CN116062620A - Auxiliary control hydraulic system of diesel monorail crane locomotive - Google Patents
Auxiliary control hydraulic system of diesel monorail crane locomotive Download PDFInfo
- Publication number
- CN116062620A CN116062620A CN202211728203.3A CN202211728203A CN116062620A CN 116062620 A CN116062620 A CN 116062620A CN 202211728203 A CN202211728203 A CN 202211728203A CN 116062620 A CN116062620 A CN 116062620A
- Authority
- CN
- China
- Prior art keywords
- valve
- control
- hydraulic system
- way
- oil
- 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.)
- Pending
Links
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
- B66C13/00—Other constructional features or details
- B66C13/18—Control systems or devices
-
- 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
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
-
- 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
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
-
- 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
-
- 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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/08—Servomotor systems incorporating electrically operated control means
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Automation & Control Theory (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention relates to the technical field of monorail cranes, in particular to an auxiliary control hydraulic system of a diesel monorail crane locomotive, which mainly comprises a load sensitive control system, a clamping control system, a braking control hydraulic system, a lifting control hydraulic system and an engine starting hydraulic system, wherein the load sensitive control system comprises a load sensitive pump, an oil tank, a main control valve and a first shuttle valve; the clamping control system comprises a first two-position four-way electromagnetic valve and a clamping oil cylinder; the brake control hydraulic system comprises a brake cylinder; the hoisting control hydraulic system comprises a hoisting motor; the engine starting hydraulic system comprises a starting motor, a first one-way valve and an energy accumulator. The auxiliary control hydraulic system of the diesel monorail crane locomotive is energy-saving, efficient, labor-saving and labor-saving, is easy to automatically control, can effectively improve the efficiency of auxiliary transportation, and reduces the labor cost.
Description
Technical Field
The invention relates to the technical field of monorail cranes, in particular to an auxiliary control hydraulic system of a diesel monorail crane vehicle.
Background
Along with the continuous development of the coal industry, each large coal mine company is accelerating the construction of a modern mine with safety, high efficiency and high yield. The modernization degree of auxiliary transportation is an important index for measuring the modernization level of a coal mine, and meanwhile, the efficiency of auxiliary transportation directly influences the production efficiency of the coal mine. The monorail crane locomotive is used as key equipment in an auxiliary transportation system and plays an important role in the construction of a modern auxiliary transportation system. The auxiliary hydraulic system of the existing diesel monorail crane adopts a control mode of a gear pump and a relief valve to control each execution action, so that unnecessary energy loss is caused; most of the auxiliary control hydraulic systems are manually operated, and the working efficiency is low, so that the auxiliary control hydraulic system of the monorail crane, which is energy-saving, efficient, labor-saving and easy to automatically control, is researched, the auxiliary transportation efficiency can be better improved, and the labor cost is reduced.
Disclosure of Invention
In order to solve the technical problems, the invention provides an auxiliary control hydraulic system of a diesel engine monorail crane with high efficiency, energy conservation and higher automation degree, which comprises the following technical scheme:
an auxiliary control hydraulic system of a diesel monorail crane comprises a load sensitive control system, a clamping control system, a braking control hydraulic system, a lifting control hydraulic system and an engine starting hydraulic system;
the load-sensitive control system comprises a load-sensitive pump, an oil tank, a main control valve and a first shuttle valve; the load-sensitive pump is connected with the oil tank through a hydraulic pipeline, an X port of the load-sensitive pump is connected with the X1 port and the X2 port of the main control valve through a first shuttle valve, and an oil outlet of the load-sensitive pump is connected with an oil inlet of the main control valve;
the clamping control system comprises a first two-position four-way electromagnetic valve and a clamping oil cylinder; the clamping oil cylinder is connected with the main control valve through a first two-position four-way electromagnetic valve;
the brake control hydraulic system comprises a brake cylinder; the oil outlet of the main control valve is connected with the small cavity of the brake oil cylinder through a pipeline;
the hoisting control hydraulic system comprises a hoisting motor; the hanging motor is connected with the main control valve;
the engine starting hydraulic system comprises a starting motor, a first one-way valve and an energy accumulator; the starting motor and the energy accumulator are connected with an oil outlet of the main control valve, the starting motor is communicated with the energy accumulator, and the first one-way valve is connected with the starting motor in parallel through a pipeline.
