CN114198349B - Continuous wall chain cutter rotation closed hydraulic system and continuous wall equipment - Google Patents

Continuous wall chain cutter rotation closed hydraulic system and continuous wall equipment Download PDF

Info

Publication number
CN114198349B
CN114198349B CN202111562646.5A CN202111562646A CN114198349B CN 114198349 B CN114198349 B CN 114198349B CN 202111562646 A CN202111562646 A CN 202111562646A CN 114198349 B CN114198349 B CN 114198349B
Authority
CN
China
Prior art keywords
oil
port
valve
pump
cartridge valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
CN202111562646.5A
Other languages
Chinese (zh)
Other versions
CN114198349A (en
Inventor
李晓星
曾庆峰
范亚雄
廉世宣
胡鑫乐
梁刚
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
China Railway Construction Heavy Industry Group Co Ltd
Original Assignee
China Railway Construction Heavy Industry Group Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by China Railway Construction Heavy Industry Group Co Ltd filed Critical China Railway Construction Heavy Industry Group Co Ltd
Priority to CN202111562646.5A priority Critical patent/CN114198349B/en
Publication of CN114198349A publication Critical patent/CN114198349A/en
Application granted granted Critical
Publication of CN114198349B publication Critical patent/CN114198349B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F5/00—Dredgers or soil-shifting machines for special purposes
    • E02F5/02—Dredgers or soil-shifting machines for special purposes for digging trenches or ditches
    • E02F5/14—Component parts for trench excavators, e.g. indicating devices travelling gear chassis, supports, skids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • 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
    • F15B2013/002—Modular valves, i.e. consisting of an assembly of interchangeable components
    • F15B2013/004—Cartridge valves
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

The invention discloses a continuous wall chain cutter rotary closed hydraulic system and continuous wall equipment, wherein the continuous wall chain cutter rotary closed hydraulic system comprises a hydraulic motor, a first load oil circuit, a second load oil circuit, a first power system and a second power system, wherein the hydraulic motor is used for driving a chain wheel and a chain to run; the hydraulic motor comprises a first oil port communicated with the first load oil way and a second oil port communicated with the second load oil way; the first power system and the second power system are connected in parallel between the first load oil circuit and the second load oil circuit. According to the continuous wall chain cutter rotary closed hydraulic system, the double-power system is adopted to control the hydraulic motor to carry out rotary cutting, so that the problem that the maintenance period is long when a single power source fails can be solved; and the hydraulic motor rotary cutting can be controlled through the double-power system, the cutting speed is high, the construction can be rapidly completed on the soft soil foundation and the sand foundation, and the construction period is effectively ensured.

