CN110030217B - Control system of floating oil cylinder of chassis of overhead working truck and overhead working truck - Google Patents
Control system of floating oil cylinder of chassis of overhead working truck and overhead working truck Download PDFInfo
- Publication number
- CN110030217B CN110030217B CN201910283786.5A CN201910283786A CN110030217B CN 110030217 B CN110030217 B CN 110030217B CN 201910283786 A CN201910283786 A CN 201910283786A CN 110030217 B CN110030217 B CN 110030217B
- Authority
- CN
- China
- Prior art keywords
- oil
- port
- valve
- working
- cylinder
- 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
Links
- 239000003921 oil Substances 0.000 claims description 406
- 239000012530 fluid Substances 0.000 claims description 22
- 239000010720 hydraulic oil Substances 0.000 claims description 7
- 238000000034 method Methods 0.000 abstract description 9
- 230000008569 process Effects 0.000 abstract description 9
- 238000005265 energy consumption Methods 0.000 abstract description 6
- 230000004044 response Effects 0.000 abstract description 6
- 230000009471 action Effects 0.000 description 8
- 238000010586 diagram Methods 0.000 description 5
- 238000006073 displacement reaction Methods 0.000 description 4
- 230000007246 mechanism Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 230000005611 electricity Effects 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000035939 shock Effects 0.000 description 2
- 238000006467 substitution reaction Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000011900 installation process Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 230000035945 sensitivity Effects 0.000 description 1
- 230000000087 stabilizing effect Effects 0.000 description 1
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
- B66F11/00—Lifting devices specially adapted for particular uses not otherwise provided for
- B66F11/04—Lifting devices specially adapted for particular uses not otherwise provided for for movable platforms or cabins, e.g. on vehicles, permitting workmen to place themselves in any desired position for carrying out required operations
- B66F11/044—Working platforms suspended from booms
-
- 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
- F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
-
- 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
- F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
-
- 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
- F15B21/087—Control strategy, e.g. with block diagram
-
- 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
- F15B2211/60—Circuit components or control therefor
- F15B2211/65—Methods of control of the load sensing pressure
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Structural Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Life Sciences & Earth Sciences (AREA)
- Geology (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The application discloses a control system of a floating oil cylinder of an underframe of an overhead working truck and the overhead working truck, wherein the control system comprises a variable pump, a control valve group for controlling a main arm and a balance valve group for controlling the floating oil cylinder, the variable pump is provided with an output oil port P and a first load feedback oil port LS, the output oil port P is connected with the control valve group and the balance valve group, the output oil port P and the control valve group are connected with the first load feedback oil port LS through an oil pump control valve block, and the overhead working truck is provided with the control system. According to the control system and the overhead working truck, the oil pump control valve block is added, when the overhead working truck walks, the variable pump is in a constant pressure control state, the quick response of the floating oil cylinder of the underframe is ensured, meanwhile, when the arm support acts, the oil pressure state of the control valve block is fed back through the oil pump control valve block, so that the variable pump processes load sensitive control, the energy consumption and starting impact of the system are reduced, and the stability and the safety are high.
Description
Technical Field
The application belongs to the technical field of overhead working equipment, and particularly relates to a control system of an underframe floating oil cylinder of an overhead working truck and the overhead working truck applying the control system.
Background
In order to improve the walking stability of the whole vehicle and the passing ability under different road conditions, the existing overhead working truck adopts a structure mode that a front axle 500 floats and a rear axle 600 swings. See fig. 1 and 2 for specific structure: the front axle 500 has a floating cylinder on the left and right sides, and under the combined action of the floating cylinders, the front axle 500 can swing up and down around a swing axis, and the rear axle 600 also adopts a swing structure. During the walking process, the rear axle 600 swings along with the ground, and the floating oil cylinders of the front axle 500 are controlled to stretch out and draw back through the floating valves 103 structurally related to the rear axle, so that the active floating function of the whole vehicle during the walking process is realized.
In the whole vehicle walking process, emergency situations are unavoidable, for example, tires on one side of the front axle 500 suddenly drop into a pit, and at the moment, if the connected floating oil cylinders cannot extend out quickly, the center of gravity of the whole vehicle can be changed instantaneously, the stability of the whole vehicle is seriously influenced, and even the risk of tipping occurs, so that the personal safety of operators is endangered. Therefore, the working condition has high requirements on the quick response of the floating oil cylinder.
In order to solve the above problems, the existing hydraulic control system adopts a constant pressure pump control mode, and the technical scheme is shown in fig. 3-6: in the figure, an output oil port P of a variable pump 100 is connected with a first oil inlet P of a control valve bank 106, a second oil inlet P of a pressure reducing flow valve 102 and a first oil inlet P1 of a loading electromagnetic valve 101 at the same time, a first load feedback oil port LS of the variable pump 100 is connected with a first working oil port a of the loading electromagnetic valve 101, an output oil port P1 of the pressure reducing flow valve 102 is connected with a third oil inlet P of a floating valve 103, a second working oil port a of the floating valve 103 is connected with a first oil inlet V1 of a left front floating oil cylinder balance valve 105 and a second oil inlet V2 of a right front floating oil cylinder balance valve 104 at the same time, a first working oil port B of the floating valve 103 is connected with a first oil inlet V2 of the left front floating oil cylinder balance valve 105 and a second oil inlet V1 of the right front floating oil cylinder balance valve 104 at the same time, and a second oil return port T of the floating valve 103 is connected with a hydraulic oil tank at the first oil return port T of the control valve bank 106 and the oil return port T1 of the loading electromagnetic valve 101 at the same time. The electric control walking handle 107 is connected with a swash plate control proportional valve of the closed walking pump 109 through a PLC controller 110, a third working oil port A of the closed walking pump 109 is connected with a fourth working oil port A of the walking motor 108, and a second working oil port B of the closed walking pump 109 is connected with a third working oil port B of the walking motor 108.
The principle of the variable displacement pump 100 is shown in fig. 4, in which 209 is a pressure control valve and 210 is a flow control valve.
The principle of the pressure reducing flow valve 102 is shown in fig. 5, wherein 206 is a pressure reducing valve and 207 is a flow valve.
