CN111237272A - Hydraulic control system for synchronous lifting of hydro-pneumatic suspension oil cylinders - Google Patents
Hydraulic control system for synchronous lifting of hydro-pneumatic suspension oil cylinders Download PDFInfo
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- CN111237272A CN111237272A CN202010041702.XA CN202010041702A CN111237272A CN 111237272 A CN111237272 A CN 111237272A CN 202010041702 A CN202010041702 A CN 202010041702A CN 111237272 A CN111237272 A CN 111237272A
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- 239000000725 suspension Substances 0.000 title claims abstract description 75
- 230000001360 synchronised effect Effects 0.000 title abstract description 16
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- 239000010720 hydraulic oil Substances 0.000 description 3
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/22—Synchronisation of the movement of two or more servomotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B2013/002—Modular valves, i.e. consisting of an assembly of interchangeable components
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Abstract
The invention discloses a hydraulic control system for synchronous lifting of an oil-gas suspension oil cylinder, which comprises a power unit, an oil inlet oil way, an oil return oil way, a plurality of suspension valve groups and oil cylinders in one-to-one correspondence with the suspension valve groups, wherein the power unit comprises an oil tank, an oil absorption filter, an oil return filter, a gear pump, a motor and a one-way valve, one side inside the oil tank is communicated with one end of the oil inlet oil way, the oil absorption filter, the gear pump and the one-way valve are sequentially arranged on the oil inlet oil way, the gear pump is connected with the motor, the other side inside the oil tank is communicated with one end of the oil return oil way, the oil return oil way is provided with the oil return. Has the advantages that: not only effectively shortens the development period, saves the development cost and enhances the reliability of the system, but also ensures that the system has higher reliability and interchangeability.
Description
Technical Field
The invention relates to the technical field of hydraulic systems, in particular to a hydraulic control system for synchronous lifting of hydro-pneumatic suspension oil cylinders.
Background
Hydro-pneumatic suspension systems, which are composed of an accumulator as a flexible hydraulic element, a suspension cylinder, and a control valve group for controlling the attitude adjustment of the suspension cylinder, are increasingly used in construction vehicles, particularly medium and heavy construction vehicles. The hydro-pneumatic suspension system has excellent nonlinear elastic characteristics and good vibration damping performance, and can meet the requirements of smoothness of engineering vehicles to the maximum extent. Generally, hydro-pneumatic suspension systems have an automatic leveling function, and extend or retract suspension cylinders on a vehicle to the same height position before driving so as to maintain the attitude balance of the vehicle.
The oil-gas suspension system controls each suspension oil cylinder through the control valve group so as to realize posture adjustment of lifting, lowering and the like of the vehicle body. Generally speaking, four points of the left front point, the right front point, the left back point and the right back point are respectively provided with a suspension oil cylinder and a control valve group thereof, and the controller controls an electromagnetic switch in each control valve group according to a certain algorithm by combining the position detection of the oil cylinder, so that the automatic leveling of the vehicle can be realized. In order to continuously improve the performance of a suspension system, people are required to continuously design and research an oil-gas suspension system, however, at present, long time and cost are generally required to be spent in designing and researching the oil-gas suspension system, and meanwhile, the use conditions, general, mature and reliable parts and supporting manufacturers of vehicles are not fully considered in the design process, so that the system cannot be guaranteed to have high reliability and interchangeability.
An effective solution to the problems in the related art has not been proposed yet.
Disclosure of Invention
Technical problem to be solved
Aiming at the defects of the prior art, the invention fully refers to the 6X6 posture control system technology to design an 8X8 type lifting control system, provides a hydraulic control system for synchronous lifting of an oil-gas suspension oil cylinder, and has the advantages of shortening the development period, saving the development cost, enhancing the reliability of the system, ensuring the system to have higher reliability and interchangeability, and further solves the problems in the background technology.
(II) technical scheme
In order to realize the advantages of shortening the development period, saving the development cost, enhancing the reliability of the system and ensuring the system to have higher reliability and interchangeability, the invention adopts the following specific technical scheme:
the utility model provides a hydraulic control system that hydro-pneumatic suspension cylinder goes up and down in step, include power pack, oil feed oil circuit, oil return oil circuit, 8 group hang the valves and with hang 8 groups of hydro-cylinders of valves one-to-one, power pack passes through respectively the oil feed oil circuit with oil return oil circuit and 8 groups hang the valves intercommunication, hang the valves all through first oil circuit with the hydro-cylinder intercommunication.