Description

Continuous wall chain cutter rotation closed hydraulic system and continuous wall equipment
Technical Field
The invention relates to the technical field of continuous wall chain cutter rotation control, in particular to a continuous wall chain cutter rotation closed hydraulic system and continuous wall equipment.
Background
With the continuous upgrading of the construction scale of domestic cities, the ground space becomes saturated. People begin to turn their eyes into the ground, seeking space for urban development. The chain-cutter type continuous wall equipment is a key equipment for TRD construction, is a continuous underground wall formed by special grooving equipment and machines, has high rigidity and high soil pressure bearing capacity, is not easy to collapse, foundation precipitation and other accidents, and is widely applied to water stopping and soil retaining construction of projects such as subway stations, urban comprehensive pipe galleries, building basements, underground parking lots and the like.
For the current single-power continuous wall hydraulic control system, because the pressure, flow and power required by the system are large, a large-specification hydraulic pump is required, and meanwhile, a large-specification engine is required to be configured to provide a power source, so that the design space of equipment is increased, meanwhile, the noise of the equipment is large, once the power source fails, the disassembly and maintenance period is long, the construction period is seriously influenced, and the construction cost is directly increased.
In summary, how to solve the problem of long disassembly and maintenance period after the power source failure of the continuous wall chain cutter rotary hydraulic control system has become a technical problem to be solved by those skilled in the art.
Disclosure of Invention
The invention aims to provide a continuous wall chain cutter rotary closed hydraulic system and continuous wall equipment, which are used for solving the problem that the continuous wall chain cutter rotary hydraulic control system has a long disassembly and maintenance period after a power source is in fault.
In order to achieve the above purpose, the invention provides a continuous wall chain cutter rotary closed hydraulic system, which comprises a hydraulic motor, a first load oil circuit, a second load oil circuit, a first power system and a second power system, wherein the hydraulic motor is used for driving a chain wheel and a chain to run;
the hydraulic motor comprises a first oil port communicated with the first load oil way and a second oil port communicated with the second load oil way;
the first power system and the second power system are connected in parallel between the first load oil circuit and the second load oil circuit.
Preferably, the first power system comprises a first control valve group, a first closed bidirectional variable plunger pump for providing pressure oil for the hydraulic motor and a first power source for driving the first closed bidirectional variable plunger pump, wherein the first closed bidirectional variable plunger pump comprises a first pump oil port, a second pump oil port and a first oil suction port for sucking oil in an oil tank; the first pump oil port is communicated with the first load oil path through a first main oil path, a first cartridge valve is arranged on the first main oil path, the second pump oil port is communicated with the second load oil path through a second main oil path, and a second cartridge valve is arranged on the second main oil path; the first control valve group is used for controlling the opening and closing of the first cartridge valve and the second cartridge valve.
Preferably, the second power system comprises a second control valve group, a second closed bidirectional variable plunger pump for providing pressure oil for the hydraulic motor and a second power source for driving the second closed bidirectional variable plunger pump, and the second closed bidirectional variable plunger pump comprises a third pump oil port, a fourth pump oil port and a second oil suction port for sucking oil in an oil tank; the third pump oil port is communicated with the first load oil path through a third main oil path, a third cartridge valve is arranged on the third main oil path, the fourth pump oil port is communicated with the second load oil path through a fourth main oil path, and a fourth cartridge valve is arranged on the fourth main oil path; the second control valve group is used for controlling the opening and closing of the third cartridge valve and the fourth cartridge valve.
Preferably, the first control valve group and the second control valve group are two-position four-way electromagnetic reversing valves, and the first control valve group and the second control valve group are integrally controlled through a shuttle valve group; the shuttle valve group comprises a first shuttle valve arranged between a first main oil way and a second main oil way, a second shuttle valve arranged between a third main oil way and a fourth main oil way, a third shuttle valve arranged between a first load oil way and a second load oil way, a fourth shuttle valve arranged between an oil pressure outlet of the second shuttle valve and an oil pressure outlet of the third shuttle valve and a fifth shuttle valve arranged between an oil pressure outlet of the fourth shuttle valve and an oil pressure outlet of the first shuttle valve, wherein the oil pressure outlet of the fifth shuttle valve is simultaneously connected with a P port of a first control valve group and a P port of a second control valve group, and a T port of the first control valve group and a T port of the second control valve group are both communicated with the oil tank.
Preferably, a first damping throttle valve is arranged between the port A of the first control valve bank and the control cavity port of the first cartridge valve, a second damping throttle valve is arranged between the port A of the first control valve bank and the control cavity port of the second cartridge valve, a third damping throttle valve is arranged between the port A of the second control valve bank and the control cavity port of the third cartridge valve, and a fourth damping throttle valve is arranged between the port A of the second control valve bank and the control cavity port of the fourth cartridge valve.
Preferably, the first power source is an electric motor, and the second power source is an engine.
Preferably, the first closed bidirectional variable plunger pump and the second closed bidirectional variable plunger pump are both provided with a built-in oil supplementing pump, and an oil suction port of the built-in oil supplementing pump is communicated with the oil tank.
Preferably, the first closed bidirectional variable plunger pump and the second closed bidirectional variable plunger pump are hydraulic pump bodies with the model code A4VG250EP4D of the Lishile brand.
Compared with the background technology, the continuous wall chain cutter rotary closed hydraulic system comprises a hydraulic motor, a first load oil circuit, a second load oil circuit, a first power system and a second power system, wherein the hydraulic motor is used for driving a chain wheel and a chain to run; the hydraulic motor comprises a first oil port communicated with the first load oil way and a second oil port communicated with the second load oil way; the first power system and the second power system are connected in parallel between the first load oil circuit and the second load oil circuit. According to the continuous wall chain cutter rotary closed hydraulic system, the double-power system is adopted to control the hydraulic motor to carry out rotary cutting, so that the problem that the maintenance period is long when a single power source fails can be solved; and the hydraulic motor rotary cutting can be controlled through the double-power system, the cutting speed is high, the construction can be rapidly completed on the soft soil foundation and the sand foundation, and the construction period is effectively ensured.
In addition, the invention also provides continuous wall equipment, which comprises a continuous wall chain cutter rotary closed hydraulic system, wherein the continuous wall chain cutter rotary closed hydraulic system is the continuous wall chain cutter rotary closed hydraulic system described in any scheme. Because the continuous wall chain cutter rotation closed hydraulic system has the technical effects, continuous wall equipment with the continuous wall chain cutter rotation closed hydraulic system also has corresponding technical effects, and the description is omitted here.
Drawings
Fig. 1 is a schematic diagram of a closed hydraulic system for swinging a continuous wall chain cutter according to an embodiment of the present invention;
fig. 2 is a schematic diagram of a hydraulic pump body of the type code A4VG250EP4D of the ristie brand provided in an embodiment of the present invention.
In the figures 1 and 2 of the drawings,
The hydraulic motor 10, the first oil port 10a, the second oil port 10b, the first load oil passage 11, the second load oil passage 12, the first control valve group 13, the first closed type bidirectional variable plunger pump 14, the first pump oil port 14a, the second pump oil port 14b, the first power source 15, the oil tank 16, the first main oil passage 17, the first cartridge valve 18, the second main oil passage 19, the second cartridge valve 20, the second control valve group 21, the second closed type bidirectional variable plunger pump 22, the second power source 23, the third pump oil port 24, the fourth pump oil port 25, the third main oil passage 26, the third cartridge valve 27, the fourth main oil passage 28, the fourth cartridge valve 29, the first shuttle valve 30, the second shuttle valve 31, the third shuttle valve 32, the fourth shuttle valve 33, the fifth shuttle valve 34, the first damping throttle 35, the second damping throttle 36, the third damping throttle 37, and the fourth damping throttle 38.
Detailed Description
The invention aims to provide a continuous wall chain cutter rotary closed hydraulic system and continuous wall equipment, which are used for solving the problem that the continuous wall chain cutter rotary hydraulic control system has a long disassembly and maintenance period after a power source is in fault.
In order to enable those skilled in the art to better understand the technical solutions provided by the present application, the technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present application, and it is obvious that the described embodiments are only some embodiments of the present application, not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the application without making any inventive effort, are intended to be within the scope of the application.