Further, the load sensitive pump comprises a variable plunger pump, a reset cylinder, a control variable cylinder, a flow control valve and a pressure control valve.
Further, the main control valve comprises a three-position four-way electromagnetic valve, a first overflow valve, a sequence valve, a first two-position two-way manual switching valve, a first hydraulic control one-way valve, a second two-position four-way electromagnetic valve, a second one-way valve and a third two-position four-way electromagnetic valve.
Furthermore, the clamping oil cylinder is controlled by the clamping control valve in the clamping control system, an oil inlet of the clamping control valve is connected with the main control valve, and an oil outlet of the clamping control valve is connected with the first two-position four-way electromagnetic valve.
Further, the clamping control valve comprises a second two-position two-way manual switching valve, a second hydraulic control one-way valve, a first two-position three-way electromagnetic valve, a two-position two-way hydraulic control reversing valve and a pressure reducing valve.
Further, the brake control hydraulic system also comprises a switching valve and a gas-liquid pump, wherein an oil inlet of the gas-liquid pump is connected with the oil tank through a pipeline, an oil outlet of the gas-liquid pump is connected with the main control valve through the switching valve, and an oil outlet at the left position of the gas-liquid pump is connected with a small cavity of the brake oil cylinder.
Furthermore, the lifting motor is precisely controlled by the manual electric control reversing valve in the lifting control hydraulic system, an oil inlet of the manual electric control reversing valve is connected with the main control valve, and an oil outlet of the manual electric control reversing valve is connected with an oil inlet of the lifting motor.
Furthermore, the starting motor and the energy accumulator are precisely controlled through the starting valve group and the energy accumulator control valve in the engine starting hydraulic system, the starting valve group and the energy accumulator control valve are connected with the oil outlet of the main control valve, the oil outlet of the starting valve group is connected with the oil inlet of the starting motor, the energy accumulator control valve is connected with the energy accumulator pipeline, and the starting motor is communicated with the energy accumulator through the starting valve group and the energy accumulator control valve.
Further, the starting valve group comprises a second shuttle valve, a third two-position two-way manual switching valve, a second two-position three-way electromagnetic valve and a third hydraulic control one-way valve.
Further, the energy accumulator control valve comprises a second overflow valve, a third two-position three-way electromagnetic valve, a fourth hydraulic control one-way valve and a fourth two-position two-way manual switching valve.
Furthermore, the engine starting hydraulic system further comprises a switching valve and a gas-liquid pump, wherein an oil inlet of the gas-liquid pump is connected with the oil tank through a pipeline, an oil outlet of the gas-liquid pump is connected with the main control valve through the switching valve, and is connected with the energy accumulator through an internal oil way and an external pipeline of the main control valve.
Further, the energy accumulator is connected with a pressure gauge.
Further, the hydraulic system also comprises an engine ECU, a controller and an operating device; the engine ECU and the operating device are electrically connected with a controller, and the controller is electrically connected with an electric element.
The auxiliary control hydraulic system of the diesel monorail crane locomotive is energy-saving, efficient, labor-saving and labor-saving, is easy to automatically control, can effectively improve the efficiency of auxiliary transportation, and reduces the labor cost.
Drawings
FIG. 1 is a schematic diagram of an auxiliary control hydraulic system of a monorail crane;
FIG. 2 is a schematic diagram of a load-sensitive control system for a monorail crane in accordance with the present invention;
FIG. 3 is a schematic diagram of a clamping control system for a monorail crane in accordance with the present invention;
FIG. 4 is a schematic diagram of a brake control hydraulic system of the monorail crane of the present invention;
FIG. 5 is a schematic diagram of a hoist control hydraulic system of the monorail crane of the present invention;
FIG. 6 is a schematic diagram of an engine starting hydraulic system of the monorail crane locomotive of the present invention;
Detailed Description
The present invention will be described in detail with reference to the accompanying drawings. The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention. It should be noted that these drawings and the written description are not intended to limit the scope of the inventive concept in any way, but to illustrate the concept of the present patent to those skilled in the art by referring to the specific embodiments.
As shown in fig. 1, the auxiliary control hydraulic system of the diesel monorail crane locomotive comprises a load sensitive control system, a clamping control system, a braking control hydraulic system, a lifting control hydraulic system and an engine starting hydraulic system.
