CN106032261A - Tension control device of high-power hydraulic winch - Google Patents
Tension control device of high-power hydraulic winch Download PDFInfo
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- CN106032261A CN106032261A CN201610580567.XA CN201610580567A CN106032261A CN 106032261 A CN106032261 A CN 106032261A CN 201610580567 A CN201610580567 A CN 201610580567A CN 106032261 A CN106032261 A CN 106032261A
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- valve
- pressure
- mouth
- control valve
- winch
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
- B66D1/28—Other constructional details
- B66D1/40—Control devices
- B66D1/42—Control devices non-automatic
- B66D1/44—Control devices non-automatic pneumatic of hydraulic
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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
- F15B21/08—Servomotor systems incorporating electrically operated control means
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a tension control device of a high-power hydraulic winch. The tension control device comprises a hydraulic power station, a proportional throttle valve, a pressure compensation valve, a counterbalance valve, a proportional overflow valve, three two-way switching valves, two pressure sensors, a shuttle valve, a speed sensor, the winch with a reduction gearbox, a large-capacity hydraulic motor and an electronic controller. The electronic controller of the control device can automatically set the proportional overflow valve according to the working conditions, the functions of a balance valve, a tension valve and a safety valve are achieved through the proportional overflow valve, meanwhile, the electronic controller can automatically control the switching valves to be switched on and off, switching of an active cable laying oil way, an active cable take-up oil way, a tension cable laying oil way and the like is achieved through different switch-on and switch-off combinations of the switching valves, and the operability, reliability and integration degree of the control device under the large-flow condition are greatly improved. In addition, the control device can achieve compound control over the work tension and cable length of the hydraulic winch, and is especially suitable for controlling the hydraulic winch with various existing tension control requirements and cable length control requirements in the ocean engineering.
Description
Technical field
The present invention relates to hydraulic drive and control technology, especially relate to the tenslator of a kind of high power hydraulic winch.
Background technology
Hydraulic wireline winch is a kind of visual plant in national product, is widely used in boats and ships and other construction industry.Along with winch volume
Fixed load and improve constantly operating rate requirement, drawworks horsepower is increasing, thus required flow is the most increasing.
At present hydraulic wireline winch commonly uses the proportional direction valve of guiding valve form as its major control element, and the most integrated other
Element realizes tension force control, Ioad-sensing control etc..But due to reasons in structure, the proportional direction valve of guiding valve form is difficult to greatly
Flow (more than 1000L/min), and the flow that present stage powerful hydraulic wireline winch often demand 2000L/min is the biggest,
For this contradiction, the proportional direction valve of equipment vendors' two guiding valve forms of many employings is connected in parallel and meets demand, but this makes
Have the disadvantage in that by situation
1. use two proportional direction valve parallel connections, asynchronous due to valve individuality manufacturing variation and the operation of two valves, it is easily caused a certain
Valve flow is excessive and makes the operability of system be deteriorated, seriously may result in wherein valve exceed its power domain owing to flow is excessive and
Make system malfunction, cause serious production accident.
2. controlling element due to how integrated other of winch control proportional direction valve, being connected in parallel of proportional direction valve causes other
Control element to be also connected in parallel, reduce the reliability of system and add cost.
3. using two proportional direction valve parallel connections, device structure is heavy, bulky, and exterior line connects complexity.
Although and have the three position four-way directional control valve of big flow plug-in mounting form in other hydraulic systems, but it is merely capable of realizing oil
Simply commutate in road, it is impossible to meet carry tensioned control function winch actively cable laying, actively draw over to one's side, tension force cable laying, passively draw over to one's side,
The oil circuit switching of constant tensile control etc., and it does not possess the function that speed controlling and tension force control, if adding on the basis of this more again
Tension valve, balanced valve etc. then can not play the advantage that inserted valve integration is good, reduce system compactness, add the cost of equipment.
Summary of the invention
In order to overcome the existing winch control valve group in above-mentioned background technology to use operability, reliable under flow high-power, big
The shortcoming that property is poor, it is an object of the invention to provide the tenslator of a kind of high power hydraulic winch, can be used for high-power,
In big flow, and integrated level, reliability height hydraulic control device.
In order to reach foregoing invention purpose, the technical solution adopted in the present invention is:
The present invention includes hydraulic power unit, control valve group integrated package, velocity sensor, the winch of band reduction box, huge discharge hydraulic motor,
Electronic controller.
