CN118257899B - Thermal valve electrohydraulic control system and application method - Google Patents
Thermal valve electrohydraulic control system and application method Download PDFInfo
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- CN118257899B CN118257899B CN202410681158.3A CN202410681158A CN118257899B CN 118257899 B CN118257899 B CN 118257899B CN 202410681158 A CN202410681158 A CN 202410681158A CN 118257899 B CN118257899 B CN 118257899B
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- 238000000034 method Methods 0.000 title claims abstract description 52
- 239000003921 oil Substances 0.000 claims abstract description 168
- 230000008569 process Effects 0.000 claims abstract description 35
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 16
- 238000006243 chemical reaction Methods 0.000 claims abstract description 8
- 230000007704 transition Effects 0.000 claims description 13
- 230000001276 controlling effect Effects 0.000 claims description 10
- 230000005611 electricity Effects 0.000 claims description 7
- 238000004891 communication Methods 0.000 claims description 4
- 230000001052 transient effect Effects 0.000 claims description 3
- 230000001105 regulatory effect Effects 0.000 claims description 2
- 238000012360 testing method Methods 0.000 abstract description 7
- 238000010586 diagram Methods 0.000 description 6
- 238000007789 sealing Methods 0.000 description 6
- 230000009471 action Effects 0.000 description 4
- 230000008901 benefit Effects 0.000 description 4
- 238000006073 displacement reaction Methods 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- RZVAJINKPMORJF-UHFFFAOYSA-N Acetaminophen Chemical compound CC(=O)NC1=CC=C(O)C=C1 RZVAJINKPMORJF-UHFFFAOYSA-N 0.000 description 1
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- 238000000418 atomic force spectrum Methods 0.000 description 1
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- 230000001627 detrimental effect Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
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- 230000035939 shock Effects 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
- F16K31/126—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a diaphragm, bellows, or the like
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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
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/025—Pressure reducing valves
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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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
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- Fluid Mechanics (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a thermal valve electrohydraulic control system and an application method thereof, which relate to the field of thermal valve control in wind tunnel tests and comprise an oil cylinder and further comprise the following components: the control module is used for controlling the connection state of the rodless cavity and the rod-containing cavity of the oil cylinder so as to enable the oil cylinder to work in a differential mode or a basic mode; the electromagnetic valve I is used for switching the working mode of the oil cylinder; an electromagnetic valve II and an electromagnetic valve III for executing valve opening and closing operations respectively; and the differential bypass is matched with the control module to regulate the flow of hydraulic oil in the mode switching process. The invention discloses a thermal valve electrohydraulic control system and an application method thereof, wherein a differential-conventional variable structure method is adopted for an oil cylinder according to the characteristic that the reaction force of a medium is gradually increased from small in the closing process of the valve, so that the closing speed of the oil cylinder is improved, the oil consumption of the oil cylinder is reduced, and the valve is loaded at the tail end according to a preset value.
Description
Technical Field
The invention relates to the field of control of a thermal valve in a wind tunnel test. More particularly, the invention relates to a thermal valve electro-hydraulic control system and an application method.
Background
The thermal valve in the wind tunnel test has higher requirements on an electrohydraulic control system: (1) Driving the valve from full open to full close or from full close to full open in the required time; (2) When the electrohydraulic control system drives the valve to be fully closed, the oil cylinder applies loading force to the valve according to test requirements, the valve is damaged due to overlarge valve closing loading force, and the valve cannot be sealed perfectly due to insufficient loading force.
The hot valve driving oil cylinder has larger diameter and long working stroke, and the working pressure of the hydraulic system needs to be kept stable under high pressure, so the electrohydraulic control system needs to be provided with more energy accumulator groups, and the hydraulic pipeline and the control valve also need to have larger diameter to meet the requirement of quick action of the oil cylinder, so the construction cost of the system is higher. The load force of the oil cylinder is a variable load characteristic which is gradually increased in the quick closing process of the driving heat valve, and the hydraulic system sets working pressure and the cylinder diameter of the oil cylinder according to the maximum load, so that the energy consumption of the system is higher. In addition, the electrohydraulic control system also needs to apply accurate thrust control to the output force of the thermal valve oil cylinder in the rapid action, so that the control difficulty of the system is further increased.