As shown in fig. 2, the load-sensitive control system includes a load-sensitive pump 1, a tank 5, a main control valve 8, and a first shuttle valve 42; the load-sensitive pump 1 is connected with the oil tank 5 through a hydraulic pipeline, the port X of the load-sensitive pump 1 is connected with the ports X1 and X2 of the main control valve 8 through the first shuttle valve 42, and meanwhile, the oil outlet of the load-sensitive pump 1 is connected with the oil inlet of the main control valve 8. The load sensitive pump 1 comprises a variable plunger pump 2, a reset cylinder 3, a control variable cylinder 4, a flow control valve 46 and a pressure control valve 47; the main control valve 8 comprises a three-position four-way electromagnetic valve 9, a first overflow valve 10, a sequence valve 11, a first two-position two-way manual switching valve 15, a first hydraulic control one-way valve 16, a second two-position four-way electromagnetic valve 17, a second one-way valve 18 and a third two-position four-way electromagnetic valve 19; the components are connected through a hydraulic pipeline or an oil way inside the valve block.
The working process of the load sensitive control system comprises the following steps: through the switching-over of three-position four-way solenoid valve 9 in main control valve 8, the monorail crane can realize the switching over of walking and hoisting two kinds of states, when the locomotive work is in the walking state, variable plunger pump 2 is exported with maximum discharge capacity under the effect of reset cylinder 3, when hydraulic oil flows through the right side of three-position four-way solenoid valve 9 in main control valve 8 and the inside oil circuit in main control valve 8, get into brake cylinder 14, clamping cylinder 27, in energy storage 39, in order to accomplish locomotive drive wheel clamping, the action such as energy storage ware fills pressure, brake cylinder release, load pressure is through the X1 mouth of main control valve 8, first shuttle valve 42, load sensitive pump 1's X mouth, feedback to the spring chamber of flow control valve 46, make variable plunger pump 2's output pressure build gradually, when pressure reaches pressure control valve 47's settlement pressure, variable plunger pump 2's output fluid can get into control variable cylinder 4 through pressure control valve 47, variable plunger pump 2's discharge capacity can reduce near to zero under control variable cylinder 4's effect at this moment, the power consumption when the monorail crane output state is greatly reduced. When the locomotive works in a hoisting state, the variable plunger pump 2 still outputs with maximum displacement under the action of the reset cylinder 3, at the moment, hydraulic oil flows through the left position of the three-position four-way electromagnetic valve 9 in the main control valve 8 and an internal oil way in the main control valve 8, finally enters a hoisting system, hoisting is executed, at the moment, load pressure is fed back to a spring cavity of the flow control valve 46 through an X2 port of the main control valve 8, the first shuttle valve 42 and an X port of the load sensitive pump 1, so that the output pressure of the variable plunger pump 2 is gradually built, and the pressure is always smaller than the set pressure of the pressure control valve 47, and therefore the variable plunger pump 2 continuously works in a large displacement state with system pressure to finish hoisting.
As shown in fig. 3, the clamping control system includes a first two-position four-way solenoid valve 26 and a clamping cylinder 27. The clamping control system is connected with the load sensitive control system, the clamping oil cylinder 27 is connected with the main control valve 8 of the load sensitive control system through the first two-position four-way electromagnetic valve 26, the clamping oil cylinder 27 is precisely controlled in the clamping control system through the clamping control valve 20, the oil inlet of the clamping control valve 20 is connected with the main control valve 8, and the oil outlet of the clamping control valve is connected with the first two-position four-way electromagnetic valve 26. The clamping control valve 20 comprises a second two-position two-way manual switching valve 21, a second hydraulic control one-way valve 22, a first two-position three-way electromagnetic valve 23, a two-position two-way hydraulic control reversing valve 24 and a pressure reducing valve 25. The engine ECU43 and the operating device 45 are connected to the controller 44 via electric wires, and the controller 44 is connected to the first two-position four-way solenoid valve 26 and the first two-position three-way solenoid valve 23 via electric wires.