The principle of the control valve group 106 is shown in fig. 6, wherein the working oil port A1 of the main arm telescopic cylinder proportional reversing valve 201 is connected with the rodless cavity of the main arm telescopic cylinder 301, and the working oil port B1 of the main arm telescopic cylinder proportional reversing valve 201 is connected with the rod cavity of the main arm telescopic cylinder 301. The working oil port A2 of the main arm amplitude changing oil cylinder proportional reversing valve 202 in the control valve bank 106 is connected with the rodless cavity of the main arm amplitude changing oil cylinder 302, and the working oil port B2 of the main arm amplitude changing oil cylinder proportional reversing valve 202 is connected with the rod cavity of the main arm amplitude changing oil cylinder 302. The working oil port A3 of the turntable rotation proportional reversing valve 203 in the control valve group 106 is connected with the fifth working oil port a of the turntable rotation motor 208, and the working oil port B3 is connected with the fourth working oil port B of the turntable rotation motor 208.
Detailed Description
The operator firstly makes the loading electromagnetic valve 101 get electricity through an enabling switch (such as a foot switch, etc.), after the valve core of the loading electromagnetic valve 101 changes direction, the first oil inlet P1 of the loading electromagnetic valve is communicated with the first working oil port A, so that the output oil port P of the variable pump 100 is directly communicated with the first load feedback oil port LS of the variable pump 100, the outlet pressure of the variable pump 100 starts to rise along with the first load feedback oil port LS, when the outlet pressure of the variable pump rises to the set value of the pressure control valve 209, the valve core of the pressure control valve 209 changes direction, and the variable pump 100 enters constant pressure control (namely, the pump outlet maintains a high pressure standby state). Then the operation hand moves to walk, the electric control walking handle 107 controls the swash plate variable output pressure oil of the closed walking pump 109 to drive the walking motor 108 to rotate, when the chassis rear axle swings and pulls the valve core of the floating valve 103 to change direction, high pressure oil at the outlet of the variable pump 100 passes through the pressure reducing valve 206 and the flow valve 207 to the third oil inlet P of the floating valve 103, when the valve core of the floating valve 103 moves rightwards (namely, the left position is connected to an oil path), the third oil inlet P of the floating valve 103 is communicated with the second working oil port A, the high pressure oil respectively enters the first oil inlet and outlet V1 of the left front floating oil cylinder balance valve 105 and the second oil inlet and outlet V2 of the right front floating oil cylinder balance valve 104, and drives the piston rod of the left front floating oil cylinder 800 to extend and the piston rod of the right front floating oil cylinder 700 to retract, so as to further drive the front axle 500 to swing around the swing axis. At this time, the return oil from the first inlet/outlet port V2 of the left front floating cylinder balance valve 105 and the second inlet/outlet port V1 of the right front floating cylinder balance valve 104 flows back to the hydraulic tank through the first working port B and the second return port T of the floating valve 103. Similarly, when the valve core of the floating valve 103 moves leftwards (i.e. the right position is connected to an oil way), the third oil inlet P of the floating valve 103 is communicated with the first working oil port B, high-pressure oil respectively enters the second oil inlet and outlet V1 of the right front floating oil cylinder balance valve 104 and the first oil inlet and outlet V2 of the left front floating oil cylinder balance valve 105, and drives the piston rod of the right front floating oil cylinder 700 to extend and the piston rod of the left front floating oil cylinder 800 to retract, so as to further drive the front axle 500 to swing around the swing shaft. At this time, the return oil from the second oil inlet/outlet V2 of the right front floating cylinder balance valve 104 and the first oil inlet/outlet V1 of the left front floating cylinder balance valve 105 flows back to the hydraulic tank through the second working port a and the second return port T of the floating valve 103.
Also, when the manipulator arm is operated in a related motion, the load solenoid valve 101 needs to be powered on by an enable switch (e.g., a foot switch, etc.), so that the variable pump 100 is controlled to be constant pressure (i.e., the pump outlet maintains a high-pressure standby state). And then respectively powering up the main arm telescopic oil cylinder proportional reversing valve 201, the main arm amplitude variable oil cylinder proportional reversing valve 202 or the turntable rotation proportional reversing valve 203, so as to further control the main arm 400 to stretch or the main arm 400 to amplitude or the turntable 300 to rotate. Throughout this action, variable displacement pump 100 is always under constant pressure control (i.e., the pump outlet is always at high pressure).
In order to ensure the quick telescopic response of the floating cylinders at the two sides of the front axle 500 under the condition of poor road conditions in the walking process, the variable pump 100 in the hydraulic system adopts a constant pressure control mode. Meanwhile, when the arm support (i.e., the main arm 400) is operated in a related manner, the variable pump 100 is also controlled by a constant pressure. This can lead to:
1. the energy consumption is high: particularly, when the arm support is moved in a related manner, no matter how large the load is, the outlet of the variable pump 100 always maintains a high-pressure state, so that a certain pressure loss exists in the system, and the energy consumption is increased.
2. There is a start-up shock: before the related action of the action arm support, hydraulic oil at inlets of the main arm telescopic oil cylinder proportional reversing valve 201, the main arm amplitude varying oil cylinder proportional reversing valve 202 and the turntable rotation proportional reversing valve 203 is in a high-pressure standby state, and when the valve ports of the main arm telescopic oil cylinder proportional reversing valve 201, the main arm amplitude varying oil cylinder proportional reversing valve 202 or the turntable rotation proportional reversing valve 203 are opened, the high-pressure oil can quickly pass through the main arm telescopic oil cylinder proportional reversing valve 201, the main arm amplitude varying oil cylinder proportional reversing valve 202 or the turntable rotation proportional reversing valve 203 to drive an executing element to act, so that impact is caused.
Disclosure of Invention
In order to solve the problems, the application provides the constant-pressure control loop of the floating oil cylinders of the chassis of the overhead working truck combined with the load sensitive control system and the overhead working truck adopting the loop, which not only can ensure the quick telescopic response of the floating oil cylinders on the two sides of the front axle under the condition of poor road conditions in the walking process, but also can solve the problems of starting impact and high energy consumption of a hydraulic system during the arm support action.