In the prior art scheme a shown in fig. 6, the solenoid valve iv 424a for controlling the switch is directly connected with the oil cylinder, and the on/off of the electromagnets on both sides of the solenoid valve iv can directly control the oil cylinder to realize the switch action. When the cylinder is detected to be closed in place, the pressure reducing valve II 36a starts to control the pressure of the rodless cavity of the cylinder, so that the thrust of the cylinder is controlled to meet the requirement of sealing and loading of the heat valve.
In prior art scheme B, shown in fig. 7, a two-stage cylinder scheme with a series combination of a fast stage and a load stage is employed. The quick-stage oil cylinder has smaller piston area, smaller valve closing volume and smaller oil cylinder output force, and is used for quickly closing the valve in the first half of closing the valve of the hot valve; the loading stage has larger piston area and larger output force, and is used for outputting large thrust when the half-path load force is increased after the thermal valve is closed.
When the hot valve is closed, the quick-stage oil cylinder is controlled to be closed quickly through the electromagnetic valve V339 a, the load force is increased gradually along with the pushing of the valve closing process, when the oil cylinder reaches a set position, the electromagnetic valve V339 a controls the loading-stage oil cylinder to feed oil, so that the oil cylinder pushes the hot valve to close the hot valve with larger pushing force, and when the hot valve is closed, the pressure reducing valve III 37a controls the loading-stage oil cylinder, so that the oil cylinder loads the hot valve according to preset pressure, and in order to enable the loading force to have a larger output range, the loading process can enable the quick stage to participate in the control of the loading force as required.
The prior art scheme C: in patent 202210542413.7, a high-flow differential-function hydraulic circuit is proposed. In the circuit, a two-way cartridge valve is controlled through an electromagnetic valve, so that a differential control hydraulic circuit of the oil cylinder is constructed, and when the piston rod of the oil cylinder extends out, the piston rod of the oil cylinder obtains faster action speed and smaller oil inlet amount in a differential oil inlet mode.
For the technical scheme A, the oil consumption is relatively large when the thermal valve is driven to be closed, the lifting speed needs a hydraulic valve group and a pipeline with larger diameter, and more energy accumulator groups are needed to provide hydraulic power, so that the hydraulic valve is only suitable for thermal valve driving control with low load and small caliber.
For the technical scheme B, the structure of the oil cylinder is complex, and the manufacturing difficulty is high. In the valve closing process, hydraulic impact is large when two-stage oil cylinders are switched, and the valve closing speed is discontinuous, so that pneumatic disturbance of a hot valve gas medium can be caused.
For the technical scheme C, the differential loop scheme is simpler, but the conventional-differential scheme is directly switched, no transition process exists, the hydraulic impact is large, the valve closing process speed is discontinuous, and the pneumatic disturbance of a hot valve flowing medium can be caused.
Disclosure of Invention
To achieve these objects and other advantages and in accordance with the purpose of the invention, there is provided a thermal valve electro-hydraulic control system including a cylinder, further including:
The control module is used for controlling the connection state of the rodless cavity and the rod-containing cavity of the oil cylinder so as to enable the oil cylinder to work in a differential mode or a basic mode;
the electromagnetic valve I is used for switching the working mode of the oil cylinder;
an electromagnetic valve II and an electromagnetic valve III for executing valve opening and closing operations respectively;
and the differential bypass is matched with the control module to regulate the flow of hydraulic oil in the mode switching process.
Preferably, the control module includes: the hydraulic control reversing valve I is arranged on the oil supply pipeline and used for switching the communication state of the rodless cavity and the rod cavity;
the hydraulic control reversing valve II is arranged on the oil supply pipeline and used for switching the rod cavity to an oil discharge channel state of oil return;
The hydraulic control reversing valve III and the hydraulic control reversing valve IV are arranged on the oil supply pipeline so that the oil cylinder is quickly positioned at the full-open position of the valve in the valve opening process.