The working process of the clamping control system comprises the following steps: when the locomotive is running, the operation device 45 is required to send an instruction to the controller 44, and then the three-position four-way electromagnetic valve 9 in the main control valve 8 is controlled to act so as to work at the right position. At this time, the load pressure is fed back to the spring cavity of the flow control valve 46 through the port X1 of the main control valve 8, the first shuttle valve 42 and the port X of the load sensitive pump 1, so that the output pressure of the variable plunger pump 2 is gradually established, and when the piston rod of the clamping cylinder 27 is completely retracted, the system pressure gradually rises to the set pressure of the pressure control valve 47, and at this time, the variable plunger pump 2 works in a high-pressure small-flow state, so that the driving wheel is kept clamped on the track all the time. In the clamping control hydraulic system, a controller 44 receives parameter signals such as engine rotating speed and the like sent by a transceiver ECU43, when the engine is detected to be in a starting state, the controller 44 sends a command to a first two-position three-way electromagnetic valve 23 to enable the first two-position three-way electromagnetic valve 23 to work at a left position, at the moment, hydraulic oil flows through the first two-position three-way electromagnetic valve 23 to open a second hydraulic control one-way valve 22, so that the hydraulic oil flows from a P port of a clamping control valve 20 to an A port through the second hydraulic control one-way valve 22, a two-position two-way hydraulic control reversing valve 24 and a pressure reducing valve 25, and then enters a small cavity of a clamping oil cylinder 27 through a first two-position four-way electromagnetic valve 26 to complete clamping action; when the engine is detected to be in a stop state, the controller 44 sends an instruction to the first two-position three-way electromagnetic valve 23, so that the first two-position three-way electromagnetic valve 23 works at the right position, and at the moment, the second hydraulic control one-way valve 22 is closed, so that hydraulic oil in a small cavity of the clamping oil cylinder cannot be lost, the driving wheel is in a clamping pressure maintaining state, and the phenomenon of slipping when the locomotive walks again is prevented. If the locomotive is not suitable for a long time, the second two-position two-way manual switching valve 21 can be operated to work at the right position, so that the clamping pressure of the driving wheel is released, and the service life of the locomotive is prolonged. The control signal is input to the controller 44 through the operation device 45, and after being processed by the controller 44, the control signal is sent to the first two-position four-way electromagnetic valve 26, so that the first two-position four-way electromagnetic valve 26 works at the left position, and at the moment, pressure oil enters the large cavity of the clamping oil cylinder 27, so that the piston rod extends out of the driving wheel to separate from the track, and free selection of driving quantity and layout can be realized.
As shown in fig. 4, the brake control hydraulic system comprises a brake oil cylinder 14, the brake control hydraulic system is connected with the load sensitive control system, and a small cavity of the brake oil cylinder 14 is connected with an oil outlet of the main control valve 8.
During the working process of the brake control hydraulic system, when the locomotive walks, hydraulic oil needs to be input into the small cavity of the brake oil cylinder 14, at the moment, the operating device 45 sends an instruction to the controller 44, so as to control the three-position four-way electromagnetic valve 9 to work at the right position, the second two-position four-way electromagnetic valve 17 to work at the left position and the third two-position four-way electromagnetic valve 19 to work at the left position. At this time, the variable plunger pump 2 outputs high-pressure oil to flow through the three-position four-way electromagnetic valve 9, the first hydraulic control one-way valve 16, the second two-position four-way electromagnetic valve 17, the third two-position four-way electromagnetic valve 19 and the first two-position two-way manual switching valve 15 in the main control valve 8 to enter the small cavity of the brake cylinder 14, at this time, the load pressure is fed back to the spring cavity of the flow control valve 46, so that the output pressure of the variable plunger pump 2 is gradually built up, when the piston rod of the brake cylinder 14 is retracted, the brake block is separated from the track, the system pressure is gradually increased to the pressure set by the pressure control valve 47, at this time, the variable plunger pump 2 works in a high-pressure small-flow state, and the brake release state is maintained. When the locomotive can not be started and needs the trailer, the gas-liquid pump 7 is connected with the underground gas source to complete the conversion of gas-liquid energy, the pressure oil discharged by the gas-liquid pump 7 enters the small cavity of the brake cylinder 14 through the left position of the switching valve 6, the piston rod is retracted to realize the release of braking, and the first two-position two-way manual switching valve 15 is required to be operated to work at the left position closing position at the moment, so that the pressure oil discharged by the gas-liquid pump 7 is prevented from leaking from the left position. An oil inlet of the gas-liquid pump 7 is connected with the oil tank 5 through a pipeline, an oil outlet of the gas-liquid pump 7 is connected with the main control valve 8 through the switching valve 6, and a left oil outlet of the gas-liquid pump is connected with a small cavity of the brake oil cylinder 14.