The application provides a control system of an underframe floating oil cylinder of an overhead working truck, which comprises a variable pump, a control valve group for controlling a main arm and a balance valve group for controlling the floating oil cylinder, wherein the variable pump is provided with an output oil port P and a first load feedback oil port LS, the output oil port P is simultaneously connected with the control valve group and the balance valve group, the output oil port P and the control valve group are connected with the first load feedback oil port LS through an oil pump control valve block, and the oil pump control valve block is used for controlling the on-off between the output oil port P and the first load feedback oil port LS and feeding the pressure of the control valve group back to the first load feedback oil port LS.
Optionally, the oil pump control valve block includes solenoid valve and tee bend shuttle valve, the solenoid valve is two tee bend solenoid valve and has second oil inlet P1, second oil return port T1 and fifth work hydraulic fluid port A, the tee bend shuttle valve has sixth work hydraulic fluid port A, feedback hydraulic fluid port LS1 and feedback hydraulic fluid port LS2, and wherein feedback hydraulic fluid port LS1 is the unidirectional input, and feedback hydraulic fluid port LS2 is the delivery outlet, output hydraulic fluid port P of variable pump is connected to second oil inlet P1, the oil tank is connected to second oil return port T1, sixth work hydraulic fluid port A of tee bend shuttle valve is connected to fifth work hydraulic fluid port A, feedback hydraulic fluid port LS2 connects the first load feedback hydraulic fluid port LS of variable pump, feedback hydraulic fluid port LS1 connects the valve group.
Optionally, the oil pump control valve block is further provided with a first throttling device and a second throttling device, the first throttling device is located between the second oil inlet P1 and the output oil port P, and the second throttling device is located between the second oil return port T1 and the oil tank.
Optionally, the control valve group comprises a main arm telescopic cylinder proportional reversing valve, a main arm amplitude cylinder proportional reversing valve and a rotary table rotary proportional reversing valve, the oil inlet ends of the main arm telescopic cylinder proportional reversing valve, the main arm amplitude cylinder proportional reversing valve and the rotary table rotary proportional reversing valve are connected in parallel with a first oil inlet P and a first oil return port T, the first oil inlet P is connected with an output port P of the variable pump, the first oil return port T is connected with an oil tank, the main arm telescopic cylinder proportional reversing valve is provided with a working port A1 and a working port B1 so as to be respectively connected with a no-rod cavity and a rod cavity of the main arm telescopic cylinder, the main arm amplitude cylinder proportional reversing valve is provided with a working port A2 and a working port B2 so as to be respectively connected with a no-rod cavity and a rod cavity of the main arm amplitude cylinder, the rotary table rotary proportional reversing valve is provided with a working port A3 and a working port B3 so as to be connected with a rotary table rotary motor, and the working port A2, the working port A3 and the working port B3 are respectively connected with a one-way feedback port LS1 through a one-way valve.
Optionally, the first oil inlet P is connected to the first oil return port T through an overflow valve.
Optionally, the working oil port A1, the working oil port B1, the working oil port A2, the working oil port B2, the working oil port A3 and the working oil port B3 are respectively connected in parallel with a feedback oil path through a one-way valve, the feedback oil path is formed with a second load feedback oil port LS and is connected with the feedback oil port LS1 through the second load feedback oil port LS, and meanwhile, the feedback oil path is connected with the first oil return port T through a third throttling device.
Optionally, the balance valve group includes a pressure reducing flow valve, a floating valve, a right front floating cylinder balance valve and a left front floating cylinder balance valve, the pressure reducing flow valve has a second oil inlet P and an output oil port P1, the floating valve has a third oil inlet P, a second oil return port T, a second working oil port a and a first working oil port B, the right front floating cylinder balance valve has a second oil inlet V1 and a second oil inlet V2 respectively abutting the rodless cavity and the rod cavity of the right front floating cylinder, the left front floating cylinder balance valve has a first oil inlet V1 and a first oil inlet V2 respectively abutting the rodless cavity and the rod cavity of the left front floating cylinder, the second oil inlet P of the pressure reducing flow valve is connected with the output oil port P of the variable pump, the output oil port P1 of the pressure reducing flow valve is connected with the third oil inlet P of the floating valve, the second working oil port a of the floating valve is simultaneously connected with the first oil inlet V1 of the left front floating cylinder balance valve and the second oil inlet V2 of the right front floating cylinder balance valve, the first oil inlet V1 of the floating cylinder balance valve is simultaneously connected with the first oil inlet V2 of the floating cylinder, and the first oil inlet V of the floating valve is simultaneously connected with the first oil inlet V1 of the floating valve.
Optionally, the pressure reducing flow valve comprises a pressure reducing valve and a flow valve, and the hydraulic oil sequentially passes through the pressure reducing valve and the flow valve after entering through the second oil inlet P and is led out from the output oil port P1.
Optionally, the automatic walking device further comprises an electric control walking handle, a PLC controller, a closed walking pump and a walking motor, wherein the closed walking pump is provided with a third working oil port A, a second working oil port B and a swash plate control proportional valve for controlling output quantity, the walking motor is provided with a fourth working oil port A and a third working oil port B, the PLC controller is electrically connected with the electric control walking handle, the oil pump control valve block and the closed walking pump, the third working oil port A is connected with the fourth working oil port A, the second working oil port B is connected with the third working oil port B, and accordingly when the electric control walking handle controls the swash plate variable output of the closed walking pump to drive the walking motor to rotate, the PLC controller starts the oil pump control valve block, and the control output oil port P is communicated with the first load feedback oil port LS.
On the other hand, the application also provides an overhead working truck, which comprises a truck body, a turntable, a main arm and a working platform, wherein the truck body is provided with a front axle and a rear axle and wheels are arranged through the front axle and the rear axle, the truck body is provided with a left front floating cylinder and a right front floating cylinder corresponding to the left and right ends of the front axle so as to adjust the swing of the front axle, the turntable is arranged on the truck body through a turntable rotating motor, the main arm is arranged on the turntable and is provided with a main arm telescopic cylinder and a main arm luffing cylinder so as to control the telescopic and swing of the main arm, the working platform is arranged on the main arm, and the overhead working truck is further provided with a control system of the chassis floating cylinder of the overhead working truck with the structure.
The beneficial effects of the application are as follows: according to the control system and the overhead working truck, the oil pump control valve block is added, when the overhead working truck walks, the variable pump is in a constant pressure control state, the quick response of the floating oil cylinder of the underframe is ensured, meanwhile, when the arm support acts, the oil pressure state of the control valve block is fed back through the oil pump control valve block, so that the variable pump processes load sensitive control, the energy consumption and starting impact of the system are reduced, and the stability and the safety are high.