Preferably, the differential bypass includes:
an orifice provided in the oil supply line for restricting the flow rate of hydraulic oil when the differential mode is switched to the basic mode;
And the hydraulic control reversing valve V and the adjustable throttle valve are arranged in the oil supply pipeline and used for returning part of hydraulic oil discharged by the rod cavity in the oil cylinder to the oil tank when the differential mode is switched to the basic mode.
Preferably, the method further comprises: a pressure reducing valve provided in the oil supply line to control the loading force when the thermal valve is fully closed.
Preferably, the method further comprises: and the high-pass shuttle valve is arranged in the oil supply pipeline and used for controlling the output of the higher one of the system pressure and the pressure of the rod cavity of the oil cylinder.
The application method of the electro-hydraulic control system of the thermal valve is based on the characteristic that the reaction force of a medium is gradually increased from small in the valve closing process, the oil cylinder works in a mode of combining a basic mode and a differential mode so as to regulate and control the closing speed of the oil cylinder, and the oil cylinder is converted into a loading mode after the valve is closed in place;
in the valve opening process, the oil cylinder works in a basic mode.
Preferably, during switching of the basic mode and the differential mode, the hydraulic flow during switching of the modes is regulated by a differential bypass in the thermo-valve electro-hydraulic control system.
Preferably, the valve closing process is configured to include:
When the valve closing operation is executed, the electromagnetic valve I is electrified, the control port of the hydraulic control reversing valve I is low-pressure, the working port of the hydraulic control reversing valve I is conducted, and the two cavities of the oil cylinder are in a communication state; meanwhile, the control port of the hydraulic control reversing valve II is high-pressure, the working port of the hydraulic control reversing valve II is closed, so that an oil discharge channel from a rod cavity of the oil cylinder to oil return is cut off, and the oil cylinder is in a differential mode;
when the conversion condition is met, the electromagnetic valve I loses electricity, the control port of the hydraulic control reversing valve I is high-pressure, the working port of the hydraulic control reversing valve I is cut off, and two cavities of the oil cylinder are not communicated, so that the oil cylinder is in a basic mode.
Preferably, in the process of converting the differential mode to the basic mode, the workflow of the differential bypass includes:
when the electromagnetic valve I is powered on, the hydraulic control reversing valve V is switched on before the hydraulic control reversing valve II is switched on and the hydraulic control reversing valve I is switched off based on the delay of the throttling hole;
After the hydraulic control reversing valve V is conducted, a part of hydraulic oil discharged by the rod cavity of the oil cylinder continues to the differential state and enters the rodless cavity of the oil cylinder, and the rest part of hydraulic oil returns to the oil tank through the throttle valve and the hydraulic control reversing valve V so as to form a transient transition state between the differential mode and the basic mode;
After the hydraulic control reversing valve II is switched on and the hydraulic control reversing valve I is switched off, the oil cylinder completely enters a basic mode.
Preferably, the valve opening process is configured to include:
The oil cylinder in the valve opening process works in a basic mode, when the valve is opened, the electromagnetic valve III and the electromagnetic valve I which bear the valve closing task lose electricity, and the pressure reducing valve is also in a forbidden state;
The electromagnetic valve II is powered on, the control ports of the hydraulic control reversing valve III and the hydraulic control reversing valve IV are in low pressure, and the working ports are communicated, so that hydraulic oil enters a rod cavity of the oil cylinder to push the piston to be lifted quickly;
when the valve is at the full-open position, the electromagnetic valve II is controlled to lose electricity based on the position feedback signal, and the working ports of the hydraulic control reversing valve III and the hydraulic control reversing valve IV are cut off, so that the oil cylinder is kept at the full-open position of the valve.