As shown in fig. 5, the hoist control hydraulic system includes a hoist motor 13, the hoist control hydraulic system is connected with the load sensitive control system, and the hoist motor 13 is connected with the main control valve 8. In the hoisting control hydraulic system, a hoisting motor 13 is precisely controlled through a manual electric control reversing valve 12, an oil inlet of the manual electric control reversing valve 12 is connected with a main control valve 8, and an oil outlet of the manual electric control reversing valve is connected with an oil inlet of the hoisting motor 13.
The working process of the lifting control hydraulic system comprises the following steps: when the locomotive performs lifting operation, the operating device 45 sends a command to the controller 44, so as to control the three-position four-way electromagnetic valve 9 to work at the left position, at this time, the load pressure is fed back to the spring cavity of the flow control valve 46 through the X2 port of the main control valve 8, the first shuttle valve 42 and the X port of the load sensitive pump 1, so that the output pressure of the variable plunger pump 2 is gradually built up, and the pressure is always smaller than the set pressure of the pressure control valve 47, so that the variable plunger pump 2 continuously outputs a large flow through the three-position four-way electromagnetic valve 9 and the manual electric control reversing valve 12 in the main control valve 8 at the system pressure, acts on the lifting motor 13, and the lifting operation is completed. In the hoisting control hydraulic system, the manual electric control reversing valve 12 has two control modes of manual control and electric control, so that the labor intensity of workers can be effectively reduced, and the working efficiency is improved. Meanwhile, in the lifting control hydraulic system, when lifting operation is carried out, the X2 port output control oil of the main control valve 8 acts on the two-position two-way hydraulic control reversing valve 24 to enable the two-position two-way hydraulic control reversing valve to work in a left-position closed state, at the moment, the pressure oil in the small cavity of the clamping oil cylinder 27 cannot leak, and the driving wheel is always clamped on the track so as to be convenient for quickly establishing the clamping pressure when the locomotive walks again.
As shown in fig. 6, the engine starting hydraulic system includes a starting motor 28, a first check valve 29, an accumulator 39; the engine starting hydraulic system is connected with the load sensitive control system, the starting motor 28 and the accumulator 39 are connected with the oil outlet of the main control valve 8, the starting motor 28 is communicated with the accumulator 39, and the first one-way valve 29 is connected with the starting motor 28 in parallel through a pipeline. In the engine starting hydraulic system, a starting motor 28 and an accumulator 39 are precisely controlled through a starting valve group 34 and an accumulator control valve 35, the starting valve group 34 and the accumulator control valve 35 are connected with an oil outlet of a main control valve 8, an oil outlet of the starting valve group 34 is connected with an oil inlet of the starting motor 28, the accumulator control valve 35 is connected with the accumulator 39 through a pipeline, and the starting motor 28 is communicated with the accumulator 39 through the starting valve group 34 and the accumulator control valve 35. The starting valve group 34 comprises a second shuttle valve 30, a third two-position two-way manual switching valve 31, a second two-position three-way electromagnetic valve 32 and a third hydraulic control one-way valve 33; the accumulator control valve 35 comprises a second relief valve 37, a third two-position three-way solenoid valve 38, a fourth pilot operated check valve 40, and a fourth two-position two-way manual switching valve 41.