As shown in fig. 1 and 2, an embodiment of the present invention provides a continuous wall chain cutter rotation closed hydraulic system, which includes a hydraulic motor 10 for driving a sprocket chain to operate, a first load oil path 11, a second load oil path 12, a first power system and a second power system; the hydraulic motor 10 includes a first oil port 10a communicating with the first load oil passage 11 and a second oil port 10b communicating with the second load oil passage 12; the first power system and the second power system are connected in parallel between the first load oil passage 11 and the second load oil passage 12.
According to the continuous wall chain cutter rotary closed hydraulic system, the double-power system is adopted to control the hydraulic motor to carry out rotary cutting, so that the problem that the maintenance period is long when a single power source fails can be solved; and the hydraulic motor rotary cutting can be controlled through the double-power system, the cutting speed is high, the construction can be rapidly completed on the soft soil foundation and the sand foundation, and the construction period is effectively ensured.
The first power source 15 may be an electric motor, and the second power source 23 may be an engine. By the design mode, the single-engine pump set is started in an emergency, the chain cutter is controlled to cut in a rotary mode, and normal cutting of equipment in an emergency state is realized; the single motor pump group starts, controls the chain cutter to cut in a rotary way, has low noise and pollution, is suitable for construction in large cities at night, and has long effective construction time. The motor pump group and the engine pump group are started simultaneously, oil liquid is converged to control the chain cutter to rotationally cut, the cutting speed is high, the construction can be rapidly completed on a soft soil foundation and a sand foundation, and the construction period is effectively ensured.
In some specific embodiments, the first power system may specifically include a first control valve group 13, a first closed bidirectional variable displacement pump 14 for providing pressure oil to the hydraulic motor 10, and a first power source 15 for driving the first closed bidirectional variable displacement pump 14, where the first closed bidirectional variable displacement pump 14 includes a first pump port 14a, a second pump port 14b, and a first oil suction port for sucking oil in the oil tank 16; the first pump oil port 14a is communicated with the first load oil path 11 through a first main oil path 17, a first cartridge valve 18 is arranged on the first main oil path 17, the second pump oil port 14b is communicated with the second load oil path 12 through a second main oil path 19, and a second cartridge valve 20 is arranged on the second main oil path 19; the first control valve group 13 is used for controlling the opening and closing of the first cartridge valve 18 and the second cartridge valve 20. The first cartridge valve 18 and the second cartridge valve 20 are controlled to be opened and closed through the first control valve group 13, so that the first power system can control the forward and reverse rotation and stop of the hydraulic motor 10.
Similarly, the second power system may specifically include a second control valve group 21, a second closed bidirectional variable displacement pump 22 for providing pressure oil to the hydraulic motor 10, and a second power source 23 for driving the second closed bidirectional variable displacement pump 22, where the second closed bidirectional variable displacement pump 22 includes a third pump oil port 24, a fourth pump oil port 25, and a second oil suction port for sucking oil in the oil tank 16; the third pump oil port 24 is communicated with the first load oil path 11 through a third main oil path 26, a third cartridge valve 27 is arranged on the third main oil path 26, the fourth pump oil port 25 is communicated with the second load oil path 12 through a fourth main oil path 28, and a fourth cartridge valve 29 is arranged on the fourth main oil path 25. The second control valve group 21 controls the opening and closing of the third cartridge valve 27 and the fourth cartridge valve 29, so that the second power system can control the forward and reverse rotation and stop of the hydraulic motor 10.
In a further embodiment, the first control valve set 13 and the second control valve set 21 may specifically be two-position four-way electromagnetic reversing valves, and the first control valve set 13 and the second control valve set 21 are integrally controlled by a shuttle valve set; the shuttle valve group includes a first shuttle valve 30 provided between the first main oil passage 17 and the second main oil passage 19, a second shuttle valve 31 provided between the third main oil passage 26 and the fourth main oil passage 28, a third shuttle valve 32 provided between the first load oil passage 11 and the second load oil passage 12, a fourth shuttle valve 33 provided between an oil pressure outlet of the second shuttle valve 31 and an oil pressure outlet of the third shuttle valve 32, and a fifth shuttle valve 34 provided between an oil pressure outlet of the fourth shuttle valve 33 and an oil pressure outlet of the first shuttle valve 30, the oil pressure outlet of the fifth shuttle valve 34 being connected to both the P port of the first control valve group 13 and the P port of the second control valve group 21, and both the T port of the first control valve group 13 and the T port of the second control valve group 21 being in communication with the tank 16. The shuttle valve group is designed to select and output the highest oil pressure on the main oil path and the load oil path to the P port of the corresponding control valve group, so that the reliability of the system is ensured.
In some more specific embodiments, a first damping throttle valve 35 may be further disposed between the a port of the first control valve bank 13 and the control cavity port of the first cartridge valve 18, a second damping throttle valve 36 is disposed between the a port of the first control valve bank 13 and the control cavity port of the second cartridge valve 20, a third damping throttle valve 37 is disposed between the a port of the second control valve bank 21 and the control cavity port of the third cartridge valve 27, and a fourth damping throttle valve 38 is disposed between the a port of the second control valve bank 21 and the control cavity port of the fourth cartridge valve 29. Through designing damping throttle valves, namely a first damping throttle valve 35, a second damping throttle valve 36, a third damping throttle valve 37 and a fourth damping throttle valve 38, damping force is increased, dynamic vibration reduction is achieved, and control characteristics are improved.
In further embodiments, the first and second closed type bi-directional variable displacement pumps 14 and 22 may be configured with a built-in oil pump having an oil suction port in communication with the oil tank 16. Through the configuration built-in oil supplementing pump, can guarantee the inside fluid of pump body and full, guarantee the life of pump body.
In some more specific embodiments, the first and second closed type bi-directional variable displacement pumps 14, 22 may each be hydraulic pumps of the type A4VG250EP4D, particularly. The brand type hydraulic pump body is provided with the built-in oil supplementing pump, the stepless variable of which the output flow is between 0 and 100 percent is proportional to the current supplied by the electromagnet a or b of the EP valve of the hydraulic pump body, and the stopping, forward rotation, reverse rotation and stepless speed regulation of the hydraulic motor 10 can be realized through the first/second closed type bidirectional variable plunger pump; the schematic diagram of the hydraulic pump body of this brand model is shown in fig. 2.
In addition, the invention also provides continuous wall equipment, which comprises a continuous wall chain cutter rotary closed hydraulic system, wherein the continuous wall chain cutter rotary closed hydraulic system is the continuous wall chain cutter rotary closed hydraulic system described in any scheme. Because the continuous wall chain cutter rotation closed hydraulic system has the technical effects, continuous wall equipment with the continuous wall chain cutter rotation closed hydraulic system also has corresponding technical effects, and the description is omitted here.
In order to better understand the continuous wall chain cutter rotary closed hydraulic system provided by the invention by the person skilled in the art, the following description is given by a specific working process of the hydraulic system:
In the normal operation mode:
1) Standby state: the first power source 15 (motor) is started, the EP valve of the first closed type bidirectional variable plunger pump 14 is not electrified, the first closed type bidirectional variable plunger pump 14 is in zero displacement standby at the moment, the electromagnet of the first control valve group 13 and the electromagnet of the second control valve group 21 are not electrified, and at the moment, P is conducted with A and B is conducted with T; the first shuttle valve 30 is connected with the second main oil way 19 through the oil port 1, is connected with the first main oil way 17 through the oil port 3, collects high-pressure oil in the first main oil way 17 and the second main oil way 19 in real time, and outputs the high-pressure oil to the oil port 3 of the fifth shuttle valve 34 through the oil port 2 of the first shuttle valve 30, and the high-pressure oil output by the oil port 2 of the fifth shuttle valve 34 is the high-pressure oil in the first main oil way 17 and the second main oil way 19 because the oil port 1 pressure of the fifth shuttle valve 34 is 0; the high-pressure oil output by the oil port 2 of the fifth shuttle valve 34 is respectively connected with the P ports of the first control valve group 13 and the second control valve group 21; high-pressure oil in the first main oil path 17 and the second main oil path 19 flows through the P port and the a port of the first/second control valve group (i.e. the reversing valve group), and flows through the 1 port and the 2 port of the first/second/third/fourth damping throttle valve 35/36/37/38 respectively, and acts on the 3 ports of the control cavity of the corresponding first/second/third/fourth cartridge valve 18/20/27/29 respectively; at this time, the first/second/third/fourth cartridge valve 18/20/27/29 is not opened and the system is not operated.