Drawings
The application is further illustrated by the following examples in conjunction with the accompanying drawings:
FIG. 1 is a side view of an overhead working truck;
FIG. 2 is a front elevational view of the overhead working truck;
FIG. 3 is a block diagram of a conventional hydraulic control system;
FIG. 4 is a schematic diagram of the variable displacement pump of FIG. 3;
FIG. 5 is a schematic view of the configuration of the pressure reducing flow valve of FIG. 3;
FIG. 6 is a schematic diagram of the control valve block of FIG. 3;
FIG. 7 is a schematic diagram of an improved hydraulic control system;
FIG. 8 is a schematic diagram of the configuration of the oil pump control valve block of FIG. 7;
fig. 9 is a schematic view of the control valve assembly of fig. 7.
Detailed Description
For the purpose of making the objects, technical solutions and advantages of the embodiments of the present application more apparent, the technical solutions of 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 apparent that the described embodiments are some embodiments of the present application, but not all embodiments of the present application. The components of the embodiments of the present application generally described and illustrated in the figures herein may be arranged and designed in a wide variety of different configurations. Thus, the following detailed description of the embodiments of the application, as presented in the figures, is not intended to limit the scope of the application, as claimed, but is merely representative of selected embodiments of the application.
Referring to fig. 7 to 9, in one aspect, the present embodiment provides a control system for a floating cylinder of an underframe of an overhead working truck, including a variable pump 100, a control valve bank 106 for controlling a main arm 400, and a balance valve bank for controlling the floating cylinder, where the variable pump 100 has an output port P and a first load feedback port LS, the output port P is connected with the control valve bank 106 and the balance valve bank at the same time, the output port P and the control valve bank 106 are connected with the first load feedback port LS through an oil pump control valve block 111, and the oil pump control valve block 111 is used for controlling on-off between the output port P and the first load feedback port LS, and can feedback the pressure of the control valve bank 106 to the first load feedback port LS.
When the hydraulic control system works, the oil pump control valve block 111 is set to automatically control the on-off between the output oil port P and the first load feedback oil port LS according to the walking state of the overhead working truck, so that the variable pump is in a constant pressure control state when walking can be realized, and the quick response of the chassis floating oil cylinder is ensured. Meanwhile, when the arm support acts, the oil pressure state of the valve group is controlled through the oil pump control valve block feedback, so that the variable pump processes load sensitive control, the energy consumption and starting impact of the system are reduced, and the stability and the safety are high.
As shown in fig. 8, the oil pump control valve block 111 includes a solenoid valve 213 and a three-way shuttle valve 212, where the solenoid valve 213 is a two-position three-way solenoid valve and has a second oil inlet P1, a second oil return port T1, and a fifth working port a, the three-way shuttle valve 212 has a sixth working port a, a feedback port LS1, and a feedback port LS2, where the feedback port LS1 is a unidirectional input port, the feedback port LS2 is an output port, the second oil inlet P1 is connected to the output port P of the variable pump 100, the second oil return port T1 is connected to the oil tank, the fifth working port a is connected to the sixth working port a of the three-way shuttle valve 212, the feedback port LS2 is connected to the first load feedback port LS of the variable pump 100, and the feedback port LS1 is connected to the control valve block 106.
Further, the oil pump control valve block 111 is further provided with a first throttling device 215 and a second throttling device 214, the first throttling device 215 is located between the second oil inlet P1 and the output oil port P, and the second throttling device 214 is located between the second oil return port T1 and the oil tank.
While the construction of variable displacement pump 100 is consistent with conventional construction, including pressure control valve 209 and flow control valve 210 as shown.
When the high-pressure oil enters through the second oil inlet P1, the high-pressure oil is throttled and limited by the first throttling device 215, so that pressure impact can be eliminated, and then the high-pressure oil stably enters the first load feedback oil port LS, and starting impact is reduced. After the work is completed, the high-pressure oil is led out from the second oil return port T1, throttled and pressure-limited by the second throttling device 214 and flows back into the oil tank. By means of this second throttling means 214 a smooth unloading can be achieved, eliminating shocks. Therefore, under the control of the control system, the operation of the overhead working truck is more stable, the service life is longer, and the safety is higher.
As shown in fig. 9, the control valve set 106 includes a main arm telescopic cylinder proportional reversing valve 201, a main arm luffing cylinder proportional reversing valve 202, and a turntable rotation proportional reversing valve 203, the oil inlet ends of the main arm telescopic cylinder proportional reversing valve 201, the main arm luffing cylinder proportional reversing valve 202, and the turntable rotation proportional reversing valve 203 are connected in parallel with a first oil inlet P, and the oil return end is connected in parallel with a first oil return port T, the first oil inlet P is connected with an output port P of the variable pump 100, the first oil return port T is connected with an oil tank, the main arm telescopic cylinder proportional reversing valve 201 is provided with a working port A1 and a working port B1 to be respectively connected with a rodless cavity and a rod cavity of the main arm telescopic cylinder 301, the main arm luffing cylinder proportional reversing valve 202 is provided with a working port A2 and a working port B2 to be respectively connected with a rodless cavity and a rod cavity of the main arm luffing cylinder 302, the turntable rotation proportional reversing valve 203 is provided with a working port A3 and a working port B3 to be connected with a turntable rotation motor 208, and the working port A1, the working port B2, the working port A3 and the working port B3 are respectively connected with a one-way port B1 and the working port B3.
In the actual production process, the working oil port A1, the working oil port B1, the working oil port A2, the working oil port B2, the working oil port A3 and the working oil port B3 may be connected in parallel with a feedback oil path 211 through a one-way valve, and the feedback oil path 211 is formed with a second load feedback oil port LS and is connected with the feedback oil port LS1 through the second load feedback oil port LS. In this way, the line arrangement can be reduced, and the feedback port LS1 can, of course, also be connected by a line alone.
