CN108869437B - Electromechanical static pressure control unit for ship - Google Patents
Electromechanical static pressure control unit for ship Download PDFInfo
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- CN108869437B CN108869437B CN201810957470.5A CN201810957470A CN108869437B CN 108869437 B CN108869437 B CN 108869437B CN 201810957470 A CN201810957470 A CN 201810957470A CN 108869437 B CN108869437 B CN 108869437B
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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
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
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Abstract
The utility model provides a naval vessel is with electromechanical static pressure control unit for control naval vessel steering wheel work, includes: the first EHA integrated valve group, the second EHA integrated valve group and the manual emergency valve group; the first EHA integrated valve group and the second EHA integrated valve group are redundant and backup with each other, and control a first hydraulic cylinder and a second hydraulic cylinder on a ship to work; the manual emergency valve group is used for controlling the first hydraulic cylinder and the second hydraulic cylinder to work in an emergency mode, exhausting and filling the first EHA integrated valve group and the second EHA integrated valve group and supplementing hydraulic oil to the first EHA integrated valve group or the second EHA integrated valve group. The steering engine controlled by the control unit on the ship has obvious technical advantages, and can replace hydraulic energy and a pipeline system which need frequent maintenance, reduce personnel allocation on the ship, effectively improve reliability and greatly reduce vibration noise generated by the hydraulic system.
Description
Technical Field
The invention relates to an electromechanical static pressure control unit for a ship, and belongs to the technical field of ship steering engine control.
Background
The prior ship steering device in China adopts a valve control hydraulic system, adjusts the flow of the hydraulic system entering an actuator by changing the size of a valve port of a servo valve, and controls the speed and displacement of a hydraulic cylinder to obtain the rotating speed and the working angle required by the steering device. However, due to the inherent structural limitation of the servo valve, the servo valve has a plurality of insurmountable problems:
1. the servo valves have high demands on the hydraulic oil. Oil pollution in work easily abrades the servo valve, and the working reliability is reduced. This requires an increase in oil filtration technology, which increases costs.
2. The valve control system needs a set of constant pressure oil source, so that the space and complexity of the system are increased, the cost of the system is increased, and the application of the system in special application places with small installation space, such as ships and warships, is limited.
3. The servo valve of the valve control system provides a maximum load pressure of only two thirds of the pressure of the oil source, which makes a large amount of system energy inefficient.
4. The valve control system has serious energy loss, large throttling heating and low efficiency.
5. The servo valve has high processing precision and is inconvenient to maintain.
Disclosure of Invention
The invention aims to: the electromechanical static pressure control unit for the ship realizes three-redundancy switching, automatic oil supplement and closed system exhaust and filling, and has the characteristics of small volume, light weight, high efficiency, low energy consumption and high reliability; personnel allocation on the ship can be reduced, reliability can be effectively improved, and vibration noise generated by a hydraulic system is greatly reduced.
The purpose of the invention is realized by the following technical scheme:
the utility model provides a naval vessel is with electromechanical static pressure control unit for control naval vessel steering wheel work, includes: the first EHA integrated valve group, the second EHA integrated valve group and the manual emergency valve group;
the first EHA integrated valve group and the second EHA integrated valve group are redundant and backup for each other, a first hydraulic cylinder and a second hydraulic cylinder on a control ship work, and the manual emergency valve group is used for emergency control of the first hydraulic cylinder and the second hydraulic cylinder, exhaust filling of the first EHA integrated valve group and the second EHA integrated valve group, and hydraulic oil supplement of the first EHA integrated valve group or the second EHA integrated valve group.
When the first EHA integrated valve group and the second EHA integrated valve group work normally at the same time, the first EHA integrated valve group and the second EHA integrated valve group control the first hydraulic cylinder and the second hydraulic cylinder on the ship to work together.
When the first EHA integrated valve group or the second EHA integrated valve group only has a group of normal work, the first hydraulic cylinder and the second hydraulic cylinder on the ship are controlled to work through the first EHA integrated valve group or the second EHA integrated valve group which normally work.
When the first EHA integrated valve group and the second EHA integrated valve group can not work normally, the first hydraulic cylinder and the second hydraulic cylinder on the ship are controlled to work by switching to the manual emergency valve group.
The first hydraulic cylinder and the second hydraulic cylinder work simultaneously or work independently, a rod cavity of the first hydraulic cylinder is communicated with a rodless cavity of the second hydraulic cylinder, and the rodless cavity of the first hydraulic cylinder is communicated with a rod cavity of the second hydraulic cylinder.