As preferred, the power unit includes oil tank, oil absorption filter, oil return filter, gear pump, motor and check valve, inside one side of oil tank with the one end intercommunication of oil feed oil circuit, set gradually on the oil feed oil circuit the oil absorption filter the gear pump with the check valve, just the oil absorption filter is located the inside of oil tank, the gear pump with the motor is connected, the inside opposite side of oil tank with the one end intercommunication of oil return oil circuit, be provided with on the oil return oil circuit the oil return filter. The power unit adopts a direct current motor to drive the gear pump, has an independent oil tank, and adopts 4609 combat tank damping liquid as hydraulic oil, so that the system independence is improved, and the faults are reduced.
Preferably, the suspension valve group comprises a three-position four-way electromagnetic proportional reversing valve, a hydraulic control one-way valve and a pressure sensor, an oil inlet P of the three-position four-way electromagnetic proportional reversing valve is communicated with the oil inlet path, an oil return port T of the three-position four-way electromagnetic proportional reversing valve is communicated with the oil return path, a working port a of the three-position four-way electromagnetic proportional reversing valve is communicated with the oil cylinder through a first oil path, the hydraulic control one-way valve and the pressure sensor are sequentially arranged on the first oil path, and a working port B of the three-position four-way electromagnetic proportional reversing valve is communicated with the hydraulic control one-way valve through a fourth oil path. This hang valves improves control accuracy and response speed through adopting the electromagnetism proportional valve group, and the integration has electromagnetism proportional reversing valve, pressure sensor and hydraulically controlled check valve in hanging the valves simultaneously, integrates the degree height, improves the pressure measurement accuracy.
Preferably, the oil tank further comprises a second oil path, one end of the second oil path is communicated with the oil tank, a two-position two-way electromagnetic directional valve is arranged on the second oil path, the other end of the second oil path is communicated with the oil inlet path, and the joint of the second oil path and the oil inlet path is positioned between the check valve and the suspension valve group, and the oil-saving valve further comprises a third oil path, one end of the third oil path is communicated with the second oil path, and the joint of the third oil path and the second oil path is positioned between the two-position two-way electromagnetic directional valve and the oil tank, the other end of the third oil path is communicated with the oil inlet path between the one-way valve and the gear pump, and a reverse flow valve is arranged on the third oil path and between the oil inlet oil path and the second oil path, and the other end of the third oil path is also connected with a pressure gauge. The effect of setting the pressure of the main oil way and unloading can be achieved under the action of the second oil way, the third oil way, the reverse flow valve, the pressure gauge and the two-position two-way electromagnetic directional valve.
Preferably, an air filter is arranged at the top of the oil tank, an oil drainage plug is arranged on one side of the bottom of the oil tank, and a liquid level thermometer is arranged at the top of the oil drainage plug. Through the use of the air filter, the air filter can filter the air in the oil tank, and avoids the phenomenon that the abrasion acceleration of a piston group or an oil cylinder is caused by the suction of dust suspended in the air into the oil cylinder; through the use of liquid level thermometer, the staff of being convenient for knows the liquid level and the temperature of the inside fluid of oil tank.
Preferably, the system further comprises 8-way angular displacement sensors, wherein the angular displacement sensors are respectively arranged on the suspension and used for acquiring the corners of the upper arm and indirectly detecting the height to ground through a one-to-one corresponding conversion relation with the height to ground. Through the use of 8-way angular displacement sensors, the effect of indirectly detecting the distance to the ground can be achieved.
Preferably, the system further comprises a controller box for receiving signals, processing programs and outputting signals, and a touch display screen is arranged on the surface of the controller box. Through the use of the controller box, various signals in the system can be received, output and processed, and transmitted to the meter for display.
(III) advantageous effects
Compared with the prior art, the invention provides a hydraulic control system for synchronous lifting of hydro-pneumatic suspension oil cylinders, which has the following beneficial effects:
(1) through the matched use of the power unit, the oil inlet oil way, the oil return oil way, the 8 groups of suspension valve banks and the 8 groups of oil cylinders, the functions of lifting and descending height adjustment and virtual ground detection can be realized, and the stability of the lifting process is effectively ensured under the combined action of the 8 groups of suspension valve banks and the 8 groups of oil cylinders, so that the hydraulic control system can meet the requirements of railway transportation and normal running of a whole vehicle;
(2) when the hydraulic control system for synchronous lifting of the hydro-pneumatic suspension oil cylinder is developed and designed, the 8X8 type lifting control system can be designed by fully using the 6X6 type attitude control system technology, so that the development period is effectively shortened, the development cost is saved, and the reliability of the system is enhanced;
(3) the hydraulic control system for synchronous lifting of the hydro-pneumatic suspension oil cylinder fully considers the use conditions of vehicles in the design process, adopts universal, mature and reliable parts and matching manufacturers, and accordingly ensures that the system has high reliability and interchangeability.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings needed in the embodiments will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings without creative efforts.