2) Forward cutting of the chain cutter: in a standby state, the EP valve electromagnet b of the first closed bidirectional variable plunger pump 14 is electrified, the oil flowing direction is from the first oil pumping port 14a to the second oil pumping port 14b, and at the moment, the first oil pumping port 14a is a working port; at this time, the electromagnet of the first control valve group 13 is powered on, P is communicated with B, A and T, the pressure oil of the 3-port of the control cavity of the first cartridge valve 18 acts on the A-port of the first control valve group 13 along the 2-port and 1-port of the first damping throttle valve 35 and then is communicated with the T-port oil return tank, and similarly, the pressure oil of the 3-port of the control cavity of the second cartridge valve 20 acts on the A-port and then is communicated with the T-port oil return tank of the first control valve group 13 along the 2-port and 1-port of the second damping throttle valve 36, and at this time, the pressure of the control cavity of the first/second cartridge valve 18/20 is 0; the electromagnet of the second control valve group 21 is not powered, and the third cartridge valve 27 and the fourth cartridge valve 29 are not opened; the system pressure oil flows through the first main oil way 17 from the first pump oil port 14a to the 1 port of the first cartridge valve 18, and because the pressure of the 3 port of the control cavity of the first cartridge valve 18 is 0, the pressure oil acting on the oil port 1 of the first cartridge valve 18 pushes the valve core of the first cartridge valve 18 to move upwards, and the first cartridge valve 18 is opened to enable the 1 port and the 2 port of the first cartridge valve 18 to be communicated; the system pressure oil flows through the first main oil way 17 and the 1 st port and the 2 nd port of the first cartridge valve 18 from the first pump oil way 14a, and acts on the first oil way 10a of the hydraulic motor 10 through the first load oil way 11 to cut the motor in a forward rotation way, wherein the first load oil way 11 is also connected with the oil way 2 of the third cartridge valve 27, and as the third cartridge valve 27 is not opened, the oil of the first power source (namely the motor pump group) cannot be connected into the second power source (the engine pump group) through the third cartridge valve 27 in a series way, so that the system reliability is high; the system oil return flows through the second load oil way 12 from the second oil port 10b of the hydraulic motor 10 to the 2 port of the second cartridge valve 20, and because the pressure of the 3 port of the control cavity of the second cartridge valve 20 is 0, the pressure oil acting on the oil port 2 of the second cartridge valve 20 pushes the cartridge valve core to move upwards at the moment, and the second cartridge valve 20 is opened to enable the 2 port and the 1 port of the second cartridge valve 20 to be communicated; the system oil return flows from the second oil port 10b of the hydraulic motor 10 to the second oil port 14b of the first closed bidirectional variable plunger pump 14 from the second load oil way 12 to the 2 port and the 1 port of the second cartridge valve 20, and the forward rotation cutting work of the chain cutter is completed; the second load oil way 12 is further connected to the oil port 2 of the fourth cartridge valve 29, and since the fourth cartridge valve 29 is not opened, the oil in the motor pump set cannot be connected to the engine pump set through the fourth cartridge valve 29, and the reliability of the system is high.
The oil port 1 of the third shuttle valve 32 is connected with the first load oil path 11 of the hydraulic motor 10, the oil port 3 of the third shuttle valve 32 is connected with the second load oil path 12, high-pressure oil in the first load oil path 11 and the second load oil path 12 is collected in real time, and is output to the oil port 1 of the fourth shuttle valve 33 through the oil pressure outlet of the third shuttle valve 32 (namely, the oil port 2 thereof), and because the oil port 3 pressure of the fourth shuttle valve 33 is 0, the high-pressure oil output by the oil pressure outlet of the fourth shuttle valve 33 (namely, the oil port 2 thereof) is the high-pressure oil in the first load oil path 11 and the second load oil path 12; at this time, the high pressure oil of the first/second load oil paths is applied to the oil port 1 of the fifth shuttle valve 34, and the high pressure oil of the first main oil path 17 and the second main oil path 19 is applied to the oil port 3 of the fifth shuttle valve 34 of the shuttle valve, so the oil pressure outlet of the fifth shuttle valve 34 (i.e., the oil port 2 thereof) outputs the highest oil pressures on the main oil paths and the load oil paths.
In the forward rotation cutting process, the load pressure changes along with the change of the geological formation; assuming that the load pressure suddenly increases and is greater than the main oil passage pressure at this time, the pressure of the first port 10a of the hydraulic motor 10 increases, the pressure of the first load oil passage 11 increases, and the oil pressure outlet of the fifth shuttle valve 34 outputs the pressure oil on the first load oil passage 11. The pressure oil of the first load oil circuit 11 acts on the opening 3 of the control cavity of the third cartridge valve 27 through the shuttle valve group, the first load oil circuit 11 is connected with the oil port 2 of the third cartridge valve 27, the pressure of the opening 1 of the third cartridge valve 27 is 0, the pressure oil of the oil ports 2 and 3 is the pressure oil of the first load oil circuit 11, the pressure oil acting area of the oil port 3 is larger than the pressure oil acting area of the oil port 2, at the moment, the third cartridge valve 27 is still kept in a closed state, the oil of the first load oil circuit cannot flow into an engine pump set through the third cartridge valve 27, and the system is high in stability and good in reliability.
Chain cutter reverse cutting: in a standby state, an EP valve electromagnet a of the first closed bidirectional variable plunger pump 14 is electrified, the oil flowing direction is from a second oil pumping port 14b to a first oil pumping port 14a, and the second oil pumping port 14b is a working port; at this time, the electromagnet of the first control valve group 13 is powered on, P is communicated with B, A and T, the pressure oil of the 3-port of the control cavity of the first cartridge valve 18 acts on the A-port of the first control valve group 13 along the 2-port and 1-port of the first damping throttle valve 35 and then is communicated with the T-port oil return tank, and similarly, the pressure oil of the 3-port of the control cavity of the second cartridge valve 20 acts on the A-port and then is communicated with the T-port oil return tank of the first control valve group 13 along the 2-port and 1-port of the second damping throttle valve 36, and at this time, the pressure of the control cavity of the first/second cartridge valve 18/20 is 0; the electromagnet of the second control valve group 21 is not powered, and the third cartridge valve 27 and the fourth cartridge valve 29 are not opened; the system pressure oil flows through the second main oil way 19 from the second pump oil port 14b to the 1 port of the second cartridge valve 20, and because the pressure of the 3 port of the control cavity of the second cartridge valve 20 is 0, the pressure oil acting on the oil port 1 of the second cartridge valve 20 pushes the valve core of the second cartridge valve to move upwards, and the second cartridge valve 20 is opened to enable the 1 port and the 2 port of the second cartridge valve 20 to be communicated; the system pressure oil flows through the second main oil way 19 from the second oil pumping port 14b, and flows through the 1 port and the 2 port of the second cartridge valve 20, and acts on the second oil port 10b of the hydraulic motor 10 through the second load oil way 12 to reversely cut the hydraulic motor, wherein the second load oil way 12 is also connected with the oil port 2 of the fourth cartridge valve 29, and as the fourth cartridge valve 29 is not opened, the oil of the motor pump set cannot be connected into the engine pump set through the fourth cartridge valve 29, so that the system reliability is high; the system oil return flows through the first load oil way 11 from the first oil port 10a of the hydraulic motor to the 2 port of the first cartridge valve 18, and because the pressure of the 3 port of the control cavity of the first cartridge valve 18 is 0, the pressure oil acting on the oil port 2 of the first cartridge valve 18 pushes the cartridge valve core to move upwards at the moment, and the first cartridge valve 18 is opened to enable the 2 port and the 1 port of the first cartridge valve 18 to be communicated; the system oil return flows from a first oil port 10a of the hydraulic motor 10 to a first pump oil port 14a of the first closed bidirectional variable plunger pump 14 from a first load oil way 11 to a 2 port and a1 port of a first cartridge valve 18, and the chain cutter reverse cutting work is completed; the first load oil circuit 11 is further connected to the oil port 2 of the third cartridge valve 27, and since the third cartridge valve 27 is not opened, oil in the motor pump set cannot be connected to the engine pump set through the third cartridge valve 27, and system reliability is high.
In emergency mode of operation:
Standby state: the second power source 23 (engine) is started, the EP valve of the second closed type bidirectional variable plunger pump 22 is not electrified, the second closed type bidirectional variable plunger pump 22 is in zero displacement standby at the moment, the electromagnet of the first control valve group 13 and the electromagnet of the second control valve group 21 are not electrified, and at the moment, P is conducted with A and B is conducted with T; the second shuttle valve 31 is connected with the fourth main oil way 28 through the oil port 1 of the second shuttle valve 31, is connected with the third main oil way 26 through the oil port 3 of the second shuttle valve 31, collects high-pressure oil in the third main oil way 26 and the fourth main oil way 28 in real time, and outputs the high-pressure oil to the oil port 3 of the fourth shuttle valve 33 through the oil port 2 of the second shuttle valve 31, and the high-pressure oil output by the oil port 2 of the fourth shuttle valve 33 is the high-pressure oil in the third main oil way 26 and the fourth main oil way 28 because the oil port 1 pressure of the fourth shuttle valve 33 is 0; the high-pressure oil output from the oil port 2 of the fourth shuttle valve 33 acts on the 1 port of the fifth shuttle valve 34, and the high-pressure oil output from the oil port 2 of the fifth shuttle valve 34 is the high-pressure oil in the third main oil path 26 and the fourth main oil path 28 because the 3 port pressure of the fifth shuttle valve 34 is 0; the high-pressure oil output by the oil port 2 of the fifth shuttle valve 34 is respectively connected with the P ports of the first control valve group 13 and the second control valve group 21 (namely the reversing valve group); high-pressure oil in the third main oil path 26 and the fourth main oil path 28 flows through the port P and the port A of the reversing valve group, respectively flows through the port 1 and the port 2 of the first/second/third/fourth damping throttle valve 35/36/37/38, and acts on the port 3 of the control cavity of the corresponding first/second/third/fourth cartridge valve 18/20/27/29; at this time, the first/second/third/fourth cartridge valve 18/20/27/29 is not opened and the system is not operated.