The first EHA integrated valve group and the second EHA integrated valve group have the same structure and respectively comprise a screw pump, a servo motor, an oil supplementing one-way valve, an electromagnetic locking valve, a self-pressurization oil tank, a charging connector, a high-pressure safety valve, a manual bypass valve and a differential pressure sensor;
the servo motor drives the screw pump to work, and the flow and the direction output by the screw pump are changed by changing the rotating speed and the steering direction of the servo motor; the oil-supplementing check valve is used for supplementing oil for the screw pump,
the self-pressurization oil tank compensates leakage of the EHA integrated valve group and provides back pressure for the EHA integrated valve group, so that air pockets are prevented from being generated; the charging connector is used for controlling the pressure of the self-pressurization oil tank,
the high-pressure safety valve is opened for unloading when the pressure of the EHA integrated valve group exceeds the allowable pressure, so that the highest pressure is limited; the manual bypass valve is opened during exhaust and filling, and is communicated with the whole hydraulic loop; the pressure difference sensor is used for monitoring the pressure difference between two cavities of the hydraulic cylinder, and the electromagnetic locking valve is used for controlling the connection or disconnection of the EHA integrated valve group and an external oil way.
The first EHA manifold block and the second EHA manifold block structure further include: the oil filter assembly, the low-pressure safety valve, the low-pressure sensor and the temperature sensor are arranged on the oil filter assembly;
the oil filter assembly is used for filtering an oil circuit of the EHA integrated valve group, the low-pressure sensor monitors the pressure of the self-pressurization oil tank, the low-pressure safety valve is used for opening unloading when the pressure of the self-pressurization oil tank exceeds the allowable pressure, and the temperature sensor monitors the temperature of the self-pressurization oil tank.
The manual emergency valve group comprises an open oil tank, a hydraulic control one-way valve, a first leakage-free electromagnetic locking valve, a manual stop valve, a manual hydraulic pump, an electric oil supplementing pump, a manual control module and an oil supplementing and filling module;
the open oil tank stores working media and provides hydraulic oil for a manual hydraulic pump and an electric oil supplementing pump, the manual hydraulic pump realizes control over a hydraulic cylinder through a manual control module, and the electric oil supplementing pump realizes oil supplementing and filling of the EHA integrated valve group through an oil supplementing and filling module; the hydraulic control one-way valve is used for discharging redundant hydraulic oil of the asymmetric hydraulic cylinder, and the redundant hydraulic oil enters the open oil tank; the first non-leakage electromagnetic locking valve and the manual stop valve are used for controlling the connection and disconnection between the first hydraulic cylinder and the second hydraulic cylinder.
The manual control module comprises a manual reversing valve, a manual leakage-free locking valve and a hydraulic locking valve; the manual leakage-free locking valve is used for controlling the on-off of an oil path between the open oil tank and the hydraulic cylinder, the manual reversing valve is used for controlling hydraulic oil output by the manual hydraulic pump to enter a rod cavity or a rodless cavity of the hydraulic cylinder, and the hydraulic locking valve is used for locking the hydraulic cylinder.
The oil supplementing and filling module comprises a second non-leakage electromagnetic locking valve, an electromagnetic bypass valve, an overflow valve, a hydraulic control non-leakage locking valve, an electromagnetic directional valve, a first one-way valve, a manual control high-pressure safety valve and a second one-way valve;
the overflow valve is used for adjusting the output pressure of the electric oil supplementing pump, the first check valve is arranged at the outlet of the electric oil supplementing pump and used for preventing oil from flowing backwards, the electromagnetic directional valve is used for controlling the opening and closing of the hydraulic control leakage-free locking valve, the hydraulic control leakage-free locking valve is used for controlling the on-off of an oil path between the open oil tank and the EHA integrated valve group, and the second check valve is used for isolating the hydraulic control check valve from the electric oil supplementing pump; the manual control high-pressure safety valve is used for opening unloading when the pressure of the manual emergency valve bank exceeds the allowable pressure,
the electromagnetic bypass valve is used for communicating two cavities of the hydraulic cylinder with the open oil tank, and the second non-leakage electromagnetic locking valve is used for isolating the self-pressurization oil tank.
Compared with the prior art, the invention has the following advantages:
(1) the invention adopts a three-redundancy design: the configuration of three redundancies of a double EHA integrated valve group and a manual emergency valve group is adopted. The fault isolation can be realized under multiple fault modes such as single EHA integrated valve group fault, double EHA integrated valve group fault, single hydraulic cylinder fault and the like, and the steering capability is ensured.