FIG. 1 is a schematic diagram of a hydraulic control system for synchronous lifting of hydro-pneumatic suspension cylinders in accordance with an embodiment of the present invention;
FIG. 2 is a schematic diagram of a power unit in a hydraulic control system for synchronous lifting of hydro-pneumatic suspension cylinders in accordance with an embodiment of the present invention;
FIG. 3 is a schematic diagram of a valve group of a hydraulic control system for synchronously lifting hydro-pneumatic suspension cylinders according to an embodiment of the invention;
FIG. 4 shows a hydraulic control system for synchronous lifting of hydro-pneumatic suspension cylinders according to an embodiment of the invention
FIG. 5 is a schematic diagram of the control system in the hydraulic control system for synchronous lifting of hydro-pneumatic suspension cylinders according to the embodiment of the invention;
FIG. 6 is a functional schematic diagram and a wiring schematic diagram of a hydraulic control system for synchronously lifting hydro-pneumatic suspension cylinders according to an embodiment of the invention;
fig. 7 is a flow chart of a main program in the hydraulic control system for synchronously lifting the hydro-pneumatic suspension cylinders according to the embodiment of the invention.
In the figure:
1. a power unit; 101. an oil tank; 102. an oil absorption filter; 103. an oil return filter; 104. a gear pump; 105. a motor; 106. a one-way valve; 107. a second oil passage; 108. a two-position two-way electromagnetic directional valve; 109. a third oil passage; 110. a reflux valve; 111. a pressure gauge; 112. an air cleaner; 113. oil drainage plug; 114. a liquid level thermometer; 2. an oil inlet path; 3. an oil return path; 4. suspending the valve bank; 401. a three-position four-way electromagnetic proportional reversing valve; 402. a hydraulic control check valve; 403. a pressure sensor; 404. a fourth oil passage; 5. an oil cylinder; 6. a first oil passage.
Detailed Description
For further explanation of the various embodiments, the drawings which form a part of the disclosure and which are incorporated in and constitute a part of this specification, illustrate embodiments and, together with the description, serve to explain the principles of operation of the embodiments, and to enable others of ordinary skill in the art to understand the various embodiments and advantages of the invention, and, by reference to these figures, reference is made to the accompanying drawings, which are not to scale and wherein like reference numerals generally refer to like elements.
According to the embodiment of the invention, a hydraulic control system for synchronous lifting of hydro-pneumatic suspension oil cylinders is provided.
Referring to the drawings and the detailed description, as shown in fig. 1-7, the hydraulic control system for synchronously lifting oil-gas suspension cylinders according to the embodiment of the invention includes a power unit 1, an oil inlet path 2, an oil return path 3, 8 groups of suspension valve banks 4, and 8 groups of cylinders 5 corresponding to the suspension valve banks 4 one by one, wherein the power unit 1 is respectively communicated with a plurality of suspension valve banks 4 through the oil inlet path 2 and the oil return path 3, and the suspension valve banks 4 are respectively communicated with the cylinders 5 through a first oil path 6.
In one embodiment, the power unit 1 includes an oil tank 101, an oil absorption filter 102, an oil return filter 103, a gear pump 104, a motor 105 and a check valve 106, one side of the inside of the oil tank 101 is communicated with one end of an oil inlet path 2, the oil inlet path 2 is sequentially provided with the oil absorption filter 102, the gear pump 104 and the check valve 106, the oil absorption filter 102 is located inside the oil tank 101, the gear pump 104 is connected with the motor 105, the other side of the inside of the oil tank 101 is communicated with one end of an oil return path 3, and the oil return path 3 is provided with the oil return filter 103.
When the power unit is specifically applied, the power unit 1 adopts a direct-current motor to drive a gear pump and is provided with an independent oil tank, 4609 combat tank damping liquid is adopted for hydraulic oil, the system independence is improved, the faults are reduced, the system output pressure is 10MPa, and the output flow is 6.57L/min. The oil tank 101, the oil absorption filter 102, the oil return filter 103, the gear pump 104, the motor 105 and the one-way valve 106 are Heideke hydraulic elements, the motor 105 is a ZD-1500C type 24V/1.5KW direct current motor, the volume of the tank body of the oil tank 101 is 60L, and the oil charge and discharge amount of an oil-gas spring, the temperature rise of the oil tank and the space occupied by other elements are mainly considered.