Forward cutting of the chain cutter: in a standby state, the EP valve electromagnet b of the second closed bidirectional variable plunger pump 22 is electrified, the oil flowing direction is from a third pump oil port 24 to a fourth pump oil port 25, and the third pump oil port 24 is a working oil port; at this time, the second control valve group 21 is powered on, P is connected B, A to T, the pressure oil at the 3 ports of the control chambers of the third cartridge valve 27 and the fourth cartridge valve 29 acts on the port a of the second control valve group 21 and then is connected to the T-port oil return tank along the 2 ports and 1 ports of the third damping throttle valve 37 and the fourth damping throttle valve 38, and at this time, the pressure of the control chambers of the third cartridge valve 27 and the fourth cartridge valve 29 is 0; the electromagnet of the first control valve group 13 is not powered, and the first cartridge valve 18 and the second cartridge valve 20 are not opened; the system pressure oil flows through the third main oil way 26 from the third pump oil port 24 to the 1 port of the third cartridge valve 27, and the pressure oil acting on the oil port 1 of the third cartridge valve 27 pushes the cartridge valve core to move upwards at the moment because the pressure of the 3 port of the control cavity of the third cartridge valve 27 is 0, and the third cartridge valve 27 is opened to enable the 1 port and the 2 port of the third cartridge valve 27 to be communicated; the system pressure oil flows through the third main oil way 26 and the 1 st and 2 nd ports of the third cartridge valve 27 from the third pump oil way 24, and acts on the first oil way 10a of the hydraulic motor 10 through the first load oil way 11 to cut the motor in a forward rotation way, wherein the first load oil way 11 is also connected with the oil way 2 of the first cartridge valve 18, and as the first cartridge valve 18 is not opened, the oil of the engine pump set cannot be connected into the generator pump set through the first cartridge valve 18 in a serial way, and the system reliability is high; the system oil return flows through the second load oil way 12 from the second oil port 10b of the hydraulic motor 10 to the 2 port of the fourth cartridge valve 29, and because the pressure of the 3 port of the control cavity of the fourth cartridge valve 29 is 0, the pressure oil acting on the oil port 2 of the fourth cartridge valve 29 pushes the cartridge valve core to move upwards at the moment, and the fourth cartridge valve 29 is opened to enable the 2 port and the 1 port of the fourth cartridge valve 29 to be communicated; the system oil return flows from the second oil port 10b of the hydraulic motor to the 2 port and the 1 port of the fourth cartridge valve 29 through the second load oil way 12 and returns to the fourth pump oil port 25 of the second closed bidirectional variable plunger pump 22, so that the forward rotation cutting work of the chain cutter is completed; the second load oil way 12 is further connected to the oil port 2 of the second cartridge valve 20, and since the second cartridge valve 20 is not opened, the oil in the engine pump set cannot be connected to the motor pump set through the second cartridge valve 20, and the reliability of the system is high.
Chain cutter reverse cutting: in a standby state, an EP valve electromagnet a of the second closed bidirectional variable plunger pump 22 is electrified, the oil flowing direction is from a fourth pump oil port 25 to a third pump oil port 24, and the fourth pump oil port 25 is a working oil port; at this time, the electromagnet of the second control valve group 21 is powered on, P is communicated with B, A and T, the pressure oil at the 3 ports of the control cavities of the third cartridge valve 27 and the fourth cartridge valve 29 acts on the port A of the second control valve group 21 and the return tank at the T again along the 2 ports and 1 ports of the third damping throttle valve 37 and the fourth damping throttle valve 38 respectively, and at this time, the pressure of the control cavities of the third cartridge valve 27 and the fourth cartridge valve 29 is 0; the electromagnet of the first control valve group 13 is not powered, and the first cartridge valve 18 and the second cartridge valve 20 are not opened; the system pressure oil flows through the fourth main oil way 28 from the fourth pump oil port 25 to the 1 port of the fourth cartridge valve 29, and the pressure oil acting on the oil port 1 of the fourth cartridge valve 29 pushes the valve core of the cartridge valve to move upwards at the moment because the pressure of the 3 port of the control cavity of the fourth cartridge valve 29 is 0, and the fourth cartridge valve 29 is opened to enable the 1 port and the 2 port of the fourth cartridge valve 29 to be communicated; the system pressure oil flows through the fourth main oil way 28 and the 1 st and 2 nd ports of the fourth cartridge valve 29 from the fourth pump oil port 25, and acts on the second oil port 10b of the hydraulic motor 10 through the second load oil way 12 to reversely cut the hydraulic motor, wherein the second load oil way 12 is also connected with the oil port 2 of the second cartridge valve 20, and as the second cartridge valve 20 is not opened, the oil of the engine pump set cannot be connected into the motor pump set through the second cartridge valve 20, and the system reliability is high; the system oil return flows through the first load oil way 11 from the first oil port 10a of the hydraulic motor 10 to the 2 port of the third cartridge valve 27, and because the pressure of the 3 port of the control cavity of the third cartridge valve 27 is 0, the pressure oil acting on the oil port 2 of the third cartridge valve 27 pushes the cartridge valve core to move upwards at the moment, and the third cartridge valve 27 is opened to enable the 2 port and the 1 port of the third cartridge valve 27 to be communicated; the system oil return flows from a first oil port of the hydraulic motor 10 to 2 ports and 1 port of a third cartridge valve 27 through a first load oil way 11 and returns to a third pump oil port 24 port of a second closed bidirectional variable plunger pump 22, so that the chain cutter reverse cutting work is completed; the first load oil circuit 11 is further connected to the oil port 2 of the first cartridge valve 18, and since the first cartridge valve 18 is not opened, oil in the engine pump set cannot be connected to the motor pump set through the first cartridge valve 18, and system reliability is high.
In the confluence operation mode:
Standby state: the second power source 23 (engine) is started, the EP valve of the second closed type bidirectional variable plunger pump 22 is not electrified, the first power source 15 (motor) is started, the EP valve of the first closed type bidirectional variable plunger pump 14 is not electrified, and at the moment, the first closed type bidirectional variable plunger pump 14 and the second closed type bidirectional variable plunger pump 22 are in zero-displacement standby; the electromagnet of the first control valve group 13 and the electromagnet of the second control valve group 21 are not electrified, and at the moment, P is communicated with A and B is communicated with T; the second shuttle valve 31 is connected with the fourth main oil way 28 through the oil port 1 of the second shuttle valve 31, is connected with the third main oil way 26 through the oil port 3 of the second shuttle valve 31, collects high-pressure oil in the third main oil way 26 and the fourth main oil way 28 in real time, and outputs the high-pressure oil to the oil port 3 of the fourth shuttle valve 33 through the oil port 2 of the second shuttle valve 31, and the high-pressure oil output by the oil port 2 of the fourth shuttle valve 33 is the high-pressure oil in the third main oil way 26 and the fourth main oil way 28 because the oil port 1 pressure of the fourth shuttle valve 33 is 0; the high-pressure oil output from the oil port 2 of the fourth shuttle valve 33 is applied to the port 1 of the fifth shuttle valve 34; the first shuttle valve 30 is connected with the second main oil way 19 through the oil port 1, is connected with the first main oil way 17 through the oil port 3, collects high-pressure oil in the first main oil way 17 and the second main oil way 19 in real time, and outputs the high-pressure oil to the oil port 3 of the fifth shuttle valve 34 through the oil port 2 of the first shuttle valve 30; the high-pressure oil output from the oil port 2 of the fifth shuttle valve 34 is the highest oil pressure in the first/second/third/fourth main oil passages 17, 19, 26, 28; the high-pressure oil output by the oil port 2 of the fifth shuttle valve 34 is respectively connected with the P ports of the first control valve group 13 and the second control valve group 21; so the highest oil pressure in the first/second/third/fourth main oil paths 17, 19, 26, 28 flows through the P port and the a port of the first/second control valve group (i.e. the reversing valve group), and flows through the 1 port and the 2 port of the first/second/third/fourth damping throttle valve 35/36/37/38 respectively to act on the control cavity 3 port of the corresponding first/second/third/fourth cartridge valve 18/20/27/29 respectively; at this time, the first/second/third/fourth cartridge valve 18/20/27/29 is not opened and the system is not operated.