The invention at least comprises the following beneficial effects: the invention provides an electrohydraulic control system method, which adopts a differential-conventional structure-changing method for an oil cylinder according to the characteristic that the reaction force of a medium is gradually increased from small in the closing process of the valve, improves the closing speed of the oil cylinder, reduces the oil consumption of the oil cylinder, and loads the valve at the tail end according to a preset value.
Additional advantages, objects, and features of the invention will be set forth in part in the description which follows and in part will become apparent to those having ordinary skill in the art upon examination of the following or may be learned from practice of the invention.
Drawings
FIG. 1 is a hydraulic schematic of an electro-hydraulic control system of the present invention;
FIG. 2 is a basic mode operation schematic of the cylinder of the present invention;
FIG. 3 is a schematic diagram of the differential mode operation of the cylinder of the present invention;
FIG. 4 is a schematic diagram of the matching of cylinder thrust and load force during valve closing according to the present invention;
FIG. 5 is a schematic diagram of a control flow of the valve of the present invention;
FIG. 6 is a hydraulic schematic diagram of prior art scheme A;
FIG. 7 is a hydraulic schematic diagram of prior art scheme B;
The hydraulic control system comprises an oil cylinder-1, a hydraulic control reversing valve VI-911A, a hydraulic control reversing valve II-911B, a hydraulic control reversing valve III-911C, a hydraulic control reversing valve IV-911D, a hydraulic control reversing valve I-911E, a hydraulic control reversing valve V-911F, a hydraulic control reversing valve VII-453, a solenoid valve III-399A, a solenoid valve II-399B, a solenoid valve I-424, a displacement sensor-292, a control valve-124A, a pressure reducing valve I-36, an orifice-20, an adjustable throttle valve-276, a high-pass shuttle valve-106, a solenoid valve IV-424A, a pressure reducing valve II-36 a, a solenoid valve V-339A and a pressure reducing valve III-37 a.
Detailed Description
The present invention is described in further detail below with reference to the drawings to enable those skilled in the art to practice the invention by referring to the description.
The invention designs an electrohydraulic control system, which mainly enables an oil cylinder to work in a combination mode of a basic mode and a differential mode in the valve closing process, and the valve is turned into a loading mode after being closed in place. The three modes are organically combined to better realize multiple targets of high valve closing speed, oil consumption saving, small hydraulic pressure fluctuation and safe loading.
Fig. 2-3 (solid lines show oil feed direction and broken lines show oil feed direction) illustrate basic and differential modes of operation of a cylinder in an electro-hydraulic control system as referred to herein, wherein the basic mode of operation of the cylinder is the most common mode of operation, with one chamber of the cylinder feeding oil and the other chamber discharging oil, and the cylinder rod is thus extendable or retractable. The differential mode of the oil cylinder is to connect the oil ports of the two cavities and then connect the oil ports with pressure oil. When pressure oil is introduced, the two cavities have the same pressure, but the area of the rodless cavity is larger than that of the rod cavity, so that the hydraulic pressure of the rodless cavity is larger than that of the rod cavity, the piston moves towards the rod cavity after overcoming friction force, and the piston rod extends out.
Differential feature 1: the cylinder piston only has one movement direction from the rodless chamber to the rod-bearing chamber in the differential mode.
Differential feature 2: when the cylinder piston moves from the rodless cavity to the rod cavity, the volume of pressure oil entering the cylinder in a differential mode is equal to the volume of the piston extending out. Therefore, the oil feed amount of the differential mode cylinder is smaller than that of the base mode.
Differential feature 3: in the differential mode, the acting area of hydraulic oil on the piston is equal to the sectional area of the piston rod, so that the thrust of the oil cylinder in the differential mode is smaller.
The working principle of the electrohydraulic control system of the present invention is described in detail below:
(1) The cylinder valve-closing adopts a working mode of combining a differential mode and a basic mode
The invention adopts a combined working mode of a differential mode and a basic mode in the valve closing process. When the thermal valve moves from the full open state to the closed state, the front section oil cylinder works in a differential mode, and the rear section is converted into a basic mode. The valve opening process cylinder operates in a basic mode.