In one embodiment, the suspension valve group 4 includes a three-position four-way electromagnetic proportional directional valve 401, a hydraulic control one-way valve 402 and a pressure sensor 403, an oil inlet P of the three-position four-way electromagnetic proportional directional valve 401 is communicated with the oil inlet oil path 2, an oil return port T of the three-position four-way electromagnetic proportional directional valve 401 is communicated with the oil return oil path 3, a working port a of the three-position four-way electromagnetic proportional directional valve 401 is communicated with the oil cylinder 5 through the first oil path 6, the hydraulic control one-way valve 402 and the pressure sensor 403 are sequentially arranged on the first oil path 6, the pressure sensor 403 is used for acquiring hydraulic oil pressure in the power cylinder, and a working port B of the three-position four-way electromagnetic proportional directional valve 401 is communicated with the hydraulic control one-way valve 402 through a fourth oil path.
In specific application, 8 groups of suspension valve banks 4 are adopted to be respectively controlled according to system requirements, the valve banks adopt Heideck valves, the model BC509500 is BC, Pmax is 18MPa, Qmax is 24L/min, the protection grade IP65 is IP, and the model is controlled to be 4-20 mADC.
The suspension valve group 4 adopts an electromagnetic proportional valve group, so that the control precision and the response speed are improved, meanwhile, the suspension valve group 4 is dispersedly arranged in each wheel cabin of the vehicle body, the limited space of the vehicle is fully utilized, pipelines are reduced, the system expansibility is strong, and the occupied space is small; the electromagnetic proportional reversing valve module, the pressure sensor module and the hydraulic control one-way valve module are integrated in the suspension valve group 4, the integration degree is high, the pressure measurement accuracy is improved, and the crude oil gas spring hydraulic control one-way valve is eliminated. In addition, the use of 8 sets of pressure sensors 403 in combination with a control program can realize elevation and elevation height adjustment and virtual ground detection.
In one embodiment, the suspension valve assembly further comprises a second oil path 107, one end of the second oil path 107 is communicated with the oil tank 101, a two-position two-way electromagnetic directional valve 108 is arranged on the second oil path 107, the other end of the second oil path 107 is communicated with the oil inlet path 2, and a connection point of the second oil path 107 and the oil inlet path 2 is located between the one-way valve 106 and the suspension valve group 4.
In one embodiment, the oil pump further includes a third oil path 109, one end of the third oil path 109 is communicated with the second oil path 107, a connection point between the third oil path 109 and the second oil path 107 is located between the two-position two-way electromagnetic directional valve 108 and the oil tank 101, the other end of the third oil path 109 is communicated with the oil inlet path 2 between the check valve 106 and the gear pump 104, a reverse flow valve 110 is arranged on the third oil path 109 and between the oil inlet path 2 and the second oil path 107, and the other end of the third oil path 109 is further connected with a pressure gauge 111.
In specific application, the two-position two-way electromagnetic directional valve 108, the reflux valve 110 and the pressure gauge 111 form a pump station valve bank, the pump station valve bank is used for setting main oil way pressure and unloading, and the pressure gauge 111 is used for displaying system pressure and is convenient for pressure setting and timing observation. In addition, the valve group adopts Hedgek valves, model BC509600, Pmax is 10MPa, Qmax is 40L/min, the protection performance grade IP65 and the signal is 24 VDC.
In one embodiment, an air cleaner 112 is arranged at the top of the oil tank 101, an oil drain plug 113 is arranged at one side of the bottom of the oil tank 101, and a liquid level thermometer 114 is arranged at the top of the oil drain plug 113.
In one embodiment, the system further comprises 8-way angular displacement sensors, wherein the angular displacement sensors are respectively arranged on the suspension and used for acquiring the rotation angle of the upper arm and indirectly detecting the ground height through a conversion relation corresponding to the ground height one to one.
In specific application, signals of the angular displacement sensor and the pressure sensor 403 are processed by the controller to participate in feedback control, and are transmitted to the instrument for display. The model of the angular displacement sensor is HAT1236-C01-360L-P01-D106-M01-S2PD-000, the measurement angle is 0-360 ℃, the maximum axial load is less than or equal to 60N, the maximum radial load is less than or equal to 100N, and the precision is as follows: less than or equal to +/-0.05 DEG, working voltage: 9-36V/DC; the pressure sensor 403 is integrated on the suspension valve group 4, the model is HDA 8446-A-0250-: 0-25MPa, output signal: 4-20mA, direct current, power supply mode: 24V.
In one embodiment, the system further comprises a controller box for receiving signals, processing programs and outputting signals, and a touch display screen is arranged on the surface of the controller box.
In specific application, in order to ensure electromagnetic compatibility, the controller box body adopts an all-metal structure, and an aviation plug is selected for outgoing lines so as to shield electromagnetic signals. The analog input signal, the analog output signal and the communication signal of the controller use separate plugs respectively. The controller mainly has the functions of receiving signals, processing programs and outputting signals, and the size of the controller is as small as possible under the condition of meeting the requirements of performance and functions.