The working process of the engine starting hydraulic system comprises the following steps: the monorail locomotive is started by supplying oil to the starting motor 28 through the accumulator 39, and the starting motor 28 acts to start the engine. When the locomotive runs, the load sensitive pump 1 outputs in a high-pressure low-flow state, at the moment, the engine ECU43 detects that the engine is in a starting state, and sends out an instruction to the controller 44, so as to control the third two-position three-way electromagnetic valve 38 to work in the left position, at the moment, high-pressure oil output by the load sensitive pump 1 enters the accumulator 39 through the main control valve 8 and the accumulator control valve 35, the pressure finally reaches the set pressure of the pressure control valve 47 in the load sensitive pump 1, and at the moment, the pressure of hydraulic oil in the accumulator 39 can be read out from the pressure gauge 36. When the engine stops working, the engine ECU43 detects that the engine is in a starting state, and sends a command to the controller 44 to control the third two-position three-way electromagnetic valve 38 to work in the right position, and at the moment, the pressure oil is sealed in the accumulator 39 under the action of the fourth hydraulic control one-way valve 40 so as to start the engine again. When the locomotive is started for the first time or the pressure of the accumulator is released for some reason, hydraulic oil needs to be pumped out through the underground air source connected with the air pump 7, and enters the accumulator 39 through the switching valve, an internal oil way in the main control valve 8 and the right position of the fourth two-position two-way manual switching valve 41 in the accumulator control valve 35, and when the pressure gauge 36 displays that the pressure reaches the pressure required for starting the locomotive, the locomotive can be started. When the pressure in the accumulator 39 reaches the pressure required for starting the locomotive, an instruction is sent to the controller 44 through the operating device 45, so that the second two-position three-way electromagnetic valve 32 is controlled to work at the left position, and the third two-position three-way electromagnetic valve 38 is controlled to work at the left position; at this time, the pressure oil in the accumulator 39 enters the starting motor 28 through the fourth hydraulic control one-way valve 40, the third hydraulic control one-way valve 33 and the second shuttle valve 30, so as to start the engine; after the engine is started, an instruction is sent to the controller 44 through the operating device 45, so that the second two-position three-way electromagnetic valve 32 is controlled to work at the right position, the pressure loss in the accumulator 39 is prevented, meanwhile, oil can be replenished from the oil tank 5 to the inlet of the starting motor 28 through the first one-way valve 29 when the starting motor is driven by the engine flywheel, and the dry grinding damage of the starting motor 28 is prevented. Meanwhile, when the second two-position three-way electromagnetic valve 32 and the third two-position three-way electromagnetic valve 38 fail, the manual starting of the engine can be realized by manually operating the fourth two-position two-way manual switching valve 41 and the third two-position two-way manual switching valve 31.
Claims (13)
1. The utility model provides a diesel engine monorail crane locomotive auxiliary control hydraulic system, includes load sensitive control system, clamping control system, braking control hydraulic system, lifts by crane control hydraulic system and engine start hydraulic system, its characterized in that:
the load-sensitive control system comprises a load-sensitive pump (1), an oil tank (5), a main control valve (8) and a first shuttle valve (42); the load-sensitive pump (1) is connected with the oil tank (5) through a hydraulic pipeline, an X port of the load-sensitive pump (1) is connected with the X1 and X2 ports of the main control valve (8) through a first shuttle valve (42), and an oil outlet of the load-sensitive pump (1) is connected with an oil inlet of the main control valve (8);
the clamping control system comprises a first two-position four-way electromagnetic valve (26) and a clamping oil cylinder (27); the clamping oil cylinder (27) is connected with the main control valve (8) through a first two-position four-way electromagnetic valve (26);
the brake control hydraulic system includes a brake cylinder (14); an oil outlet of the main control valve (8) is connected with a small cavity of the brake oil cylinder (14) through a pipeline;
the hoisting control hydraulic system comprises a hoisting motor (13); the hanging motor (13) is connected with the main control valve (8);
the engine starting hydraulic system comprises a starting motor (28), a first one-way valve (29) and an energy accumulator (39); the starting motor (28) and the energy accumulator (39) are connected with an oil outlet of the main control valve (8), the starting motor (28) is communicated with the energy accumulator (39), and the first one-way valve (29) is connected with the starting motor (28) in parallel through a pipeline.
2. The auxiliary control hydraulic system of a diesel monorail crane vehicle according to claim 1, wherein: the load-sensitive pump (1) comprises a variable plunger pump (2), a reset cylinder (3), a control variable cylinder (4), a flow control valve (46) and a pressure control valve (47).
3. The auxiliary control hydraulic system of a diesel monorail crane vehicle according to claim 1, wherein: the main control valve (8) comprises a three-position four-way electromagnetic valve (9), a first overflow valve (10), a sequence valve (11), a first two-position two-way manual switching valve (15), a first hydraulic control one-way valve (16), a second two-position four-way electromagnetic valve (17), a second one-way valve (18) and a third two-position four-way electromagnetic valve (19).