As shown in fig. 4 (in the figure, the origin of coordinates where a is located indicates that the valve is fully opened, the ordinate where B is located indicates that the valve is fully closed, the abscissa where C is located indicates that the cylinder thrust corresponding to the load force is provided, D indicates the load force curve, E indicates the differential mode, F indicates the basic mode, G indicates the seal loading), the load force of the thermal valve is mainly the friction force at the initial stage of closing the valve, and the required cylinder thrust is small, which coincides with the above feature 3. The advantage of using differential mode is that feature 2, i.e. less oil is used, and thus faster speed, the pressure fluctuations of the accumulator are also significantly reduced. With the valve closing process, the acting force of the high-pressure gas medium on the driving mechanism is gradually increased, the oil cylinder is required to have higher output force, the electrohydraulic control system selects the engine to change the oil cylinder into a basic mode, the output thrust can be greatly improved, and the thrust requirement of valve closing is met.
At the end of the valve closing stroke, the oil cylinder is controlled by the pressure reducing valve, so that the output thrust of the oil cylinder is limited, and the valve is protected from being damaged while the sealing of the valve is ensured.
The control scheme has the advantages that the differential mode is adopted at the initial stage of valve closing to reduce the oil consumption for valve closing and accelerate the valve closing speed, and further, the working pressure of the accumulator group falls less because of the reduction of the oil consumption, so that the pressure output is more stable. And at the rear section of the valve closing, if the output force of the differential mode is insufficient, the differential mode is changed into a basic mode, and the output thrust is increased to smoothly complete the valve closing process. When the closing valve is closed, the valve is converted into a loading mode, the output thrust of the oil cylinder is limited through the pressure reducing valve, the sealing of the valve is ensured, and overload damage is avoided.
Fig. 1 is a hydraulic schematic diagram of an electrohydraulic control system of the present invention, in which a pilot operated directional control valve vii 453 is connected in series with a solenoid valve iii 399A to control on/off of a pilot operated directional control valve ii 911B, a displacement sensor 292 is used to detect the position of an oil cylinder 1 (the arrow on the right side of the oil cylinder 1 indicates the valve closing direction), a control valve 124A is used to prevent high pressure oil from being directly discharged from the pilot operated directional control valve ii 911B in the process of switching from differential to basic mode, the solenoid valve iii 399A is used to execute the control of the valve closing, the solenoid valve ii 399B is used to execute the control of the valve opening, the solenoid valve i 424 is the control solenoid valve of the oil cylinder differential mode and the basic mode, and a pressure reducing valve i 36 is used for controlling the loading force when the thermal valve is fully closed, so as to ensure that the thermal valve has sufficient sealing specific pressure, and at the same time, the output force is limited too large to protect the thermal valve sealing surface. The hydraulic control reversing valve is provided with a pilot control port and two working ports, the two working ports are cut off when the pilot port pressure is high, the two working ports are conducted when the pilot port pressure is low, wherein the hydraulic control reversing valve VI 911A is used for controlling the on-off of pressure oil to a rodless cavity oil way of an oil cylinder when the valve is closed, the hydraulic control reversing valve II 911B is used for controlling the on-off of the oil cylinder rod cavity to an oil return channel oil discharge oil way when the valve is closed, the hydraulic control reversing valve III 911C is used for controlling the on-off of pressure oil to the rodless cavity oil way when the valve is opened, the hydraulic control reversing valve IV 911D is used for controlling the on-off of the rodless cavity to the oil return channel when the valve is opened, and the hydraulic control reversing valve I911E is used for communicating the on-off of two cavities of the oil cylinder in the valve closing and is in a differential mode and a basic mode for closing the valve.
Wherein the pilot operated directional valve V911F is used to form a differential bypass with the orifice 20 and the adjustable throttle 276. The high-pass shuttle valve 106 takes the higher of the system pressure and the pressure of the rod cavity of the oil cylinder as output, so that the reliability of each hydraulic control reversing valve in the cut-off process is ensured.