Further, the first oil inlet P is connected to the first oil return port T through the relief valve 204. Therefore, when the hydraulic oil output by the output oil port P is in excess of the oil quantity required by action, the hydraulic oil flows back to the oil tank through the overflow valve 204, so that the large load on the main arm telescopic oil cylinder proportional reversing valve 201, the main arm amplitude oil cylinder proportional reversing valve 202 and the turntable rotation proportional reversing valve 203 is avoided, and the service life of equipment is prolonged. And the overflow valve is preferably arranged between the oil return ends of the main arm telescopic oil cylinder proportional reversing valve 201, the main arm amplitude variable oil cylinder proportional reversing valve 202 and the turntable rotation proportional reversing valve 203 and the first oil return port T, so that stable unloading of the main arm telescopic oil cylinder proportional reversing valve 201, the main arm amplitude variable oil cylinder proportional reversing valve 202 and the turntable rotation proportional reversing valve 203 is realized.
Further, the feedback oil path 211 is connected to the first oil return port T through a third throttling device 205. In this way, when the oil pressure in the feedback oil path 211 exceeds the flow rate of the three-way shuttle valve 212, smooth unloading can be achieved by the third throttle device 205 flowing back to the oil tank, thereby protecting the three-way shuttle valve 212.
The main arm telescopic cylinder proportional reversing valve 201 and the main arm luffing cylinder proportional reversing valve 202 can be connected with a main arm telescopic cylinder and a main arm luffing cylinder of an overhead working truck through a balance valve body structure in the actual installation process, and the specific connection relation can refer to the related description of the application number CN 201810226178.6. While the working oil port A3 of the turntable rotation proportional directional valve 203 is connected to the fifth working oil port a of the turntable rotation motor 208, and the working oil port B3 is connected to the fourth working oil port B of the turntable rotation motor 208.
As shown in the figure, the balancing valve set includes a pressure reducing flow valve 102, a floating valve 103, a right front floating cylinder balancing valve 104 and a left front floating cylinder balancing valve 105, the pressure reducing flow valve 102 has a second oil inlet P and an output oil port P1, the floating valve 103 has a third oil inlet P, a second oil return port T, a second working oil port a and a first working oil port B, the right front floating cylinder balancing valve 104 has a second oil inlet V1 and a second oil inlet V2 respectively abutting the rodless cavity and the rod cavity of the right front floating cylinder 700, the left front floating cylinder balancing valve 105 has a first oil inlet V1 and a first oil inlet V2 respectively abutting the rodless cavity and the rod cavity of the left front floating cylinder 800, the second oil inlet P of the pressure reducing flow valve 102 is connected with the output oil port P of the variable pump 100, the output oil port P1 of the pressure reducing flow valve 102 is connected with the third oil inlet P of the floating valve 103, the second working oil port a of the floating valve 103 is simultaneously connected with the first oil inlet V1 of the right front floating cylinder balancing valve 105 and the second oil inlet V2 of the floating cylinder balancing valve 103, and the left front floating cylinder balancing valve 103 is simultaneously connected with the first oil inlet V1 of the right front floating cylinder balancing valve 103 and the second oil inlet V2.
Specifically, the pressure-reducing flow valve 102 includes a pressure-reducing valve 206 and a flow valve 207, and hydraulic oil enters through the second oil inlet P, sequentially passes through the pressure-reducing valve 206 and the flow valve 207, and is led out from the output oil port P1.
In addition, the control system of the present embodiment includes, in addition to the variable pump 100, the control valve group 106 for controlling the main arm 400, and the balance valve group for controlling the floating cylinder, an electric control traveling handle 107, a PLC controller 110, a closed traveling pump 109, and a traveling motor 108, where the closed traveling pump 109 has a third working port a, a second working port B, and a swash plate control proportional valve for controlling the output, the traveling motor 108 has a fourth working port a and a third working port B, the PLC controller 110 is electrically connected to the electric control traveling handle 107, the oil pump control valve block 111, and the closed traveling pump 109, the third working port a is connected to the fourth working port a, and the second working port B is connected to the third working port B, so that when the electric control traveling handle 107 controls the swash plate variable output of the closed traveling pump 109 to drive the traveling motor 108 to rotate, the oil pump control valve block 111 is started by the PLC controller 110, and the control output port P is communicated to the first load feedback port LS.
The first throttle device 215, the second throttle device 214, and the third throttle device 205 are each provided in the throttle structure in this embodiment.
The control system adopting the structure has the following working mechanism:
when the operator walks, the PLC controller 110 adjusts the swash plate control proportional valve of the closed traveling pump 109 according to the state of the electrically controlled traveling handle 107, so that the closed traveling pump 109 supplies oil to the traveling motor 108 to drive the traveling. Meanwhile, the PLC controller 110 makes the solenoid valve 213 of the oil pump control valve block 111 be powered, the high pressure oil of the output port P is fed back to the first load feedback port LS through the solenoid valve 213 and the feedback port LS2 of the three-way shuttle valve 212 after the pressure impact is eliminated by the first throttling device 215, and after the outlet pressure of the variable pump 100 rises to the set value of the pressure control valve 209, the pressure control valve 209 is reversed, and the variable pump 100 enters a constant pressure control state (i.e., the pump outlet maintains a high pressure standby state). When the rear axle of the chassis swings and pulls the valve core of the floating valve 103 to change direction, the pressure oil at the outlet of the variable pump 100 passes through the pressure reducing flow valve 102 to the third oil inlet P of the floating valve 103, when the valve core of the floating valve 103 moves rightwards (namely, the left position is connected to an oil way), the third oil inlet P of the floating valve 103 is communicated with the second working oil port A, high-pressure oil respectively enters the first oil inlet and outlet port V1 of the left front floating oil cylinder balance valve 105 and the second oil inlet and outlet port V2 of the right front floating oil cylinder balance valve 104, the piston rod of the left front floating oil cylinder 800 is driven to extend, the piston rod of the right front floating oil cylinder 700 is driven to retract, and the front axle 500 is further driven to swing around the swing axis, and at this time, the return oil at the first oil inlet and outlet port V2 of the left front floating oil cylinder balance valve 105 and the second oil inlet and outlet port V1 of the right front floating oil cylinder balance valve 104 flow back to the oil tank through the first working oil port B and the second oil return port T of the floating valve 103. Similarly, when the valve core of the floating valve 103 moves leftwards (i.e. the right position is connected to the oil way), the third oil inlet P of the floating valve 103 is communicated with the first working oil port B, high-pressure oil respectively enters the first oil inlet and outlet port V2 of the left front floating oil cylinder balance valve 105 and the second oil inlet and outlet port V1 of the right front floating oil cylinder balance valve 104, the piston rod of the left front floating oil cylinder 800 is driven to retract, the piston rod of the right front floating oil cylinder 700 is driven to extend, and the front axle 500 is further driven to swing around the swing shaft, and at this time, return oil of the first oil inlet and outlet port V1 of the left front floating oil cylinder balance valve 105 and the second oil inlet and outlet port V2 of the right front floating oil cylinder balance valve 104 flows back to the oil tank through the second working oil port a and the second oil return port T of the floating valve 103.