Forward cutting of the chain cutter: in a standby state, the EP valve electromagnets b of the first closed type bidirectional variable plunger pump 14 and the second closed type bidirectional variable plunger pump 22 are electrified, the oil flowing direction of the second power source 23 (engine pump group) is from a third oil pumping port 24 to a fourth oil pumping port 25, the third oil pumping port 24 is a working oil port, the oil flowing direction of the first power source 15 (motor pump group) is from a first oil pumping port 14a to a second oil pumping port 14b, and the first oil pumping port 14a is the working oil port; at this time, the electromagnet of the first control valve group 13 and the electromagnet of the second control valve group 21 are simultaneously powered on, the P is communicated with B, A and the T is communicated, the pressure oil at the 3 ports of the control cavity of the first/second/third/fourth cartridge valve 18/20/27/29 acts on the electromagnet of the first control valve group 13 and the A port and the T port of the second control valve group 21 respectively along the 2 ports and the 1 ports of the first/second/third/fourth damping throttle valve 35/36/37/38, and the pressure of the control cavity of the first/second/third/fourth cartridge valve 18/20/27/29 is 0; the pressure oil of the engine pump set system flows through the third main oil way 26 from the third pump oil port 24 to the 1 port of the third cartridge valve 27, and the pressure oil acting on the oil port 1 of the third cartridge valve 27 pushes the cartridge valve core to move upwards at the moment because the pressure of the 3 port of the control cavity of the third cartridge valve 27 is 0, and the third cartridge valve 27 is opened to enable the 1 port and the 2 port of the third cartridge valve 27 to be communicated; meanwhile, the pressure oil of the motor pump set system flows through the first main oil way 17 from the first pump oil port 14a to the 1 port of the first cartridge valve 18, and because the pressure of the 3 ports of the control cavity of the first cartridge valve 18 is 0, the pressure oil acting on the oil port 1 of the first cartridge valve 18 pushes the valve core of the first cartridge valve 18 to move upwards, and the first cartridge valve 18 is opened to enable the 1 port and the 2 port of the first cartridge valve 18 to be communicated; the first power system (motor pump system) pressure oil flows through the first main oil passage 17 from the first pump oil port 14a, and flows through the 1 st port and the 2 nd port of the first cartridge valve 18, and acts on the first oil port 10a of the hydraulic motor 10 through the first load oil passage 11 to cut the motor in the forward rotation direction, while the second power system (engine pump system) pressure oil flows through the third main oil passage 26 from the third pump oil port 24, flows through the 1 st port and the 2 nd port of the third cartridge valve 27, and acts on the first oil port 10a of the hydraulic motor 10 through the first load oil passage 11 to cut the motor in the forward rotation direction. The system oil return flows through the second load oil way 12 from the second oil port 10b of the hydraulic motor 10 to the 2 port of the second cartridge valve 20, and because the pressure of the 3 port of the controller of the second cartridge valve 20 is 0, the pressure oil acting on the oil port 2 of the second cartridge valve 20 pushes the cartridge valve core to move upwards at the moment, and the second cartridge valve 20 is opened to enable the 2 port and the 1 port of the second cartridge valve 20 to be communicated; the return oil of the motor pump set system flows through the second load oil way 12 from the second oil port 10b of the hydraulic motor 10 to the 2 port and the 1 port of the second cartridge valve 20, and returns to the second pump oil port 14b of the first closed bidirectional variable plunger pump 14, so that the forward rotation cutting work of the chain cutter is completed; meanwhile, the system oil return flows through the second load oil way 12 from the second oil port 10b of the hydraulic motor 10 to the 2 port of the fourth cartridge valve 29, and because the pressure of the 3 port of the controller of the fourth cartridge valve 29 is 0, the pressure oil acting on the oil port 2 of the fourth cartridge valve 29 pushes the cartridge valve core to move upwards at the moment, and the fourth cartridge valve 29 is opened to enable the 2 port and the 1 port of the fourth cartridge valve 29 to be communicated; the return oil of the engine pump set system flows from the second oil port 10b of the hydraulic motor 10 to the 2 ports and the 1 ports of the fourth cartridge valve 29 through the second load oil way 12 and returns to the fourth pump oil port 25 of the second closed bidirectional variable plunger pump 22, so that the forward rotation cutting work of the chain cutter is completed.
Chain cutter reverse cutting: in a standby state, the EP valve electromagnets a of the first closed bidirectional variable plunger pump 14 and the second closed bidirectional variable plunger pump 22 are powered on, the oil flowing direction of the second power source 23 (engine pump group) is from a fourth pump oil port 25 to a third pump oil port 24, the fourth pump oil port 25 is a working oil port, the oil flowing direction of the first power source 15 (motor pump group) is from a second pump oil port 14b to a first pump oil port 14a, and the second pump oil port 14b is a working oil port; at this time, the electromagnet of the first control valve group 13 and the electromagnet of the second control valve group 21 are simultaneously powered on, the P is communicated with B, A and the T is communicated, the pressure oil at the 3 ports of the control cavity of the first/second/third/fourth cartridge valve 18/20/27/29 acts on the electromagnet of the first control valve group 13 and the A port and the T port of the second control valve group 21 respectively along the 2 ports and the 1 ports of the first/second/third/fourth damping throttle valve 35/36/37/38, and the pressure of the control cavity of the first/second/third/fourth cartridge valve 18/20/27/29 is 0;
The pressure oil of the second power source system (engine pump system) flows through the fourth main oil way 28 from the fourth oil pumping port 25 to the 1 port of the fourth cartridge valve 29, and the pressure oil acting on the oil port 1 of the fourth cartridge valve 29 pushes the cartridge valve core to move upwards at the moment because the pressure of the 3 port of the control cavity of the fourth cartridge valve 29 is 0, so that the 1 port and the 2 port of the fourth cartridge valve 29 are communicated; meanwhile, the pressure oil of the first power system (a motor pump set system) flows through the second main oil way 19 from the second oil pumping port 14b to the 1 port of the second cartridge valve 20, and as the pressure of the 3 port of the control cavity of the second cartridge valve 20 is 0, the pressure oil acting on the oil port 1 of the second cartridge valve 20 pushes the valve core of the second cartridge valve to move upwards, and the second cartridge valve 20 is opened to enable the 1 port and the 2 port of the second cartridge valve 20 to be communicated; the engine pump set system pressure oil flows through the fourth main oil passage 28 from the fourth pump oil port 25, and flows through the 1 st port and the 2 nd port of the fourth cartridge valve 29, and acts on the second oil port 10b of the hydraulic motor 10 through the second load oil passage 12 to reversely cut the hydraulic motor, and meanwhile, the motor pump set system pressure oil flows through the second main oil passage 19 from the second pump oil port 14b, flows through the 1 st port and the 2 nd port of the second cartridge valve 20, and acts on the second oil port 10b of the hydraulic motor 10 through the second load oil passage 12 to reversely cut the hydraulic motor. The system oil return flows through the first load oil way 11 from the first oil port 10a of the hydraulic motor 10 to the 2 port of the first cartridge valve 18, and because the pressure of the 3 port of the controller of the first cartridge valve 18 is 0, the pressure oil acting on the oil port 2 of the first cartridge valve 18 pushes the cartridge valve core to move upwards at the moment, and the first cartridge valve 18 is opened to enable the 2 port and the 1 port of the first cartridge valve 18 to be communicated; the return oil of the motor pump set system flows through the first load oil way 11 from the first oil port 10a of the hydraulic motor to the 2 ports and 1 port of the first cartridge valve 18 and returns to the first pump oil port 14a of the first closed bidirectional variable plunger pump 14, so that the chain cutter reverse cutting work is completed; meanwhile, the system oil return flows through the first load oil way 11 from the first oil port of the hydraulic motor 10 to the 2 port of the third cartridge valve 27, and because the pressure of the 3 port of the controller of the third cartridge valve 27 is 0, the pressure oil acting on the oil port 2 of the third cartridge valve 27 pushes the cartridge valve core to move upwards at the moment, and the third cartridge valve 27 is opened to enable the 2 port and the 1 port of the third cartridge valve 27 to be communicated; the return oil of the engine pump set system flows from the first oil port of the hydraulic motor 10 to the 2 ports and the 1 ports of the third cartridge valve 27 through the first load oil way 11 and returns to the third pump oil port 24 of the second closed bidirectional variable plunger pump 22, so that the forward rotation cutting work of the chain cutter is completed.
The continuous wall chain cutter rotary closed hydraulic system and the continuous wall equipment provided by the invention are described in detail. It should be noted that, in the present specification, each embodiment is described in a progressive manner, and each embodiment is mainly described as different from other embodiments, and identical and similar parts between the embodiments are all enough to be referred to each other.
It should also be noted that, in this document, terms such as "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that an article or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such article or apparatus. Without further limitation, an element defined by the phrase "comprising one … …" does not exclude the presence of other like elements in an article or device comprising the element.
The principles and embodiments of the present invention have been described herein with reference to specific examples, the description of which is intended only to facilitate an understanding of the core concepts of the invention. It should be noted that it will be apparent to those skilled in the art that various modifications and adaptations of the invention can be made without departing from the principles of the invention and these modifications and adaptations are intended to be within the scope of the invention as defined in the following claims.