(2) The invention realizes the automatic oil supplementing technology of the closed system. When the closed system works for a long time, the liquid level in the system can be gradually reduced because the outward micro leakage of the movable sealing part can not be avoided. In order to avoid the influence of too low liquid level on the oil absorption performance of the pump, an electric oil supplementing pump is designed to automatically supplement oil for a closed system. The method can thoroughly solve the problem of oil supplement of the closed system of the electromechanical static pressure hydraulic cylinder in the application of the closed system and the continuous operation of ships and warships for a long time, has automatic oil supplement, and can effectively improve the reliability of the EHA closed system.
(3) The invention realizes the free control switching between the symmetrical cylinder and the asymmetrical cylinder. The EHA is a closed system, and the oil discharge amount and the oil return amount of a motor pump are theoretically equal, so that an asymmetric cylinder cannot be controlled; in order to solve the problem, a hydraulic control one-way valve element is added, when the asymmetric cylinder retracts, the hydraulic control one-way valve is opened, redundant hydraulic oil flows into a pressurization oil tank, and free switching of the EHA closed system to control the symmetric cylinder and the asymmetric cylinder is achieved.
(4) The invention realizes the exhaust and filling of the closed system, and in consideration of the maintainability of the system, after the control unit is disassembled and maintained on the ship, the system can exhaust and fill the electromechanical static pressure closed system through the self open oil tank and the electric oil replenishing pump without additional equipment.
(5) The invention realizes the isolation and reliable sealing of the open hydraulic system and the closed hydraulic system, designs the leakage-free locking valve for ensuring the reliable isolation and switching of the open hydraulic system (manual emergency valve group) and the closed hydraulic system (EHA integrated valve group), and adopts a manual or hydraulic signal mode to trigger according to the use requirement.
(6) The invention realizes the isolation switching of a single hydraulic cylinder passage under the condition of a large amount of oil leakage, and sets the multi-path electromagnetic bypass valve, the electromagnetic locking valve and the manual stop valve aiming at the working condition configured by double hydraulic cylinders, so that under the condition that a certain hydraulic cylinder has a large amount of oil leakage, the fault hydraulic cylinder can be quickly isolated without influencing the normal steering of the other hydraulic cylinder.
(7) The invention realizes the pressure balance of the oil tanks of the double EHA closed system, and the self-pressurizing oil tanks of the two EHA integrated valve groups are directly communicated together through the manual emergency valve group, thereby avoiding the pressure imbalance of the oil tanks caused by the opening pressure difference of the oil supplementing check valve and the internal leakage difference of the servo motor pump.
Drawings
Fig. 1 is a schematic diagram of an electromechanical static pressure control unit for a ship of the invention.
Detailed Description
The electromechanical static pressure control unit for the ship is designed and provided for the ship application environment, is a novel electromechanical control device for controlling the speed and the direction of a hydraulic cylinder by changing the rotating speed and the steering of a servo motor pump, and has the dual advantages of low electromechanical servo vibration noise and strong heavy load capacity of a traditional hydraulic system.
As shown in fig. 1, the invention provides an electromechanical static pressure control unit for a ship, which is used for controlling the operation of a ship steering engine, and comprises: the first EHA integrated valve group, the second EHA integrated valve group and the manual emergency valve group;
the first EHA integrated valve group and the second EHA integrated valve group are redundant and backup for each other, a first hydraulic cylinder and a second hydraulic cylinder on a control ship work, and the manual emergency valve group is used for emergency control of the first hydraulic cylinder and the second hydraulic cylinder, exhaust filling of the first EHA integrated valve group and the second EHA integrated valve group, and hydraulic oil supplement of the first EHA integrated valve group or the second EHA integrated valve group.
and a, when the first EHA integrated valve group and the second EHA integrated valve group work normally at the same time, the first EHA integrated valve group and the second EHA integrated valve group control a first hydraulic cylinder and a second hydraulic cylinder on the ship to work together.
And b, when only one group of the first EHA integrated valve group or the second EHA integrated valve group works normally, controlling the first hydraulic cylinder and the second hydraulic cylinder on the ship to work through the first EHA integrated valve group or the second EHA integrated valve group which works normally.
And c, when the first EHA integrated valve group and the second EHA integrated valve group can not work normally, switching to a manual emergency valve group to control a first hydraulic cylinder and a second hydraulic cylinder on the ship to work.
The first hydraulic cylinder and the second hydraulic cylinder work simultaneously or work independently, a rod cavity of the first hydraulic cylinder is communicated with a rodless cavity of the second hydraulic cylinder, and the rodless cavity of the first hydraulic cylinder is communicated with a rod cavity of the second hydraulic cylinder.