When the walking is stopped, the electric control walking handle 107 is reset, the PLC 110 causes the electromagnetic valve 213 of the oil pump control valve block 111 to lose electricity, and the pressure oil in the first load feedback oil port LS of the original variable pump 100 flows back to the oil tank through the electromagnetic valve 213 and the second throttling device 214, so that the stable unloading control of the variable pump 100 is realized.
When the main arm 400 is operated by an operator, for example, the main arm 400 is extended, the left side of the proportional reversing valve 201 of the main arm telescopic cylinder in the control valve group 106 is powered (i.e., DT2 shown in the drawing is powered), the left side is connected to the oil path, at this time, the solenoid valve 213 in the oil pump control valve block 111 is de-energized, high-pressure oil at the outlet of the variable pump 100 cannot enter the second oil inlet P1, but enters the rodless cavity of the main arm telescopic cylinder 301 from the first oil inlet P via the working oil port A1, meanwhile, the pressure oil is fed back to the feedback oil port LS1 via the check valve and the second load feedback oil port LS, and is fed back to the first load feedback oil port LS of the variable pump 100 and the valve core spring cavity side of the flow control valve 210 via the three-way shuttle valve 212, so that the swash plate control proportional valve of the variable pump 100 is adjusted according to the opening degree of the proportional reversing valve 201 of the main arm telescopic cylinder, thereby realizing load sensitivity control. In the whole action process, the third throttling device 205 plays a certain role in stabilizing pressure on the feedback oil path 211, so that larger pressure fluctuation is avoided, and meanwhile, after the main arm telescopic oil cylinder proportional reversing valve 201 in the control valve group 106 is powered off, the pressure in the feedback oil path 211 can be slowly released through the third throttling device 205, so that stable unloading control of the variable pump 100 is realized.
On the other hand, this embodiment also discloses an overhead working truck, which comprises a truck body 200, a turntable 300, a main arm 400 and a working platform, wherein the truck body 200 is provided with a front axle 500 and a rear axle 600, wheels are installed through the front axle 500 and the rear axle 600, the truck body 200 is provided with a left front floating cylinder 800 and a right front floating cylinder 700 corresponding to the left and right ends of the front axle 500 so as to adjust the swing of the front axle 500, the turntable 300 is installed on the truck body 200 through a turntable rotary motor 208, the main arm 400 is installed on the turntable 300 and is provided with a main arm telescopic cylinder 301 and a main arm luffing cylinder 302 so as to control the telescopic and swing of the main arm 400, and the working platform is installed on the main arm 400 and is also provided with a control system of the chassis floating cylinder of the overhead working truck with the structure.
The valve body of the float valve 103 is arranged on the vehicle body 200, and the valve core pull rod is connected with the rear axle 600, so that the valve core pull rod of the float valve 103 is driven to move when the rear axle 600 swings. In actual installation, the floating valve 103 is vertically installed, so when the rear axle 600 swings, the spool pull rod of the floating valve 103 is driven to move upwards or downwards, and when the spool pull rod moves upwards, the spool pull rod of the floating valve 103 moves rightwards correspondingly to the left access oil way mentioned in the working mechanism of the control system, and when the spool pull rod moves downwards, the spool pull rod of the floating valve 103 moves rightwards, so that the working mechanism of the control system is realized.
The overhead working truck controlled by the control system has the advantages of stable action, longer service life and higher safety.
The above examples are only preferred embodiments of the application, and other embodiments of the application are possible. Equivalent modifications and substitutions can be made by those skilled in the art without departing from the spirit of the application, and these equivalent modifications or substitutions are intended to be included within the scope of the present application as set forth in the following claims.
Claims (8)
1. The control system of the chassis floating cylinder of the overhead working truck comprises a variable pump (100), a control valve group (106) for controlling a main arm (400) and a balance valve group for controlling the floating cylinder, wherein the variable pump (100) is provided with an output oil port P and a first load feedback oil port LS, and the output oil port P is simultaneously connected with the control valve group (106) and the balance valve group, and the control system is characterized in that the output oil port P and the control valve group (106) are connected with the first load feedback oil port LS through an oil pump control valve block (111), and the oil pump control valve block (111) is used for controlling the on-off between the output oil port P and the first load feedback oil port LS and can feed back the pressure of the control valve group (106) to the first load feedback oil port LS; the balance valve group comprises a pressure reducing flow valve (102), a floating valve (103), a right front floating cylinder balance valve (104) and a left front floating cylinder balance valve (105), wherein the pressure reducing flow valve (102) is provided with a second oil inlet P and an output oil port P1, the floating valve (103) is provided with a third oil inlet P, a second oil return port T, a second working oil port A and a first working oil port B, the right front floating cylinder balance valve (104) is provided with a second oil inlet/outlet V1 and a second oil inlet/outlet V2 which are respectively butted with a rodless cavity of the right front floating cylinder (700) and a rod cavity, the left front floating cylinder balance valve (105) is provided with a first oil inlet/outlet V1 and a first oil inlet/outlet V2 which are respectively butted with the rodless cavity of the left front floating cylinder (800), the second oil inlet P of the pressure reducing flow valve (102) is connected with the output oil port P of the variable pump (100), the output oil port P1 of the pressure reducing flow valve (102) is connected with the third oil inlet P of the floating valve (103), the second floating valve (103) is connected with the first oil inlet/outlet V2 of the floating cylinder (103) and the left front floating cylinder balance valve (104) is connected with the first oil inlet/outlet V2 of the left front floating cylinder (104) and the left front floating cylinder balance valve (2) is connected with the left front floating cylinder balance valve (2) and the left front oil cylinder (105) at the same time, the second oil return port T of the floating valve (103) is connected with an oil tank; still include automatically controlled walking handle (107), PLC controller (110), closed running pump (109) and walking motor (108), closed running pump (109) have third work hydraulic fluid port A, second work hydraulic fluid port B and the sloping cam plate control proportional valve of control output, walking motor (108) have fourth work hydraulic fluid port A and third work hydraulic fluid port B, automatically controlled walking handle (107), oil pump control valve piece (111) and closed running pump (109) of PLC controller (110) electric connection, fourth work hydraulic fluid port A is connected to third work hydraulic fluid port A, third work hydraulic fluid port B is connected to second work hydraulic fluid port B to when automatically controlled walking handle (107) control closed running pump (109) sloping cam plate variable output and drive walking motor (108) rotate, start oil pump control valve piece (111) through PLC controller (110), make control output hydraulic fluid port P communicate first load feedback hydraulic fluid port LS.