Claims (6)

1. The continuous wall chain cutter rotation closed hydraulic system is characterized by comprising a hydraulic motor (10) for driving a chain wheel and a chain to run, a first load oil circuit (11), a second load oil circuit (12), a first power system and a second power system;
The hydraulic motor (10) comprises a first oil port (10 a) communicated with the first load oil path (11) and a second oil port (10 b) communicated with the second load oil path (12);
The first power system and the second power system are connected in parallel between the first load oil circuit (11) and the second load oil circuit (12);
The first power system comprises a first control valve group (13), a first closed bidirectional variable plunger pump (14) for providing pressure oil for the hydraulic motor (10) and a first power source (15) for driving the first closed bidirectional variable plunger pump (14), wherein the first closed bidirectional variable plunger pump (14) comprises a first pump oil port (14 a), a second pump oil port (14 b) and a first oil suction port for sucking oil in an oil tank (16); the first oil pumping port (14 a) is communicated with the first load oil circuit (11) through a first main oil circuit (17), a first cartridge valve (18) is arranged on the first main oil circuit (17), the second oil pumping port (14 b) is communicated with the second load oil circuit (12) through a second main oil circuit (19), and a second cartridge valve (20) is arranged on the second main oil circuit (19); the first control valve group (13) is used for controlling the opening and closing of the first cartridge valve (18) and the second cartridge valve (20);
The second power system comprises a second control valve group (21), a second closed bidirectional variable plunger pump (22) for providing pressure oil for the hydraulic motor (10) and a second power source (23) for driving the second closed bidirectional variable plunger pump (22), wherein the second closed bidirectional variable plunger pump (22) comprises a third pump oil port (24), a fourth pump oil port (25) and a second oil suction port for sucking oil in an oil tank (16); the third pump oil port (24) is communicated with the first load oil path (11) through a third main oil path (26), a third cartridge valve (27) is arranged on the third main oil path (26), the fourth pump oil port (25) is communicated with the second load oil path (12) through a fourth main oil path (28), and a fourth cartridge valve (29) is arranged on the fourth main oil path (28); the second control valve group (21) is used for controlling the opening and closing of the third cartridge valve (27) and the fourth cartridge valve (29);
The first control valve group (13) and the second control valve group (21) are two-position four-way electromagnetic reversing valves, and the first control valve group (13) and the second control valve group (21) are integrally controlled through a shuttle valve group; the shuttle valve group comprises a first shuttle valve (30) arranged between a first main oil way (17) and a second main oil way (19), a second shuttle valve (31) arranged between a third main oil way (26) and a fourth main oil way (28), a third shuttle valve (32) arranged between a first load oil way (11) and a second load oil way (12), a fourth shuttle valve (33) arranged between an oil pressure outlet of the second shuttle valve (31) and an oil pressure outlet of the third shuttle valve (32) and a fifth shuttle valve (34) arranged between an oil pressure outlet of the fourth shuttle valve (33) and an oil pressure outlet of the first shuttle valve (30), wherein the oil pressure outlet of the fifth shuttle valve (34) is simultaneously connected with a P port of a first control valve group (13) and a P port of a second control valve group (21), and a T port of the first control valve group (13) and a T port of the second control valve group (21) are both communicated with an oil tank (16).
2. The continuous wall chain cutter rotary closed hydraulic system according to claim 1, wherein a first damping throttle valve (35) is arranged between an A port of the first control valve group (13) and a control cavity port of the first cartridge valve (18), a second damping throttle valve (36) is arranged between the A port of the first control valve group (13) and a control cavity port of the second cartridge valve (20), a third damping throttle valve (37) is arranged between the A port of the second control valve group (21) and a control cavity port of the third cartridge valve (27), and a fourth damping throttle valve (38) is arranged between the A port of the second control valve group (21) and a control cavity port of the fourth cartridge valve (29).
3. The continuous wall chain cutter swing closed hydraulic system according to claim 1, wherein the first power source (15) is an electric motor and the second power source (23) is an engine.
4. The continuous wall chain cutter rotary closed hydraulic system according to claim 1, wherein a first closed bidirectional variable plunger pump (14) and the second closed bidirectional variable plunger pump (22) are provided with built-in oil supplementing pumps, and an oil suction port of each built-in oil supplementing pump is communicated with the oil tank (16).
5. The continuous wall chain cutter rotary closed hydraulic system according to claim 1, wherein the first closed bidirectional variable plunger pump (14) and the second closed bidirectional variable plunger pump (22) are hydraulic pump bodies of the rissin brand model code A4VG250EP 4D.
6. A continuous wall apparatus comprising a continuous wall link cutter gyrating closed hydraulic system as defined in any one of claims 1 to 5.
CN202111562646.5A 2021-12-20 2021-12-20 Continuous wall chain cutter rotation closed hydraulic system and continuous wall equipment Active CN114198349B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202111562646.5A CN114198349B (en) 2021-12-20 2021-12-20 Continuous wall chain cutter rotation closed hydraulic system and continuous wall equipment