The touch display screen is supposed to adopt a touch screen type operation display and is integrated on the controller box. The box body also adopts an all-metal structure and an aviation plug, and the power supply and the CAN communication interface of the instrument respectively use independent plugs. The ground height of each suspension distance and the pressure of the hydro-pneumatic spring are displayed in a digital form, and in addition, a virtual switch is arranged for each operation. The operation interface of the touch display screen is shown in fig. 4.
In addition, the hydraulic control system also includes a control system design.
1) The principle and function of the control system, as shown in fig. 5, are schematic diagrams of the principle of the control system, and according to the requirement of the system on hardware, a controller needs 16 analog input ports to acquire signals of 8 paths of displacement sensors and 8 paths of pressure sensors; 2 switching value output signals control a 1-path motor and a 1-path electromagnetic directional valve; 16 paths of analog signals output 16 paths of signals for controlling 8 electromagnetic proportional valves; in addition, there is 1 way CAN communication interface. The functional diagram and the wiring schematic diagram are shown in fig. 6.
2) The switching value output control part has DC power of 1.5KW, so that the contactor is selected for conversion, the controller outputs switching value to control the coil of the contactor, and the motor power is connected to the contact of the contactor. In addition, one path of electromagnetic directional valve is directly controlled by a switching value output interface of the controller 5A.
3) And the analog quantity output control part is used for controlling the proportional valve by the analog quantity output signal. The analog quantity signal output by the controller is used as the input signal of a proportional amplifier carried by the proportional valve, and the current signal output by the proportional amplifier directly drives the proportional solenoid valve. The proportional amplifiers can respectively control the electromagnet coils, namely the oil circuit of the system can be controlled to be charged and discharged. The proportional amplifier has higher requirement on the quality of the power supply, and the power supply adopts a single stabilized voltage power supply.
4) The cable design, the cable plays the effect of connecting entire system, and the cable of taking the metallic shield layer is all selected for use to the cable, and the cable is different pencil according to heavy current, undercurrent, control scheme, signal line respectively when the design, should also follow this principle when the cable laying.
5) The electromagnetic compatibility design directly influences whether the whole system can work stably and reliably, and the electromagnetic compatibility design is taken as a key point in engineering design. The measures taken can be combined into the following: the controller and the instrument lamp are all of metal structures, an aviation plug is selected for outgoing lines, and the controller and the instrument lamp are designed and separated from a large current, a small current, a control circuit and a signal circuit during cable laying. For outsourcing products, the electromagnetic compatibility performance of the products is controlled by a technical protocol.
In order to facilitate understanding of the above technical solutions of the present invention, the system functions, the operation processes and the control programs of the present invention in the practical process will be described in detail below.
The system functions are as follows: 1) according to the operation division of driver, the vehicle is under quiescent condition (ground is basic level and neglects the temperature rise and to the system influence), and the function that possesses is:
① transportation position-one-click automatic lowering high, lowering the vehicle body from the current position to the upper stopper position, fully bearing the vehicle body by the upper stopper, lowering the vehicle body by 124 + -10 mm relative to the static equilibrium position (i.e. normal driving position), which is 286 + -10 mm above the ground.
② driving position, one-click automatic vehicle height restoring, vehicle body lifting from current position to static balance position, and hydro-pneumatic suspension at static balance position, where the distance from ground is 410 +/-10 mm.
③ scram, one-click automatic stop of current operation, and emergency stop of ascending and descending.
④ Emergency mode is manual mode, in which the hydraulic valve is controlled directly by operation command according to the height requirement of the vehicle body to regulate the suspension of each bridge without signal feedback, and the first, second, third and fourth bridges can be regulated independently or simultaneously.
2) The system is divided according to the functions of the system program, and the system has the functions as follows:
① has automatic and manual lifting functions, automatic is the main one and manual is the auxiliary one, among which, the automatic function is the one-key automatic in-place adjustment, the manual function is the adjustment according to the visual height requirement, it is the emergency function.
② has a 'virtual ground' detection function, because the vehicle is an 8-point suspension support, when a certain suspension naturally hangs down due to the elasticity of hydro-pneumatic spring and self-weight action to cause the tyre to be grounded and the height display is in place, if the suspension is in a pressure deficiency state and is stressed less than the theoretical stress, the suspension has a 'virtual ground' phenomenon, and the pressure is increased after the hydro-pneumatic spring is filled with oil through the detection of a pressure sensor to ensure no virtual ground.
③ has the function of real-time reporting of the pressure of each hydro-pneumatic spring when each suspension distance is high, and the reported data is used for terminal display and program feedback control input.
④ has the function of automatic locking when power is off, the system is locked after power is off, and the vehicle height is kept still.