As shown in fig. 1, the first EHA integrated valve group and the second EHA integrated valve group have the same structure, and both include a screw pump 1, a servo motor 2, an oil supplementing check valve 3, an electromagnetic locking valve 5, a self-pressurizing oil tank 6, an air charging nozzle 10, a high-pressure safety valve 11, a manual bypass valve 12, a differential pressure sensor 13, an oil filter assembly 4, a low-pressure safety valve 7, a low-pressure sensor 8 and a temperature sensor 9;
it should be noted that some of the components shown in fig. 1 are numbered A, B, and the main purpose is to distinguish the first EHA manifold from the second EHA manifold, because the first EHA manifold and the second EHA manifold have the same structure, the same components are numbered the same and are distinguished by a/B. In the specific embodiment, A/B is not distinguished any more, and is only indicated by the same numerical reference; the invention designs the screw pump 2 and the servo motor 1 into a whole in structure, and the whole is called a servo motor pump.
The servo motor 2 drives the screw pump 1 to work, and the flow and the direction output by the screw pump 1 are changed by changing the rotating speed and the steering direction of the servo motor 2; the oil supplementing one-way valve 3 is used for supplementing oil for the screw pump 1, and the self-pressurization oil tank 6 compensates leakage of the EHA integrated valve group and provides back pressure for the EHA integrated valve group to prevent cavitation; the charging connector 10 is used for controlling the pressure of the self-pressurization oil tank 6, and the high-pressure safety valve 11 is opened for unloading when the pressure of the EHA integrated valve group exceeds the allowable pressure, so that the highest pressure is limited; the manual bypass valve 12 is opened during exhaust and filling, and is communicated with the whole hydraulic circuit; the differential pressure sensor 13 is used for monitoring the differential pressure of two cavities of the hydraulic cylinder, and the electromagnetic locking valve 5 is used for controlling the connection or disconnection of the EHA integrated valve group and an external oil circuit. The oil filter assembly 4 is used for filtering an oil circuit of the EHA integrated valve group, the low-pressure sensor 8 is used for monitoring the pressure of the self-pressurization oil tank 6, the low-pressure safety valve 7 is used for opening unloading when the pressure of the self-pressurization oil tank 6 exceeds the allowable pressure, and the temperature sensor 9 is used for monitoring the temperature of the self-pressurization oil tank 6.
As shown in fig. 1, the manual emergency valve set includes an open oil tank, a hydraulic control check valve 15, a first non-leakage electromagnetic locking valve 17, a manual stop valve 18, a manual hydraulic pump 19, an electric oil supply pump 21, a manual control module, and an oil supply and filling module.
The open oil tank stores working media and provides hydraulic oil for the manual hydraulic pump 19 and the electric oil supplementing pump 21, the manual hydraulic pump 19 realizes control over a hydraulic cylinder through a manual control module, and the electric oil supplementing pump 21 realizes oil supplementing and filling of the EHA integrated valve group through an oil supplementing and filling module; the hydraulic control one-way valve 15 is used for discharging redundant hydraulic oil of the asymmetric hydraulic cylinder, so that the redundant hydraulic oil enters the open oil tank; the first leakless electromagnetic locking valve 17 and the manual stop valve 18 are used for controlling the connection and disconnection between the first hydraulic cylinder and the second hydraulic cylinder.
The manual control module comprises a manual reversing valve 20, a manual leakage-free locking valve 24 and a hydraulic locking valve 25; the manual leakage-free locking valve 24 is used for controlling the on-off of an oil path between the open oil tank and the hydraulic cylinder, the manual reversing valve 20 is used for controlling hydraulic oil output by the manual hydraulic pump 19 to enter a rod cavity or a rodless cavity of the hydraulic cylinder, and the hydraulic locking valve 25 is used for locking the hydraulic cylinder.
The oil supplementing and filling module comprises a second non-leakage electromagnetic locking valve 14, an electromagnetic bypass valve 16, an overflow valve 26, a hydraulic control non-leakage locking valve 27, an electromagnetic directional valve 28, a first check valve 29, a manual control high-pressure safety valve 30 and a second check valve 31;
the overflow valve 26 is used for setting the output pressure of the electric oil supplementing pump 21, the first check valve 29 is arranged at the outlet of the electric oil supplementing pump 21 and used for preventing oil from flowing backwards, the electromagnetic directional valve 28 is used for controlling the opening and closing of the hydraulic control non-leakage locking valve 27, the hydraulic control non-leakage locking valve 27 is used for controlling the on-off of an oil path between the open oil tank and the EHA integrated valve group, and the second check valve 31 is used for isolating the hydraulic control check valve 15 and the electric oil supplementing pump 21; the manual high-pressure safety valve 30 is used for opening the unloading when the pressure of the manual emergency valve bank exceeds the allowable pressure.