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202111562646.5A CN114198349B (en) 2021-12-20 2021-12-20 Continuous wall chain cutter rotation closed hydraulic system and continuous wall equipment

Publications (2)

Publication Number Publication Date
CN114198349A CN114198349A (en) 2022-03-18
CN114198349B true CN114198349B (en) 2024-06-14

Family

ID=80655516

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202111562646.5A Active CN114198349B (en) 2021-12-20 2021-12-20 Continuous wall chain cutter rotation closed hydraulic system and continuous wall equipment

Country Status (1)

Country Link
CN (1) CN114198349B (en)

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101503960A (en) * 2009-03-02 2009-08-12 浙江大学 Multi-pump combined driving shield-tunneling blade disc hydraulic system

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102587435B (en) * 2012-03-15 2013-06-19 中国铁建重工集团有限公司 Open hydraulic system for horizontal chain-blade type integral-cutting wall forming equipment
CN103047207B (en) * 2012-12-24 2015-04-29 中联重科股份有限公司 Flow dividing and combining valve bank, hydraulic system, load sensitive hydraulic system and engineering machinery
CN204638113U (en) * 2015-03-13 2015-09-16 辽宁瑞丰专用车制造有限公司 A kind of for fracturing blender truck enclosed pump double-pump confluence system
JP6544643B2 (en) * 2015-10-26 2019-07-17 日立オートモティブシステムズ株式会社 Hydraulic control device and brake system
CN109595224A (en) * 2018-12-25 2019-04-09 中国铁建重工集团有限公司 A kind of construction of diaphragm wall equipment and its double dynamical multi-state hydraulic control system
CN113550943A (en) * 2021-08-12 2021-10-26 中国铁建重工集团股份有限公司 Chain cutter tensioning control system and method of roof cutting pressure relief trolley

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101503960A (en) * 2009-03-02 2009-08-12 浙江大学 Multi-pump combined driving shield-tunneling blade disc hydraulic system

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
OYC98-3型越野叉车行走机构液压传动系统原理及其故障诊断;王荔军;苏欣平;徐传斌;;军事交通学院学报;20171225(第12期);全文 *

Also Published As

Publication number Publication date
CN114198349A (en) 2022-03-18

Similar Documents

Publication Publication Date Title
CN203926203U (en) There is the hydraulic system of afflux performance
CN203892301U (en) Meterless hydraulic system having multi-circuit recuperation
CN103307060B (en) The oil hydraulic cylinder control system of directly driving type servo-pump control electricity liquid combination drive and controlling method
CN100424361C (en) Closed electrohydraulic controlling system
CN203926235U (en) Have many actuators loop without throttling hydraulic system
CN100593646C (en) Unpowered oil supplied direct drive displacement control electrohydraulic servo- closed type oil source system
KR20110031905A (en) Controller of hybrid construction machine
CN101967980B (en) Cutterhead closed type hydraulic drive system adopting revolving speed-variable and displacement-variable compound control
KR20110093934A (en) Hybrid construction machine
WO2013059001A1 (en) Meterless hydraulic system having flow sharing and combining functionality
CN105637233A (en) Control system for hybrid construction machine
CN201010925Y (en) Straight walking mechanism of hydraulic excavator
CN201696054U (en) Closed-type hydraulic driving system with variable-speed variable-displacement combined control of shield cutter head
WO2013058973A1 (en) Meterless hydraulic system having flow sharing and combining functionality
CN114198349B (en) Continuous wall chain cutter rotation closed hydraulic system and continuous wall equipment
CN108953309B (en) Energy recovery and recycling hydraulic system
CN203962530U (en) Have share and combination function without throttling hydraulic system
CN100552218C (en) Multi-purpose hydraulic negative-feedback pump
CN112761648B (en) Shield that possesses self-checking and safe redundancy impels hydraulic system
WO2012113208A1 (en) Power drive device of concrete pumping equipment and concrete pumping equipment
CN106870482A (en) The vibration hydraulic system of cement pavement resonance rock crushing plant
CN108915021B (en) Multi-mode rotary electrohydraulic control system for hydraulic excavator
CN113586532B (en) Construction machine
CN106762928B (en) Automobile hydraulic system and engineering truck with it
CN111288044A (en) Hydraulic system and engineering machinery

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
GR01 Patent grant
GR01 Patent grant