力工作，低冲压力与减压阀11的先导控制压力相关。液控二通方向阀6的弹簧设定压力介入溢流阀20和溢流阀21之间，此时梭阀 19的出口先导压力不能使其换向，液压泵2控制腔X处压力由第四溢流阀9设定，即此时液压泵2控制腔通过第四溢流阀9连通油箱，液压泵2出口压力继续以低冲压力对应的设定值工作。
手柄控制多路换向阀3换向到第三工作位，进行凿岩控制，多路换向阀3的P通B，第二液控方向阀13换向，P通A；多路换向阀3A口通过阻尼16连通油箱，第一液控方向阀14不换向，A通T。液压泵2出口高压油经过阻尼10到第二液控方向阀13的P口，第二液控方向阀13的P通A，高压油经过阻尼18和第二溢流阀21溢流，此时梭阀19的出口先导压力为溢流阀21的设定压力，液控逻辑阀12打开，液压泵2出口高压油经过减压阀11和液控逻辑阀12进入凿岩机22，以高冲压力工作，低冲压力与减压阀11的先导控制压力相关。液控二通方向阀6的弹簧设定压力介入溢流阀20和溢流阀21之间，此时梭阀19的出口先导压力使其换向，液压泵2控制腔X处压力由第三溢流阀8设定，液压泵2控制腔通过第三溢流阀8连通油箱，液压泵2出口压力高冲压力对应的设定值工作。
手柄控制多路换向阀3换向到第一工作位，多路换向阀3的A和B通T回油箱，第二液压方向阀13和第一液控方向阀14不换向，因此梭阀19的输出先导压力为零，液控逻辑阀12关闭，冲击不工作。
因此开孔阶段，凿岩机22以低冲压力工作，冲击压力由第一溢流阀20设定，液压泵2出口压力由第四溢流阀9设定。凿岩阶段，凿岩机22以高冲压力工作，冲击压力由第二溢流阀21设定，液压泵出口压力由第三溢流阀8设定，凿岩机22冲击控制在不同的工作阶段泵出口压力自适应调整。
系统具有高冲击和低冲击两种工作方式，以适应不同工作要求。多路换向阀3具有定位功能，三个不同位置都能锁定，上位是待机位，冲击不工作；中位是开孔控制，低冲击压力；下位是凿岩控制，高冲击压力；从待机到开孔，再到凿岩，手柄控制顺序操作，操控流畅。
高压冲击油与多路换向阀3的进油并联，多路换向阀3作为冲击先导控制，高冲压力和低冲压力通过溢流阀分别设定，多路换向阀3控制液控方向阀换向，接通冲击先导控制油，使能冲击功能，高压冲击油不经过多路换向阀而直接通过液控逻辑阀12接入凿岩机22。
高冲击和低冲击对应不同的冲击控制先导压力，将该先导压力反馈到液控二通方向阀6，通过液控二通方向阀6控制选择不同的溢流阀，溢流阀的设定压力控制恒压变量泵出口压力，进而实现液压泵2压力与高冲击、低冲击控制的自适应控制。
多路换向阀3控制高冲和低冲的先导控制油路，大流量高压冲击油通过阀的开断控制直接进入凿岩机22，避免了阀控产生较大的压力损失，提高了系统效率；采用小流量多路阀作为先导实现冲击控制，降低了系统成本，避免了多路换向阀高压冲击，提高了系统可靠性。提高了凿岩机22的使用寿命；液压泵2压力根据冲击控制方式自适应调整压力，降低了压力损失，减小发热，提高了系统的可靠性。
除了上述冲击控制液压系统，本发明的具体实施方式还提供一种包括上述冲击控制液压系统的凿岩台车，该凿岩台车其他各部分的结构请参考现有技术，本文不再赘述。
以上对本发明所提供的凿岩台车及其冲击控制液压系统进行了详细介绍。本文中应用了具体个例对本发明的原理及实施方式进行了阐述，以上实施例的说明只是用于帮助理解本发明的方法及其核心思想。应当指出，对于本技术领域的普通技术人员来说，在不脱离本发明原理的前提下，还可以对本发明进行若干改进和修饰，这些改进和修饰也落入本发明权利要求的保护范围内。

Claims (8)