4. The auxiliary control hydraulic system of a diesel monorail crane vehicle according to claim 1, wherein: the clamping control system is characterized in that a clamping oil cylinder (27) is controlled through a clamping control valve (20), an oil inlet of the clamping control valve (20) is connected with a main control valve (8), and an oil outlet of the clamping control valve is connected with a first two-position four-way electromagnetic valve (26).
5. The auxiliary control hydraulic system of the diesel monorail crane locomotive as claimed in claim 4, wherein: the clamping control valve (20) comprises a second two-position two-way manual switching valve (21), a second hydraulic control one-way valve (22), a first two-position three-way electromagnetic valve (23), a two-position two-way hydraulic control reversing valve (24) and a pressure reducing valve (25).
6. The auxiliary control hydraulic system of a diesel monorail crane vehicle according to claim 1, wherein: the brake control hydraulic system further comprises a switching valve (6) and a gas-liquid pump (7), an oil inlet of the gas-liquid pump (7) is connected with the oil tank (5) through a pipeline, an oil outlet of the gas-liquid pump (7) is connected with the main control valve (8) through the switching valve (6), and a left oil outlet of the gas-liquid pump is connected with a small cavity of the brake oil cylinder (14).
7. The auxiliary control hydraulic system of a diesel monorail crane vehicle according to claim 1, wherein: the lifting motor (13) is precisely controlled through a manual electric control reversing valve (12) in the lifting control hydraulic system, an oil inlet of the manual electric control reversing valve (12) is connected with the main control valve (8), and an oil outlet of the manual electric control reversing valve is connected with an oil inlet of the lifting motor (13).
8. The auxiliary control hydraulic system of a diesel monorail crane vehicle according to claim 1, wherein: the engine starting hydraulic system is characterized in that a starting motor (28) and an energy accumulator (39) are precisely controlled through a starting valve bank (34) and an energy accumulator control valve (35), the starting valve bank (34) and the energy accumulator control valve (35) are connected with an oil outlet of a main control valve (8), the oil outlet of the starting valve bank (34) is connected with an oil inlet of the starting motor (28), the energy accumulator control valve (35) is connected with an energy accumulator (39) through a pipeline, and the starting motor (28) is communicated with the energy accumulator (39) through the starting valve bank (34) and the energy accumulator control valve (35).
9. The auxiliary control hydraulic system of a diesel monorail crane vehicle of claim 8, wherein: the starting valve group (34) comprises a second shuttle valve (30), a third two-position two-way manual switching valve (31), a second two-position three-way electromagnetic valve (32) and a third hydraulic control one-way valve (33).
10. The auxiliary control hydraulic system of a diesel monorail crane vehicle of claim 8, wherein: the energy accumulator control valve (35) comprises a second overflow valve (37), a third two-position three-way electromagnetic valve (38), a fourth hydraulic control one-way valve (40) and a fourth two-position two-way manual switching valve (41).
11. The auxiliary control hydraulic system of a diesel monorail crane vehicle according to claim 1, wherein: the engine starting hydraulic system further comprises a switching valve (6) and a gas-liquid pump (7), an oil inlet of the gas-liquid pump (7) is connected with the oil tank (5) through a pipeline, an oil outlet of the gas-liquid pump (7) is connected with a main control valve (8) through the switching valve (6), and an internal oil way and an external pipeline of the main control valve (8) are connected with an energy accumulator (39).
12. A diesel monorail crane locomotive auxiliary control hydraulic system according to any one of claims 1 to 11, wherein: the accumulator (39) is connected with the pressure gauge (36).