⑤ has the functions of over-stroke, overload protection and misoperation prevention, and the detection signals of the angular displacement sensors and the pressure sensors are fed back and controlled together.
The working process is as follows: 1) transport position (high descending)
In the operation interface, clicking a 'transport position' key in an automatic area; the motor M105 is electrified, the one-way valve 106 is electrified, the S1 end of the three-position four-way electromagnetic proportional directional valve 401 is electrified and is in the maximum opening degree to reduce the time of the vehicle descending height, when the terminal point is approached, the angular displacement sensor feeds back and adjusts the proper opening degree of the S1 end of the three-position four-way electromagnetic proportional directional valve 401, after the automatic adjustment of the vehicle descending height program is completed, the S1 end of the three-position four-way electromagnetic proportional directional valve 401 is powered off, the one-way valve 106 is powered off, the motor M105 is powered off, and the vehicle descending height is finished.
2) Transport position (high lifting)
In the operation interface, clicking a 'transport position' key in an automatic area; the motor M105 is electrified, the one-way valve 106 is electrified, the S2 end of the two-position two-way electromagnetic directional valve 401 is electrified and is in the maximum opening degree to reduce the vehicle lifting time, when the terminal point is approached, the angular displacement sensor and the pressure sensor feed back and adjust the proper opening degree of the S2 end of the two-position two-way electromagnetic directional valve 401, after the vehicle lifting program is automatically adjusted, the S2 end of the two-position two-way electromagnetic directional valve 401 is powered off, the one-way valve 106 is powered off, the motor M105 is powered off, and the vehicle lifting is in a high junction. .
3) Emergency stop
When the system is in the lifting process, an 'emergency stop' key is clicked in an automatic area of an operation interface, the three-position four-way electromagnetic proportional directional valve 401 is powered off and returns to the middle position, the one-way valve 106 is powered off and returns to the position, and the motor M105 is powered off and stops; when the lifting system is not started, the 'emergency stop' key is directly pressed, and the key is invalid.
4) Starting again after stopping
After the 'emergency stop' key is executed in the lifting process, if the 'automatic lifting'/'middle position' key in the automatic area of the operation interface is clicked again, the lifting system starts to execute unfinished actions until the completion is finished.
5) Moving up and down
In an operation interface, an emergency manual key, a first bridge/second bridge/third bridge/four bridge key, a manual ascending/manual descending key, are sequentially clicked in a manual area; the motor M105 is electrified, the one-way valve 106 is electrified, the three-position four-way electromagnetic proportional directional valve 401 is electrified, and corresponding ascending and descending actions are executed; when the 'stop manual' key is clicked, the three-position four-way electromagnetic proportional directional valve 401 is powered off, the one-way valve 106 is powered off, the motor M105 is powered off, and the current lifting action is finished. In the process, program feedback adjustment is not carried out, and the electromagnetic valve is directly controlled to carry out oil charging and discharging.
6) Display device
And displaying the ground height of each wheel suspension distance and the pressure value of the hydro-pneumatic spring in real time in a display area of an operation interface. The display control box needs to display and operate in real time;
in addition, the information needs to be displayed on the terminal after passing through the CAN bus as follows:
① the method comprises pressing the "transportation position" key to display "transportation position adjustment" during adjustment process, or "transportation position" after adjustment;
② the method comprises pressing a "driving position" key to display "driving position adjustment" during adjustment process, and displaying "driving position" after adjustment;
③ pressing the "scram" key, showing "lifting scram";
④ shows "manually ascending" and "manually descending" when manually ascending and descending, and shows "manually ending" when finishing.
As shown in fig. 7, it is a flow chart of the main program, which adopts a sequence control loop, and mainly consists of an automatic function program and a manual function program. The automatic function program comprises an emergency stop part, a vehicle descending part, a vehicle ascending part and the like; the manual functions comprise three parts of instructions of manual emergency/stop, bridge selection and manual lifting/descending, and the manual lifting and descending functions are realized. The driver inputs corresponding operation instructions and calls each program module.
Automatic lifting and descending procedures: the automatic lifting and descending program comprises four functions of one-key vehicle lifting, vehicle lifting and emergency stop.
Wherein, 1) the car height, rise the car height and adjust the procedure and mainly include the following several parts:
reading a key instruction of a driver, and starting a program;
starting a motor and delaying time;
and (6) carrying out height adjustment. In the initial stage, the proportional valve is in the maximum opening degree; when the target height value approaches the end point, determining the duty ratio by using the deviation of the target height value and the detection value of the sensor, inputting the duty ratio into the corresponding electromagnet, and adjusting the proper opening of the proportional valve;
a "virtual earth" adjustment is performed. After the height adjustment is finished, the vehicle body is parallel to the ground, pressure shortage may occur on a certain wheel at the moment, the duty ratio is determined by the difference between the target pressure value and the detection value of the sensor and input to the oil-gas spring oil-filled electromagnet at the virtual ground point, and only oil filling fine adjustment is carried out to improve the pressure. When the car is lowered to the high height, the detection of 'virtual ground' is not needed, and the car is lowered to the upper limit;
and stopping the motor and ending the program.