The electromagnetic bypass valve 16 is used for communicating two cavities of the hydraulic cylinder with the open oil tank, and the second non-leakage electromagnetic locking valve 14 is used for isolating the self-pressurization oil tank 6.
The EAC integrated valve group and the ship installation machine foot are additionally provided with a shock pad (vibration isolator), so that the vibration can be further reduced, and the noise is reduced.
The working principle is as follows:
1. dual EHA integration valve bank + dual hydraulic cylinder mode.
The rotation speed and the rotation direction of servo motor pumps of the two EHA integrated valve groups are the same, the four electromagnetic locking valves 5 are powered on and opened at the same time, at the moment, if the motor pumps rotate forwards, a rod cavity of the asymmetric hydraulic cylinder A23 and a rodless cavity of the asymmetric hydraulic cylinder B23 are high-pressure cavities, the pressure is determined by load, a rodless cavity of the asymmetric hydraulic cylinder A23 and a rod cavity of the asymmetric hydraulic cylinder B23 are low-pressure cavities, and the right action of a steering mechanism is realized; when the servo motor pump is reversed, the pressures of the two cavities of the hydraulic cylinders A23 and B23 are converted along with the reverse direction of the servo motor pump, and the reverse action of the rudder pushing mechanism is realized.
2. Single EHA integration valve bank + dual hydraulic cylinder mode.
Under the condition that one EHA integrated valve group has a fault, two electromagnetic locking valves 5 of the fault valve group are powered off and closed to realize fault isolation of the hydraulic control system, and the other integrated valve group which normally works can still control the hydraulic cylinder A23 and the hydraulic cylinder B23 to work to realize control of the steering mechanism.
3. Single EHA integration valve bank + single hydraulic cylinder mode.
Under the condition that one set of hydraulic cylinder has a fault (taking the fault of the hydraulic cylinder A23 as an example), the two first electromagnetic non-leakage locking valves 14 and the two second electromagnetic non-leakage locking valves 17 are powered on and closed, the servo motor pump A is stopped, the two electromagnetic bypass valves A16 are powered on and opened, the oil supplementing motor pump 21 is started, the electromagnetic directional valve 28 is powered on so as to open the hydraulic control non-leakage locking valve 27, and at the moment, two cavities of the fault hydraulic cylinder are communicated with the open oil tank B and are in a follow-up state; when the asymmetric hydraulic cylinder B23 which normally works retracts, the oil inlet amount of the rod cavity is smaller than the oil outlet amount of the rodless cavity, and at the moment, the hydraulic control one-way valve B15 is opened, so that redundant hydraulic oil flows into the pressurization oil tank; when the asymmetric hydraulic cylinder extends out, the oil inlet amount of the rodless cavity is larger than the oil outlet amount of the rod cavity, and at the moment, the self-pressurization oil tank 6 supplies hydraulic oil to the oil return end of the servo motor pump B through the oil supply one-way valve 3.
4. And (5) working modes of a manual emergency valve group.
Under the condition that the two EHA integrated valve groups cannot work, all power supplies of the steering engine are cut off, at the moment, the four electromagnetic locking valves 5 are turned off when power is lost, the manual leakage-free locking valve 24 is opened, and the manual hydraulic pump 19 can realize the change of the movement direction of the hydraulic cylinder through the manual reversing valve 20. The manual hydraulic pump station is an open system, and the working principle of controlling the symmetrical hydraulic cylinder and the asymmetrical hydraulic cylinder is the same.
5. Automatic oil supplementing function.
When the liquid level of the self-pressurization oil tank 6 is lower than a normal value, the oil supplementing motor pump 21 is started, the electromagnetic directional valve 28 is electrified, so that the hydraulic control leakage-free locking valve 27 is opened, and oil supplementation is carried out on the two self-pressurization oil tanks 6; after the liquid level of the oil tank 6 is recovered to a normal value, the electromagnetic directional valve 28 is electrically switched off, so that the hydraulic control leakage-free locking valve 27 is closed, the oil supplementing motor pump 21 is stopped, and the oil supplementing process is completed.