13. A diesel monorail crane locomotive auxiliary control hydraulic system according to any one of claims 1 to 11, wherein: the engine ECU (43), the controller (44) and the operating device (45) are also included; the engine ECU (43) and the operating device (45) are electrically connected with a controller (44), and the controller (44) is electrically connected with the electrical components of the hydraulic system.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211728203.3A CN116062620A (en) | 2022-12-29 | 2022-12-29 | Auxiliary control hydraulic system of diesel monorail crane locomotive |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211728203.3A CN116062620A (en) | 2022-12-29 | 2022-12-29 | Auxiliary control hydraulic system of diesel monorail crane locomotive |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN116062620A true CN116062620A (en) | 2023-05-05 |
Family
ID=86179599
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202211728203.3A Pending CN116062620A (en) | 2022-12-29 | 2022-12-29 | Auxiliary control hydraulic system of diesel monorail crane locomotive |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN116062620A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116677676A (en) * | 2023-06-26 | 2023-09-01 | 中国矿业大学 | Release control system and method for braking recovery energy of diesel engine monorail crane |
| CN116768063A (en) * | 2023-06-12 | 2023-09-19 | 徐州徐工能源装备有限公司 | Automatic increasing and decreasing driving control system and control method for monorail crane |
| CN116902018A (en) * | 2023-06-26 | 2023-10-20 | 中国矿业大学 | Diesel engine monorail crane braking energy recovery system and control method |
| CN118811700B (en) * | 2024-09-20 | 2024-11-15 | 云南星石科技有限公司 | Diesel engine monorail crane and control system thereof |
-
2022
- 2022-12-29 CN CN202211728203.3A patent/CN116062620A/en active Pending
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116768063A (en) * | 2023-06-12 | 2023-09-19 | 徐州徐工能源装备有限公司 | Automatic increasing and decreasing driving control system and control method for monorail crane |
| CN116768063B (en) * | 2023-06-12 | 2024-01-02 | 徐州徐工能源装备有限公司 | Automatic increasing and decreasing driving control system and control method for monorail crane |
| CN116677676A (en) * | 2023-06-26 | 2023-09-01 | 中国矿业大学 | Release control system and method for braking recovery energy of diesel engine monorail crane |
| CN116902018A (en) * | 2023-06-26 | 2023-10-20 | 中国矿业大学 | Diesel engine monorail crane braking energy recovery system and control method |
| CN118811700B (en) * | 2024-09-20 | 2024-11-15 | 云南星石科技有限公司 | Diesel engine monorail crane and control system thereof |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102587444B (en) | Oil hybrid system for excavator with energy differential recovery | |
| CN116062620A (en) | Auxiliary control hydraulic system of diesel monorail crane locomotive | |
| CN202081450U (en) | Potential energy differential recovery system for moving arm of oil-liquid hybrid power excavator | |
| CN101704336B (en) | Energy-saving hydraulic hybrid power system of loader | |
| CN102134047B (en) | Energy-saving hydraulic system of electric forklift | |
| CN109080454B (en) | Electrohydraulic driving system for reducing motor power | |
| CN103950870B (en) | A kind of forklift hydraulic system of double pump fuel feeding band energy regenerating | |
| CN102616705B (en) | Energy-saving forklift hydraulic system with energy recovery function | |
| CN109139583B (en) | Hydraulic control system for forklift | |
| CN103161190A (en) | Hybrid power full hydraulic loading machine hydraulic system based on pressure common rail system | |
| CN113183736B (en) | Electro-hydraulic hybrid power system for loader oil and control method thereof | |
| CN107524187B (en) | Hydraulic-electric hybrid recycling system for braking energy of rotary motion | |
| CN102616700B (en) | Oil and air hybrid driven lifting control device | |
| CN202542790U (en) | Energy-saving forklift hydraulic system with energy recycling | |
| CN203890013U (en) | Double-pump oil supply and energy recovery type forklift hydraulic system | |
| CN203604282U (en) | Braking, steering, lifting main control hydraulic integrated block of heavy loading truck | |
| CN219060177U (en) | Hydraulic energy-saving system for excavator | |
| CN201962039U (en) | Energy-saving hydraulic system of electronic forklift | |
| CN204628110U (en) | A kind of car lift deceleration pressure dwelling loop | |
| CN115402928A (en) | Diesel engine monorail crane locomotive driving clamping automatic control system | |
| CN114873461A (en) | Hydraulic control system for lifting beam of monorail crane and working method of hydraulic control system | |
| CN110894731B (en) | Working device buffer system and engineering equipment | |
| CN210193224U (en) | Shore bridge tilting-hanging integrated electro-hydraulic control system | |
| CN108591189B (en) | Variable-parameter energy accumulator control system and movable arm energy-saving hydraulic system | |
| CN103114624A (en) | Load-sensitive operation system of loading machine |
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 |