2) The flow stopping process mainly comprises the following parts:
when the initial key input instruction of the driver is 'emergency stop', the motor is not started, and the program is not executed;
in the program execution process, when a driver inputs an 'emergency stop' instruction through a key, all the electromagnetic valves are powered off, the motor stops, and the program is ended.
Manual emergency ascending and descending procedures: when the automatic program fails, the proportional valve can be manually and directly controlled to suspend and lift in an emergency, the sensor signal is only used for displaying and does not participate in adjustment, and the lifting height is in accordance with the visual requirement of a driver. The whole vehicle is divided into 4 groups of one, two, three and four bridges, and single bridge or multiple bridges are selected to lift according to requirements.
Wherein, 1) the dynamic emergency rising and falling flow mainly comprises the following parts:
reading in a key instruction of a driver, wherein the key instruction comprises an emergency/stop instruction, a bridge selection instruction, a lifting instruction and a descending instruction, and starting a program;
starting the motor;
directly inputting the duty ratio 1 to a corresponding electromagnet, and fully opening a proportional valve;
when a stop instruction is read in, inputting the duty ratio 0 to all the electromagnets, and returning the proportional valve to the middle position; the electromagnetic valve of the main valve returns to the original position and the motor stops;
and finishing manually.
In conclusion, by means of the technical scheme, the power unit, the oil inlet oil way, the oil return oil way, the 8 groups of suspension valve banks and the 8 groups of oil cylinders are matched for use, so that the functions of lifting and descending height adjustment and virtual ground detection can be realized, and the stability of the lifting process is effectively ensured under the combined action of the 8 groups of suspension valve banks and the 8 groups of oil cylinders, so that the hydraulic control system can meet the requirements of railway transportation and normal running of a whole vehicle; when the hydraulic control system for synchronous lifting of the hydro-pneumatic suspension oil cylinder is developed and designed, the 8X8 type lifting control system can be designed by fully using the 6X6 type attitude control system technology, so that the development period is effectively shortened, the development cost is saved, and the reliability of the system is enhanced; the hydraulic control system for synchronous lifting of the hydro-pneumatic suspension oil cylinder fully considers the use conditions of vehicles in the design process, adopts universal, mature and reliable parts and matching manufacturers, and therefore effectively ensures that the system has high reliability and interchangeability.
The working principle or specific details of the hydraulic control system for synchronous lifting of the hydro-pneumatic suspension oil cylinder are as follows: when the vehicle descends, the controller controls the motor M105 to be powered on, the one-way valve 106 to be powered on, the S1 end of the three-position four-way electromagnetic proportional directional valve 401 to be powered on and at the maximum opening degree to reduce the time of descending the vehicle, when the terminal point is approached, the angular displacement sensor feeds back and adjusts the proper opening degree of the S1 end of the three-position four-way electromagnetic proportional directional valve 401, after the automatic adjustment of the descending vehicle high program is completed, the S1 end of the three-position four-way electromagnetic proportional directional valve 401 is powered off, the one-way valve 106 is powered off, the motor M105 is powered off, and the descending vehicle; when a vehicle rises, the controller controls the motor M105 to be powered on, the one-way valve 106 to be powered on, the S2 end of the two-position two-way electromagnetic directional valve 401 to be powered on and at the maximum opening degree to reduce the vehicle rising time, when the terminal point is approached, the angular displacement sensor and the pressure sensor feed back and adjust the proper opening degree of the S2 end of the two-position two-way electromagnetic directional valve 401, and after the vehicle rising program is automatically adjusted, the S2 end of the two-position two-way electromagnetic directional valve 401 is powered off, the one-way valve 106 is powered off, the motor M105 is powered off, and the vehicle rises to be high.
In the present invention, unless otherwise expressly specified or limited, the terms "mounted," "disposed," "connected," "secured," "screwed" and the like are to be construed broadly, e.g., as meaning fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; the terms may be directly connected or indirectly connected through an intermediate, and may be communication between two elements or interaction relationship between two elements, unless otherwise specifically limited, and the specific meaning of the terms in the present invention will be understood by those skilled in the art according to specific situations.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents, improvements and the like that fall within the spirit and principle of the present invention are intended to be included therein.