  1. 一种凿岩台车的冲击控制液压系统，包括液压泵(2)、凿岩机(22)和多路换向阀(3)，其特征在于，所述多路换向阀(3)的两个工作油口分别连通第一液控方向阀(14)的液控油口和第二液控方向阀(13)的液控油口，所述液压泵(2)的输出口通过液控逻辑阀(12)连通所述凿岩机(22)，所述液压泵(2)的输出口通过所述第一液控方向阀(14)连通第一溢流阀(20)，所述液压泵(2)的输出口通过所述第二液控方向阀(13)连通第二溢流阀(21)，还包括梭阀(19)，所述梭阀(19)的两个进油口分别连通所述第一溢流阀(20)的进油口和所述第二溢流阀(21)的进油口，所述梭阀(19)的出油口连通所述液控逻辑阀(12)的液控油口，所述第一溢流阀(20)的设定压力小于所述第二溢流阀(21)的设定压力；
    所述多路换向阀(3)处于第一工作位时，所述第一液控方向阀(14)和所述第二液控方向阀(13)均关闭，所述液控逻辑阀(12)关闭，所述凿岩机(22)停止工作；
    所述多路换向阀(3)处于第二工作位时，所述第一液控方向阀(14)打开，所述第二液控方向阀(13)关闭，液压油经由所述梭阀(19)进入所述液控逻辑阀(12)的液控油口，所述液控逻辑阀(12)打开，所述凿岩机(22)处于开孔模式；
    所述多路换向阀(3)处于第三工作位时，所述第二液控方向阀(13)打开，所述第一液控方向阀(14)关闭，液压油经由所述梭阀(19)进入所述液控逻辑阀(12)的液控油口，所述液控逻辑阀(12)打开，所述凿岩机(22)处于凿岩模式。
  2. 根据权利要求1所述的冲击控制液压系统，其特征在于，所述多路换向阀(3)具体为手动三位六通换向阀，所述手动三位六通换向阀处于第一工作位时，隔绝所述液压泵(2)和所述第一液控方向阀(14)的液控油口及所述第二液控方向阀(13)的液控油口；所述手动三位六通换向阀处于第二工作位时，液压油能够进入所述第一液控方向阀(14)的液控油口；所述手动三位六通换向阀处于第三工作位时，液压油能够进入所述第二液控方向阀(13)的 液控油口。
  3. 根据权利要求2所述的冲击控制液压系统，其特征在于，所述手动三位六通换向阀和所述液压泵(2)之间设置有安全单向阀(5)和安全溢流阀(4)。
  4. 根据权利要求1所述的冲击控制液压系统，其特征在于，所述液压泵(2)和所述液控逻辑阀(12)之间设置有减压阀(11)。
  5. 根据权利要求1所述的冲击控制液压系统，其特征在于，所述液压泵(2)和所述第一液控方向阀(14)及所述第二液控方向阀(13)之间设置有第一阻尼(10)；所述第一液控方向阀(14)和所述第一溢流阀(20)之间设置有第四阻尼(17)，所述第二液控方向阀(13)和所述第二溢流阀(21)之间设置有第五阻尼(18)。
  6. 根据权利要求5所述的冲击控制液压系统，其特征在于，所述第一液控方向阀(14)及所述第二液控方向阀(13)具体为二位三通液控方向阀。
  7. 根据权利要求1至6任意一项所述的冲击控制液压系统，其特征在于，所述液压泵(2)控制腔还连通并联设置的电磁球阀(7)、第三溢流阀(8)和第四溢流阀(9)，所述第三溢流阀(8)的预设压力大于第四溢流阀(9)的预设压力，所述第三溢流阀(8)和所述第四溢流阀(9)之间设置有液控二通方向阀(6)，所述液控二通方向阀(6)的液控油口连通所述梭阀(19)的出油口，所述液控二通方向阀(6)的开启压力介于所述第一溢流阀(20)的预设压力与所述第二溢流阀(21)的预设压力之间；
    系统启动时，所述电磁球阀(7)处于第一工作位，所述液压泵(2)控制腔能够通过所述电磁球阀(7)连通油箱；启动完成后，所述电磁球阀(7)处于第二工作位，所述液压泵(2)控制腔能够通过所述第三溢流阀(8)或所述第四溢流阀(9)连通油箱；
    所述多路换向阀(3)处于第一工作位时，所述液压泵(2)控制腔能够通过所述电磁球阀(7)连通油箱；
    所述多路换向阀(3)处于第二工作位时，所述液控二通方向阀(6)处于第一工作位，所述液压泵(2)通过所述第四溢流阀(9)连通油箱；
    所述多路换向阀(3)处于第三工作位时，所述液控二通方向阀(6)处于第二工作位，所述液压泵(2)通过所述第三溢流阀(8)连通油箱。
  8. 一种凿岩台车，包括冲击控制液压系统，其特征在于，所述冲击控制液压系统具体为权利要求1至7任意一项所述的冲击控制液压系统。
PCT/CN2019/124223 2018-12-10 2019-12-10 凿岩台车的冲击控制液压系统 WO2020119668A1 (zh)

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