6. And the open system has an exhaust and filling function to the closed system.
After disassembly and maintenance on a ship, the system needs to exhaust and fill, and the process is as follows:
a) the system is powered off, a manual leakage-free locking valve 24 is opened, and the hydraulic cylinder is manually steered for 10 cycles to complete the exhaust and filling of the hydraulic cylinder;
b) disconnecting the self-sealing joint 22 of the hydraulic cylinder, opening the electromagnetic bypass valve A12, electrifying and opening two electromagnetic locking valves A5 and a single electromagnetic bypass valve A16 (above), electrifying and closing a first non-leakage electromagnetic locking valve B14, starting the oil supplementing motor pump 21, electrifying the electromagnetic reversing valve 28 to open the hydraulic non-leakage locking valve, starting the A1# servo motor pump (+300r/min, so that the electromagnetic bypass valve A16 (above) is a high-pressure port), and working for 1 min; the electromagnetic bypass valve A16 (above) is powered off, the electromagnetic bypass valve B16 (below) is powered on and is opened, and the work time is 1 min; the electromagnetic bypass valve B16 (below) is powered off, the electromagnetic bypass valve A16 (below) is powered on and opened, the servo motor pump A rotates reversely (-300 r/min), so that the electromagnetic bypass valve A16 (below) is a high-pressure port), and the work time is 1 min; the electromagnetic bypass valve A16 (below) is powered off, the electromagnetic bypass valve B16 (above) is powered on and is opened, and the work time is 1 min; the servo motor pump A is stopped, the manual bypass valve A12 is closed, the two electromagnetic locking valves A5 and the single electromagnetic bypass valve A16 (above) are electrically closed, and the electromagnetic leakage-free locking valve A14 is electrically closed;
c) the electromagnetic leakage-free locking valve B14 is electrically opened, the servo motor pump B is started, and the step B) is repeated;
d) connecting an actuator self-seal 22, starting an electric oil supplementing pump 21, electrifying and closing an electromagnetic non-leakage locking valve B14, electrifying and opening two electromagnetic locking valves A5, electrifying an electromagnetic reversing valve 28 to open a hydraulic non-leakage locking valve 27, starting a servo motor pump A (1000r/min), powering down all valves except the electromagnetic reversing valve 28 after the position is closed-loop operated for 5min, and stopping the servo motor pump A; the electromagnetic bypass valve A16 and the electromagnetic locking valve B5 are powered on and opened, the servo motor pump B is started (1000r/min), and the system is powered off and stopped after the position closed loop works for 5 min;
e) repeating step a);
f) finishing filling;
the main parameters of the electromechanical static pressure control unit and the hydraulic servo system of the ship in service are compared as follows:
as can be seen from the above table, the electro-mechanical static pressure control unit has the following advantages over the active ship hydraulic servo system:
1. small occupied space and light weight. The permanent magnet synchronous motor with high power density is adopted, so that the volume and the weight are small; the traditional open type large oil tank is cancelled, and a small closed type oil tank is adopted, so that oil is less; and an integrated design is adopted, and the pipeline connection is cancelled internally, so that the volume and the weight are greatly reduced.
2. Low noise and vibration. The EHA integrated valve group adopts a high-pressure low-noise servo motor pump, so that the vibration noise can be reduced from the source; the system pressure has the load self-adaptive characteristic, and a soft start-stop strategy is adopted in control, so that the reversing impact can be obviously reduced; the hydraulic pipelines are few, and the pipeline vibration is obviously reduced; the integrated valve group and the ship installation machine foot are additionally provided with the shock pad, so that the vibration can be further reduced.
3. Strong anti-pollution capability and high reliability. The traditional electro-hydraulic steering device adopts an open oil tank, so that oil is more, the oil tank is communicated with external atmosphere and is easy to be polluted, and the service life of a hydraulic component is shortened by reversing impact caused by a valve control mode. The EHA integrated valve group adopts a closed oil tank, can be basically and completely isolated from the outside, is not easy to be polluted by oil, and has stable motor pump control reversing and long service life of components.
In addition, the hydraulic loop of the electromechanical static pressure control unit is simple, hydraulic oil output by the motor pump directly enters the hydraulic cylinder, hydraulic components such as a reversing valve and a hydraulic lock are not arranged in the middle of the hydraulic cylinder, the number of the components is small, fault points are reduced, and the reliability is higher.
4. The maintainability is good. The control unit adopts the modularized design, the number of components and pipelines is reduced, and the main modules can be rapidly replaced through the self-sealing connector, so that the workload of maintenance and repair is greatly reduced, and the maintenance cost is reduced. The system is internally provided with no rotary seal, the linear motion seal adopts a redundant combination seal mode, the external seal adopts a multi-seal structure, the high seal reliability is realized, and the maintenance period of the system can be obviously prolonged.
5. High efficiency and low energy consumption. The servo motor is adopted for frequency conversion and speed regulation control, so that the control efficiency is high; the number of pipelines is small, the oil way is simple, and the throttling loss is small; in the rudder angle keeping process, the motor is in low-speed standby, the heating is small, and the energy consumption is low.