2. The control system of the floating cylinder of the chassis of the overhead working truck according to claim 1, wherein the oil pump control valve block (111) comprises an electromagnetic valve (213) and a three-way shuttle valve (212), the electromagnetic valve (213) is a two-position three-way electromagnetic valve and is provided with a second oil inlet P1, a second oil return port T1 and a fifth working port a, the three-way shuttle valve (212) is provided with a sixth working port a, a feedback port LS1 and a feedback port LS2, the feedback port LS1 is a unidirectional input port, the feedback port LS2 is an output port, the second oil inlet P1 is connected with the output port P of the variable pump (100), the second oil return port T1 is connected with the oil tank, the fifth working port a is connected with the sixth working port a of the three-way shuttle valve (212), the feedback port LS2 is connected with the first load feedback port LS of the variable pump (100), and the feedback port LS1 is connected with the control valve block (106).
3. A control system of a floating cylinder of an underframe of an overhead working truck according to claim 2, characterized in that the oil pump control valve block (111) is further provided with a first throttling device (215) and a second throttling device (214), the first throttling device (215) is located between the second oil inlet P1 and the output oil port P, and the second throttling device (214) is located between the second oil return port T1 and the oil tank.
4. A control system of an underframe floating oil cylinder of an overhead working truck according to claim 2 or 3, wherein the control valve group (106) comprises a main arm telescopic oil cylinder proportional reversing valve (201), a main arm amplitude varying oil cylinder proportional reversing valve (202) and a turntable rotation proportional reversing valve (203), the oil inlet ends of the main arm telescopic oil cylinder proportional reversing valve (201), the main arm amplitude varying oil cylinder proportional reversing valve (202) and the turntable rotation proportional reversing valve (203) are connected in parallel with a first oil inlet P, the oil return end is connected in parallel with a first oil return port T, the first oil inlet P is connected with an output oil port P of a variable pump (100), the first oil return port T is connected with an oil tank, the main arm telescopic oil cylinder proportional reversing valve (201) is provided with a working oil port A1 and a working oil port B1 to be respectively connected with a rodless cavity and a rod cavity of the main arm telescopic oil cylinder (301), the main arm amplitude variable oil cylinder proportional reversing valve (202) is provided with a working oil port A2 and a working oil port B2 to be respectively connected with the rodless cavity and the rod cavity of the main arm amplitude variable oil cylinder (302), the turntable rotation proportional reversing valve (203) is provided with a working oil port A3 and a working oil port B3 to be connected with the turntable rotation motor (208), and the working oil port A1, the working oil port B1, the working oil port A2, the working oil port B2, the working oil port A3 and the working oil port B3 are respectively connected with a feedback oil port LS1 through one-way valves.
5. The control system of the floating cylinder of the chassis of the overhead working truck according to claim 4, wherein the first oil inlet P is connected with the first oil return port T through an overflow valve (204).
6. The control system of an under-frame floating cylinder of an overhead working truck according to claim 4, wherein the working oil port A1, the working oil port B1, the working oil port A2, the working oil port B2, the working oil port A3 and the working oil port B3 are each connected in parallel with a feedback oil path (211) through a check valve, the feedback oil path (211) is formed with a second load feedback oil port LS and is connected to the feedback oil port LS1 through the second load feedback oil port LS, and the feedback oil path (211) is connected to the first oil return port T through a third throttle device (205).
7. A control system of a floating cylinder of an underframe of an overhead working truck according to claim 1, wherein the pressure reducing flow valve (102) comprises a pressure reducing valve (206) and a flow valve (207), and hydraulic oil enters through the second oil inlet P and then sequentially passes through the pressure reducing valve (206) and the flow valve (207) to be led out from the output port P1.