(2) Control of oil cylinder working mode in valve closing process
As shown in fig. 5, the control flow of the valve includes:
1) After the valve is closed, the electromagnetic valve I424 is powered on, the control port of the hydraulic control reversing valve I911E is low-pressure, the working port of the hydraulic control reversing valve I911E is conducted, and the two cavities of the oil cylinder are in a communicating state; meanwhile, the control port of the hydraulic control reversing valve II 911B is high-pressure, the working port of the hydraulic control reversing valve II 911B is closed, so that an oil discharge channel from a rod cavity of the oil cylinder to oil return is cut off, and the oil cylinder is in a differential mode.
2) When the conversion condition is satisfied (the conversion condition herein means: when the hydraulic control reversing valve I911E reaches a preset position, the speed is reduced to a certain degree, the pressure of the rodless cavity of the oil cylinder is increased to any one of the preset degrees to be used as a judging condition for judging whether the mode is switched or not, the electromagnetic valve I424 is powered off, the control port of the hydraulic control reversing valve I911E is high-pressure, the working port of the hydraulic control reversing valve I911E is cut off, and the two cavities of the oil cylinder are not communicated to be in a basic working mode.
3) If the above-described transition is accomplished instantaneously without a gradual transition, hydraulic flow transients may result in hydraulic hammer impacts within the hydraulic system, which are extremely detrimental to hydraulic lines and components. In addition, the abrupt change of the oil cylinder speed can also cause abnormal disturbance of a gas medium, and has adverse effects on test conditions. To this end, the invention provides an adjustable flow differential bypass, which is formed by pilot operated directional valve V911F and adjustable throttle valve 276. When the electromagnetic valve I424 is powered on, the hydraulic control reversing valve V911F is turned on before the hydraulic control reversing valve II 911B is turned on and the hydraulic control reversing valve I911E is turned off due to the delay action of the throttle hole 20. After the hydraulic control reversing valve V911F is conducted, the hydraulic oil is discharged from the rod cavity of the oil cylinder: a portion continues the differential state into the cylinder rodless chamber and the remaining portion is returned to the tank by the adjustable throttle 276 and the pilot operated directional valve v 911F, thus creating a transient transition state (between differential mode and base mode). Then the hydraulic control reversing valve II 911B is conducted and the hydraulic control reversing valve I911E is cut off, so that the oil cylinder completely enters the basic mode. Since a transition between the differential mode and the basic mode occurs during mode transition, the hydraulic shock of the transition is greatly reduced. The purpose of the adjustable throttle 276 is to properly distribute the flow during the transition to achieve the desired transition.
In the valve closing process of the scheme, the oil cylinder works in a combination mode of a basic mode and a differential mode, and the valve is turned into a loading mode after being closed in place. And the loading mode is that after the oil cylinder drives the thermal valve to a position close to the full closing position (the position can be set), the pressure reducing valve I36 outputs according to the preset pressure, then the electromagnetic valve III 399A is powered off to close the quick closing valve channel, and finally the oil cylinder closes the valve by the preset thrust to seal the valve without damaging the sealing structure of the valve.
The three modes are organically combined to better realize multiple targets of high valve closing speed, oil consumption saving, small hydraulic pressure fluctuation and safe loading.
Furthermore, the bypass channel with adjustable flow rate is added in the differential mode, so that hydraulic impact is reduced when the valve is switched from differential mode to basic mode, test equipment is protected, and the test is more stable.
(3) Load control of shut-off valve tip
The cylinder has a buffer structure at the end of closing valve (the position connection relation is not described in the prior art), which can slow down the pushing speed at the end of closing valve stroke of the cylinder and protect the valve from violent impact. In addition, the speed of the tail end of the oil cylinder is reduced, sufficient adjusting time is provided for loading control of the oil cylinder, and the buffer of the tail end of the oil cylinder not only gives consideration to the speed reduction of the tail end of the oil cylinder to protect the valve from being impacted, but also adds in-place identification of the tail end loading.