The above description is only for the best mode of the present invention, but the scope of the present invention is not limited thereto, and any changes or substitutions that can be easily conceived by those skilled in the art within the technical scope of the present invention are included in the scope of the present invention.
Those skilled in the art will appreciate that the invention may be practiced without these specific details.
Claims (7)
1. The utility model provides a naval vessel is with electromechanical static pressure control unit for control naval vessel steering wheel work, its characterized in that includes: the first EHA integrated valve group, the second EHA integrated valve group and the manual emergency valve group;
the first EHA integrated valve group and the second EHA integrated valve group are redundant and backup with each other, a first hydraulic cylinder and a second hydraulic cylinder on a ship are controlled to work, and the manual emergency valve group is used for emergently controlling the first hydraulic cylinder and the second hydraulic cylinder to work, exhausting and filling the first EHA integrated valve group and the second EHA integrated valve group, and supplementing hydraulic oil to the first EHA integrated valve group or the second EHA integrated valve group;
the manual emergency valve group comprises an open oil tank, a hydraulic control one-way valve (15), a first non-leakage electromagnetic locking valve (17), a manual stop valve (18), a manual hydraulic pump (19), an electric oil supplementing pump (21), a manual control module and an oil supplementing and filling module;
the open oil tank stores working media and provides hydraulic oil for the manual hydraulic pump (19) and the electric oil supplementing pump (21), the manual hydraulic pump (19) realizes control over a hydraulic cylinder through a manual control module, and the electric oil supplementing pump (21) realizes oil supplementing and filling of the EHA integrated valve group through an oil supplementing and filling module; the hydraulic control one-way valve (15) is used for discharging the redundant hydraulic oil of the asymmetric hydraulic cylinder and enabling the redundant hydraulic oil to enter the open oil tank; the first non-leakage electromagnetic locking valve (17) and the manual stop valve (18) are used for controlling the connection and disconnection between the first hydraulic cylinder and the second hydraulic cylinder;
the manual control module comprises a manual reversing valve (20), a manual leakage-free locking valve (24) and a hydraulic locking valve (25); the manual leakage-free locking valve (24) is used for controlling the on-off of an oil path between the open oil tank and the hydraulic cylinder, the manual reversing valve (20) is used for controlling hydraulic oil output by the manual hydraulic pump (19) to enter a rod cavity or a rodless cavity of the hydraulic cylinder, and the hydraulic locking valve (25) is used for locking the hydraulic cylinder;
the oil supplementing and filling module comprises a second non-leakage electromagnetic locking valve (14), an electromagnetic bypass valve (16), an overflow valve (26), a hydraulic control non-leakage locking valve (27), an electromagnetic directional valve (28), a first one-way valve (29), a manual control high-pressure safety valve (30) and a second one-way valve (31);
the overflow valve (26) is used for setting the output pressure of the electric oil supplementing pump (21), the first one-way valve (29) is arranged at the outlet of the electric oil supplementing pump (21) and used for preventing oil from flowing backwards, the electromagnetic reversing valve (28) is used for controlling the opening and closing of the hydraulic control non-leakage locking valve (27), the hydraulic control non-leakage locking valve (27) is used for controlling the opening and closing of an oil way between the open oil tank and the EHA integrated valve group, and the second one-way valve (31) is used for isolating the hydraulic control one-way valve (15) and the electric oil supplementing pump (21); the manual high-pressure safety valve (30) is used for opening the unloading when the pressure of the manual emergency valve bank exceeds the allowable pressure
The electromagnetic bypass valve (16) is used for communicating two cavities of the hydraulic cylinder with the open oil tank, and the second non-leakage electromagnetic locking valve (14) is used for isolating the self-pressurization oil tank (6).
2. The electromechanical static pressure control unit for a ship of claim 1, characterized in that: when the first EHA integrated valve group and the second EHA integrated valve group work normally at the same time, the first EHA integrated valve group and the second EHA integrated valve group control the first hydraulic cylinder and the second hydraulic cylinder on the ship to work together.
3. The electromechanical static pressure control unit for a ship of claim 1, characterized in that: when the first EHA integrated valve group or the second EHA integrated valve group only has a group of normal work, the first hydraulic cylinder and the second hydraulic cylinder on the ship are controlled to work through the first EHA integrated valve group or the second EHA integrated valve group which normally work.
4. The electromechanical static pressure control unit for a ship of claim 1, characterized in that: when the first EHA integrated valve group and the second EHA integrated valve group can not work normally, the first hydraulic cylinder and the second hydraulic cylinder on the ship are controlled to work by switching to the manual emergency valve group.