Claims (8)
1. The utility model provides a hydraulic control system that hydro-pneumatic suspension hydro-cylinder goes up and down in step, its characterized in that, include power pack (1), oil feed oil circuit (2), oil return oil circuit (3), a plurality of valves (4) that hang and a plurality of hydro-cylinder (5) that hang valves (4) one-to-one, power pack (1) passes through respectively oil feed oil circuit (2) with oil return oil circuit (3) and a plurality of hang valves (4) intercommunication, hang valves (4) all through first oil circuit (6) with hydro-cylinder (5) intercommunication.
2. The hydraulic control system for synchronously lifting an oil-gas suspension oil cylinder according to claim 1, characterized in that the power unit (1) comprises an oil tank (101), an oil absorption filter (102), an oil return filter (103), a gear pump (104), a motor (105) and a one-way valve (106), one side in the oil tank (101) is communicated with one end of the oil inlet channel (2), the oil inlet path (2) is sequentially provided with the oil absorption filter (102), the gear pump (104) and the one-way valve (106), the oil suction filter (102) is positioned inside the oil tank (101), the gear pump (104) is connected with the motor (105), the other side in the oil tank (101) is communicated with one end of the oil return way (3), the oil return filter (103) is arranged on the oil return oil way (3).
3. The hydraulic control system for synchronously lifting an oil-gas suspension oil cylinder according to claim 1, it is characterized in that the suspension valve group (4) comprises a three-position four-way electromagnetic proportional reversing valve (401), a hydraulic control one-way valve (402) and a pressure sensor (403), an oil inlet P of the three-position four-way electromagnetic proportional reversing valve (401) is communicated with the oil inlet channel (2), an oil return port T of the three-position four-way electromagnetic proportional reversing valve (401) is communicated with the oil return oil way (3), the working port A of the three-position four-way electromagnetic proportional reversing valve (401) is communicated with the oil cylinder (5) through the first oil way (6), the first oil path (6) is sequentially provided with the hydraulic control one-way valve (402) and the pressure sensor (403), and a working port B of the three-position four-way electromagnetic proportional directional valve (401) is communicated with the hydraulic control one-way valve (402) through a fourth oil way (404).
4. The hydraulic control system for synchronously lifting oil-gas suspension oil cylinders according to claim 2, characterized by further comprising a second oil path (107), wherein one end of the second oil path (107) is communicated with the oil tank (101), a two-position two-way electromagnetic directional valve (108) is arranged on the second oil path (107), the other end of the second oil path (107) is communicated with the oil inlet path (2), and the joint of the second oil path (107) and the oil inlet path (2) is located between the check valve (106) and the suspension valve group (4).
5. The hydraulic control system for synchronously lifting oil and gas suspension oil cylinders is characterized by further comprising a third oil path (109), one end of the third oil path (109) is communicated with the second oil path (107), the joint of the third oil path (109) and the second oil path (107) is located between the two-position two-way electromagnetic directional valve (108) and the oil tank (101), the other end of the third oil path (109) is communicated with the oil inlet oil path (2) between the one-way valve (106) and the gear pump (104), a backflow valve (110) is arranged on the third oil path (109) and located between the oil inlet oil path (2) and the second oil path (107), and the other end of the third oil path (109) is further connected with a pressure gauge (111).
6. The hydraulic control system for synchronously lifting an oil-gas suspension oil cylinder as claimed in claim 2, wherein an air filter (112) is arranged at the top of the oil tank (101), an oil drain plug (113) is arranged on one side of the bottom of the oil tank (101), and a liquid level thermometer (114) is arranged at the top of the oil drain plug (113).
7. The hydraulic control system for synchronously lifting an oil-gas suspension cylinder as claimed in claim 1, further comprising a plurality of angular displacement sensors, wherein the angular displacement sensors are respectively arranged on the suspension for collecting the rotation angle of the upper arm, and indirectly detecting the height of the ground through a one-to-one correspondence conversion relation with the height of the ground.
8. The hydraulic control system for synchronously lifting an oil-gas suspension oil cylinder according to claim 1, characterized by further comprising a controller box for receiving signals, processing programs and outputting signals, wherein a touch display screen is arranged on the surface of the controller box.
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| CN114893459A (en) * | 2022-04-25 | 2022-08-12 | 阳春新钢铁有限责任公司 | Electrode lifting hydraulic conversion standby system for LF refining furnace |
| CN115366772A (en) * | 2022-08-30 | 2022-11-22 | 龙岩市海德馨汽车有限公司 | An intelligent control system and control method for a landing carriage |
| CN115450968A (en) * | 2022-08-16 | 2022-12-09 | 浙江鼎信航天科技有限公司 | An active hydraulic lifting control system |
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