8. The utility model provides an aerial working vehicle, includes automobile body (200), revolving stage (300), main arm (400) and work platform, automobile body (200) have front axle (500) and rear axle (600) and install the wheel through front axle (500) and rear axle (600), automobile body (200) correspond the left and right sides both ends of front axle (500) and are provided with left front floating hydro-cylinder (800) and right front floating hydro-cylinder (700) to adjust the swing of front axle (500), revolving stage (300) are installed on automobile body (200) through revolving stage gyration motor (208), main arm (400) are installed on revolving stage (300) and are provided with main arm telescopic cylinder (301) and main arm luffing cylinder (302) to control the flexible and the swing of main arm (400), work platform installs on main arm (400), its characterized in that still includes the control system of the aerial working vehicle chassis floating hydro-cylinder of any one of claims 1-7.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910283786.5A CN110030217B (en) | 2019-04-10 | 2019-04-10 | Control system of floating oil cylinder of chassis of overhead working truck and overhead working truck |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910283786.5A CN110030217B (en) | 2019-04-10 | 2019-04-10 | Control system of floating oil cylinder of chassis of overhead working truck and overhead working truck |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110030217A CN110030217A (en) | 2019-07-19 |
| CN110030217B true CN110030217B (en) | 2023-12-01 |
Family
ID=67237781
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910283786.5A Active CN110030217B (en) | 2019-04-10 | 2019-04-10 | Control system of floating oil cylinder of chassis of overhead working truck and overhead working truck |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN110030217B (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110304137B (en) * | 2019-08-13 | 2021-07-09 | 徐州重型机械有限公司 | Hydraulic system and crane |
| CN110645213A (en) * | 2019-09-06 | 2020-01-03 | 湖南星邦重工有限公司 | Active floating control method and system for underframe and aerial work platform thereof |
| CN110566522A (en) * | 2019-09-06 | 2019-12-13 | 湖南星邦重工有限公司 | Active floating control system for underframe and aerial work platform thereof |
| CN110985464A (en) * | 2019-12-30 | 2020-04-10 | 徐州海伦哲特种车辆有限公司 | Automatic interlocking control system for getting on and off of overhead working truck and control method thereof |
| CN112833058B (en) * | 2021-01-21 | 2023-03-31 | 长沙中联重科环境产业有限公司 | Load-sensitive hydraulic system and hedge trimming equipment |
| CN114278631A (en) * | 2021-12-31 | 2022-04-05 | 潍柴动力股份有限公司 | Excavator walking motor control system |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101857174A (en) * | 2010-05-13 | 2010-10-13 | 卢宇 | Hydraulic system of mechanically operated triple pump |
| CN106829815A (en) * | 2017-03-27 | 2017-06-13 | 徐工消防安全装备有限公司 | The arm support control system and aerial work platform of aerial work platform |
| CN108278229A (en) * | 2018-03-19 | 2018-07-13 | 湖南星邦重工有限公司 | A kind of crank arm type high-altitude operation vehicle connector leveling hydraulic system |
| CN108658019A (en) * | 2018-07-03 | 2018-10-16 | 徐州海伦哲专用车辆股份有限公司 | A kind of working bucket leveling system of high-altitude operation vehicle |
| CN109250626A (en) * | 2018-11-22 | 2019-01-22 | 徐州海伦哲特种车辆有限公司 | A kind of small connecting lever insulating overhead operating vehicle cantilever crane and its control system |
| CN210599623U (en) * | 2019-04-10 | 2020-05-22 | 湖南星邦智能装备股份有限公司 | Control system of floating oil cylinder of high-altitude operation vehicle chassis and high-altitude operation vehicle |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20180319634A1 (en) * | 2014-10-30 | 2018-11-08 | Xuzhou Heavy Machinery Co., Ltd. | Crane hydraulic system and controlling method of the system |
-
2019
- 2019-04-10 CN CN201910283786.5A patent/CN110030217B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101857174A (en) * | 2010-05-13 | 2010-10-13 | 卢宇 | Hydraulic system of mechanically operated triple pump |
| CN106829815A (en) * | 2017-03-27 | 2017-06-13 | 徐工消防安全装备有限公司 | The arm support control system and aerial work platform of aerial work platform |
| CN108278229A (en) * | 2018-03-19 | 2018-07-13 | 湖南星邦重工有限公司 | A kind of crank arm type high-altitude operation vehicle connector leveling hydraulic system |
| CN108658019A (en) * | 2018-07-03 | 2018-10-16 | 徐州海伦哲专用车辆股份有限公司 | A kind of working bucket leveling system of high-altitude operation vehicle |
| CN109250626A (en) * | 2018-11-22 | 2019-01-22 | 徐州海伦哲特种车辆有限公司 | A kind of small connecting lever insulating overhead operating vehicle cantilever crane and its control system |
| CN210599623U (en) * | 2019-04-10 | 2020-05-22 | 湖南星邦智能装备股份有限公司 | Control system of floating oil cylinder of high-altitude operation vehicle chassis and high-altitude operation vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| CN110030217A (en) | 2019-07-19 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN110030217B (en) | Control system of floating oil cylinder of chassis of overhead working truck and overhead working truck | |
| CN210599623U (en) | Control system of floating oil cylinder of high-altitude operation vehicle chassis and high-altitude operation vehicle | |
| CN110566522A (en) | Active floating control system for underframe and aerial work platform thereof | |
| KR101680902B1 (en) | Steering load sensing system for a heavy equipment | |
| CN104718150A (en) | Lifting device | |
| CN110645213A (en) | Active floating control method and system for underframe and aerial work platform thereof | |
| CN202827257U (en) | Hydraulic lifting control system for mine self-discharging vehicle and mine self-discharging vehicle | |
| CN111483284B (en) | Hydraulic suspension system, lifting control method and multi-axis flat car | |
| CN113389761A (en) | Scissor-fork type aerial work platform and floating control system thereof | |
| CN110285102B (en) | Multi-shaft emergency rescue vehicle hydraulic steering control system with active suspension | |
| CN113511601B (en) | Rotary hydraulic system, engineering machine and rotary control method | |
| CN108730244B (en) | Winch motor feeding hydraulic system and method and slot milling machine | |
| CN113135223B (en) | Steering drive control system and engineering machinery | |
| CN113683033A (en) | Hydraulic full-time floating control system and control method of cantilever type aerial work platform | |
| CN212672126U (en) | High-altitude operation vehicle and full-floating control system of walking chassis thereof | |
| CN109505812A (en) | A kind of variable pump bi-mode control hydraulic system and tunneling operation vehicle | |
| CN113697672A (en) | Hydraulic control system of crane and offshore crane | |
| CN212202669U (en) | Engineering machinery walking mechanism and crawler tensioning device integrated hydraulic control system | |
| CN211009327U (en) | Active floating control system for underframe and aerial work platform thereof | |
| CN212148295U (en) | Hydraulic suspension system and multi-axis flat car | |
| CN110630576A (en) | High-performance scissor-fork type hydraulic system for aerial work platform | |
| CN215626637U (en) | Hydraulic full-time floating control system of cantilever type aerial work platform | |
| CN111120437A (en) | Multi-mode steering and traveling system of engineering machinery | |
| CN107504000B (en) | Multi-way reversing device of lorry-mounted crane | |
| CN103613011B (en) | Autonomous control system for crane |
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 | ||
| CB02 | Change of applicant information | ||
| CB02 | Change of applicant information |
Address after: 410600 Jinzhou Avenue East 128, Ningxiang hi tech Industrial Park, Changsha, Hunan Applicant after: Hunan Xingbang Intelligent Equipment Co.,Ltd. Address before: 410600 Jinzhou Avenue East 128, Ningxiang hi tech Industrial Park, Changsha, Hunan Applicant before: HUNAN SINOBOOM HEAVY INDUSTRY Co.,Ltd. |
|
| GR01 | Patent grant | ||
| GR01 | Patent grant |