5. The electromechanical static pressure control unit for a ship of claim 1, characterized in that: the first hydraulic cylinder and the second hydraulic cylinder work simultaneously or work independently, a rod cavity of the first hydraulic cylinder is communicated with a rodless cavity of the second hydraulic cylinder, and the rodless cavity of the first hydraulic cylinder is communicated with a rod cavity of the second hydraulic cylinder.
6. The electromechanical static pressure control unit for a ship of claim 1, characterized in that: the first EHA integrated valve group and the second EHA integrated valve group are identical in structure and respectively comprise a screw pump (1), a servo motor (2), an oil supplementing one-way valve (3), an electromagnetic locking valve (5), a self-pressurization oil tank (6), an inflating nozzle (10), a high-pressure safety valve (11), a manual bypass valve (12) and a differential pressure sensor (13);
the servo motor (2) drives the screw pump (1) to work, and the flow and the direction output by the screw pump (1) are changed by changing the rotating speed and the steering direction of the servo motor (2); the oil-supplementing one-way valve (3) is used for supplementing oil for the screw pump (1),
the self-pressurization oil tank (6) compensates leakage of the EHA integrated valve group and provides back pressure for the EHA integrated valve group to prevent cavitation; the charging connector (10) is used for controlling the pressure of the self-pressurization oil tank (6),
the high-pressure safety valve (11) is opened for unloading when the pressure of the EHA integrated valve group exceeds the allowable pressure, so that the highest pressure is limited; the manual bypass valve (12) is opened during exhaust and filling, and is communicated with the whole hydraulic circuit; the pressure difference sensor (13) is used for monitoring the pressure difference between two cavities of the hydraulic cylinder, and the electromagnetic locking valve (5) is used for controlling the connection or disconnection of the EHA integrated valve group and an external oil way.
7. The electromechanical static pressure control unit for a ship of claim 6, wherein: the first EHA manifold block and the second EHA manifold block structure further include: the oil filter assembly (4), the low-pressure safety valve (7), the low-pressure sensor (8) and the temperature sensor (9);
the oil filter assembly (4) is used for filtering an oil circuit of the EHA integrated valve group, the low-pressure sensor (8) monitors the pressure of the self-pressurization oil tank (6), the low-pressure safety valve (7) is used for opening unloading when the pressure of the self-pressurization oil tank (6) exceeds the allowable pressure, and the temperature sensor (9) monitors the temperature of the self-pressurization oil tank (6).
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| CN201810957470.5A CN108869437B (en) | 2018-08-22 | 2018-08-22 | Electromechanical static pressure control unit for ship |
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| CN201810957470.5A CN108869437B (en) | 2018-08-22 | 2018-08-22 | Electromechanical static pressure control unit for ship |
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| CN110630591B (en) * | 2019-07-31 | 2021-05-28 | 武汉船用机械有限责任公司 | Hydraulic system of full-rotation rudder propeller device and control method thereof |
| CN112460098B (en) * | 2020-11-13 | 2022-10-14 | 北京精密机电控制设备研究所 | High-reliability static pressure locking system |
| CN113719486A (en) * | 2021-08-31 | 2021-11-30 | 上海衡拓液压控制技术有限公司 | EHA hydraulic synchronization system |
| CN117950303A (en) * | 2024-03-25 | 2024-04-30 | 中国汽车工业工程有限公司 | Feeding system capable of realizing mutual standby of multiple feeding units and control method |
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| JP4169913B2 (en) * | 2000-08-07 | 2008-10-22 | ナブテスコ株式会社 | Actuator |
| CN103075393A (en) * | 2011-10-26 | 2013-05-01 | 北京精密机电控制设备研究所 | Novel multi-redundancy electromechanical hydrostatic servo mechanism |
| CN105570237B (en) * | 2014-10-31 | 2019-02-26 | 北京精密机电控制设备研究所 | A kind of double redundancy electromechanical static pressure servo mechanism |
| CN204512079U (en) * | 2015-01-28 | 2015-07-29 | 北京航空航天大学 | A kind of two remaining Electrical hydrostatic actuator |
| CN106337845B (en) * | 2016-09-08 | 2018-02-13 | 北京精密机电控制设备研究所 | A kind of bi-directional electromechanical Static prestressed-pile device |
| CN106402098B (en) * | 2016-10-19 | 2018-11-06 | 北京精密机电控制设备研究所 | A kind of electromechanical static pressure control system |
| JP2018094969A (en) * | 2016-12-08 | 2018-06-21 | 住友精密工業株式会社 | Eha system of aircraft landing gear |
| CN108194433A (en) * | 2017-12-20 | 2018-06-22 | 北京交通大学 | Electromechanical static pressure actuating system |
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