When the displacement sensor on the oil cylinder detects (belongs to the prior art and the position connection relation is not described) to the set position of the end loading, the pressure output is controlled by the pressure reducing valve I36, meanwhile, the electromagnetic valve III 399A is powered off, and the residual stroke and the output force are controlled by the pressure reducing valve I36.
(4) Control of valve opening process
The cylinder in the valve opening process works in a basic mode.
When the valve is opened, the solenoid valve III 399A and the solenoid valve I424 which bear the valve closing task are powered off, and the pressure reducing valve I36 is also placed in a forbidden state. The valve opening electromagnetic valve II 399B is powered up, so that the control ports of the hydraulic control reversing valve III 911C and the hydraulic control reversing valve IV 911D are low in pressure, the working ports of the two valves are conducted, hydraulic oil enters a rod cavity of an oil cylinder to push a piston to rapidly lift, when the valve is fully opened, the electromagnetic valve II 399B is controlled to lose electricity according to a position feedback signal, the working ports of the hydraulic control reversing valve III 911C and the hydraulic control reversing valve IV 911D are cut off, and the oil cylinder is kept at the valve fully opened position.
It should be further noted that the adjustable throttle valve 276 of the present invention may also achieve a more smooth stepless transition control through the use of electro-hydraulic proportional valves or electro-hydraulic servo valves.
The hydraulic control reversing valve is an oil way switch control element, and other switch elements such as a two-way cartridge valve, a hydraulic control one-way valve and the like can be used for replacing the hydraulic control reversing valve.
In addition, the pressure reducing valve can be manually adjusted or an electrohydraulic proportional pressure reducing valve.
The above is merely illustrative of a preferred embodiment, but is not limited thereto. In practicing the present invention, appropriate substitutions and/or modifications may be made according to the needs of the user.
The number of equipment and the scale of processing described herein are intended to simplify the description of the present invention. Applications, modifications and variations of the present invention will be readily apparent to those skilled in the art.
Although embodiments of the invention have been disclosed above, they are not limited to the use listed in the specification and embodiments. It can be applied to various fields suitable for the present invention. Additional modifications will readily occur to those skilled in the art. Therefore, the invention is not to be limited to the specific details and illustrations shown and described herein, without departing from the general concepts defined in the claims and their equivalents.
Claims (8)
1. The utility model provides a hot valve electrohydraulic control system, includes the hydro-cylinder, its characterized in that still includes:
The control module is used for controlling the connection state of the rodless cavity and the rod-containing cavity of the oil cylinder so as to enable the oil cylinder to work in a differential mode or a basic mode;
the electromagnetic valve I is used for switching the working mode of the oil cylinder;
an electromagnetic valve II and an electromagnetic valve III for executing valve opening and closing operations respectively;
a differential bypass matched with the control module to regulate the flow of hydraulic oil in the mode switching process;
The control module includes: the hydraulic control reversing valve I is arranged on the oil supply pipeline and used for switching the communication state of the rodless cavity and the rod cavity;
the hydraulic control reversing valve II is arranged on the oil supply pipeline and used for switching the rod cavity to an oil discharge channel state of oil return;
the hydraulic control reversing valve III and the hydraulic control reversing valve IV are arranged on the oil supply pipeline so that the oil cylinder is rapidly positioned at the full-open position of the valve in the valve opening process;
The differential bypass includes:
The throttle is arranged in the oil supply pipeline and used for limiting the flow of hydraulic oil when the differential mode is switched to the basic mode, so that the hydraulic control reversing valve V is switched on before the hydraulic control reversing valve II is switched on and the hydraulic control reversing valve I is switched off;
And the hydraulic control reversing valve V and the adjustable throttle valve are arranged in the oil supply pipeline and used for returning part of hydraulic oil discharged by the rod cavity in the oil cylinder to the oil tank when the differential mode is switched to the basic mode.
2. The thermal valve electro-hydraulic control system of claim 1, further comprising: a pressure reducing valve provided in the oil supply line to control the loading force when the thermal valve is fully closed.
3. The thermal valve electro-hydraulic control system of claim 1, further comprising: and the high-pass shuttle valve is arranged in the oil supply pipeline and used for controlling the output of the higher one of the system pressure and the pressure of the rod cavity of the oil cylinder.
4. An application method of a thermal valve electrohydraulic control system according to any one of claims 1 to 3, characterized in that based on the characteristic that the reaction force of a medium is gradually increased from small in the valve closing process, the oil cylinder works in a mode of combining a basic mode and a differential mode in the valve closing process to regulate the closing speed of the oil cylinder, and the oil cylinder is converted into a loading mode after the valve is closed in place;
in the valve opening process, the oil cylinder works in a basic mode.
5. The method of claim 4, wherein the hydraulic flow rate during the switching of the mode is regulated by a differential bypass in the electro-hydraulic thermal valve control system during the switching of the base mode and the differential mode.
6. The method of claim 4, wherein the valve closing process is configured to include:
When the valve closing operation is executed, the electromagnetic valve I is electrified, the control port of the hydraulic control reversing valve I is low-pressure, the working port of the hydraulic control reversing valve I is conducted, and the two cavities of the oil cylinder are in a communication state; meanwhile, the control port of the hydraulic control reversing valve II is high-pressure, the working port of the hydraulic control reversing valve II is closed, so that an oil discharge channel from a rod cavity of the oil cylinder to oil return is cut off, and the oil cylinder is in a differential mode;
when the conversion condition is met, the electromagnetic valve I loses electricity, the control port of the hydraulic control reversing valve I is high-pressure, the working port of the hydraulic control reversing valve I is cut off, and two cavities of the oil cylinder are not communicated, so that the oil cylinder is in a basic mode.
7. The method of claim 6, wherein the workflow of the differential bypass during the transition from the differential mode to the base mode comprises:
when the electromagnetic valve I is powered on, the hydraulic control reversing valve V is switched on before the hydraulic control reversing valve II is switched on and the hydraulic control reversing valve I is switched off based on the delay of the throttling hole;
After the hydraulic control reversing valve V is conducted, a part of hydraulic oil discharged by the rod cavity of the oil cylinder continues to the differential state and enters the rodless cavity of the oil cylinder, and the rest part of hydraulic oil returns to the oil tank through the throttle valve and the hydraulic control reversing valve V so as to form a transient transition state between the differential mode and the basic mode;
After the hydraulic control reversing valve II is switched on and the hydraulic control reversing valve I is switched off, the oil cylinder completely enters a basic mode.
8. The method of claim 4, wherein the valve opening procedure is configured to include:
The oil cylinder in the valve opening process works in a basic mode, when the valve is opened, the electromagnetic valve III and the electromagnetic valve I which bear the valve closing task lose electricity, and the pressure reducing valve is also in a forbidden state;
The electromagnetic valve II is powered on, the control ports of the hydraulic control reversing valve III and the hydraulic control reversing valve IV are in low pressure, and the working ports are communicated, so that hydraulic oil enters a rod cavity of the oil cylinder to push the piston to be lifted quickly;
when the valve is at the full-open position, the electromagnetic valve II is controlled to lose electricity based on the position feedback signal, and the working ports of the hydraulic control reversing valve III and the hydraulic control reversing valve IV are cut off, so that the oil cylinder is kept at the full-open position of the valve.
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| AT242459B (en) * | 1962-11-24 | 1965-09-27 | Teves Kg Alfred | Current regulator |
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| IN171213B (en) * | 1988-01-27 | 1992-08-15 | Hitachi Construction Machinery | |
| AT505724B1 (en) * | 2007-09-12 | 2010-06-15 | Trumpf Maschinen Austria Gmbh | DRIVE DEVICE FOR A BEND PRESS |
| CN103448293B (en) * | 2013-03-09 | 2015-07-08 | 虔东稀土集团股份有限公司 | Powder press hydraulic system |
| CN108843630B (en) * | 2018-07-23 | 2024-02-02 | 中国重型机械研究院股份公司 | Position and pressure continuously adjustable driving roller depressing hydraulic control system |
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