The high pressure delivery side of pump of hydraulic power unit connects the A of proportional throttle valve respectively by the MP hydraulic fluid port on control valve group integrated package
Mouthful with the A mouth of pressure-compensated valve, the B mouth of pressure-compensated valve is connected with the B mouth of counterbalance valve and passes through on control valve group integrated package
MT hydraulic fluid port takes back fuel tank through return filter, the B mouth of proportional throttle valve respectively with the A mouth and of first two-way switch valve
The A mouth of two two-way switch valves is connected, the A mouth of counterbalance valve, the B mouth of proportional pressure control valve and the B of the 3rd two-way switch valve
Mouth is connected, and the B mouth of the A mouth of proportional pressure control valve and first two-way switch valve is connected also with the first pressure transducer after being connected
The B chamber of huge discharge hydraulic motor is connect, the B mouth of second two-way switch valve and by the MB hydraulic fluid port on control valve group integrated package
The MA oil that the A mouth of three two-way switch valves is connected with second pressure transducer after being connected and passes through on control valve group integrated package
Mouth connects the A chamber of huge discharge hydraulic motor, and the pressure acquisition mouth of shuttle valve is respectively by MA, MB oil on control valve group integrated package
Mouth is connected with A, B chamber of huge discharge hydraulic motor, and the pressure output of shuttle valve is connected with pressure-compensated valve；Huge discharge hydraulic pressure
Motor is connected with the winch of band reduction box, and equipped with velocity sensor on the winch of band reduction box, electronic controller is believed with instruction respectively
Number, second pressure sensing in the first pressure transducer in velocity sensor, control valve group integrated package and control valve group integrated package
Device electrically connects.
Described control valve group integrated package, including proportional throttle valve, pressure-compensated valve, counterbalance valve, proportional pressure control valve, first
Two-way switch valve, second two-way switch valve, the 3rd two-way switch valve, first pressure transducer the second pressure transducer, shuttle
Valve.
Described proportional throttle valve, including large-capacity valve core plug-in unit and proportional pilot valve.
Described pressure-compensated valve, including solenoid directional control valve, sequence valve and large-capacity valve core plug-in unit.
Described counterbalance valve, including solenoid directional control valve, overflow valve and large-capacity valve core plug-in unit.
Described proportional pressure control valve, including proportional pilot valve and large-capacity valve core plug-in unit.
Described first two-way switch valve, including solenoid directional control valve, shuttle valve and large-capacity valve core plug-in unit；Second two-way switch
Valve, including solenoid directional control valve, shuttle valve and large-capacity valve core plug-in unit；3rd two-way switch valve, including solenoid directional control valve and big stream
Amount spool plug-in unit.
Described hydraulic power unit, including motor, high-pressure pump, fuel tank, return filter；The inlet port of high-pressure pump is with fuel tank even
Connecing, the oil-out of high-pressure pump is connected with pressure-compensated valve, and the oil-out of return filter is connected with fuel tank, entering of return filter
Hydraulic fluid port is connected with the B mouth of counterbalance valve by the MT hydraulic fluid port on control valve group integrated package, and high-pressure pump is by shaft coupling with motor even
Connect.
Described electronic controller, selects Siemens S7-300 series of PLC controller, and its model is 315-2DP.
Compared with background technology, one has the beneficial effect that
1) two-way plug-in valve is used to make control device have good reliability and operability at big flow, the maximum control of two-way plug-in valve
Flow is up to more than 10000L/min, and its valve port pressuring drop is less, device good energy saving property.
2) use electronic controller is according to the sensor signal automatic decision operating mode of command signal and collection, and controls inserted valve first
Conductive magnetism reversal valve realizes the switching of different oil circuit, with adaptation condition.Valve group opens and closes combination flexibly, uses less valve member to produce
More oil circuit combination, drastically increases the integrated level of device.
3) electronic controller is used to automatically control proportional pressure control valve according to the sensor signal of command signal and collection so that it is not
Under same operating mode, proportion by subtraction serves as overflow valve, relief valve and balanced valve, further increases the integrated level of system.
4) this control device can follow the moment of torsion arbitrarily set automatically or rate curve is operated, and can automatically remember
Systematic parameter in record construction, improves the automaticity of system.
The invention is particularly suited to the most tensioned various controls in ocean engineering requires but also has cable length to control the hydraulic wireline winch required
Manipulation.
Accompanying drawing explanation
Fig. 1 is the system construction drawing of the present invention.
Fig. 2 is the schematic diagram of control valve group integrated package.
Fig. 3 is electronic controller signal wiring schematic diagram.
Fig. 4 is electronic controller operating mode decision flow chart.
In figure: 1, motor, 2, high-pressure pump, 3, fuel tank, 4, return filter, 5, proportional throttle valve (includes flowing greatly
Amount spool plug-in unit 5.2 and proportional pilot valve 5.1), 6, pressure-compensated valve (include solenoid directional control valve 6.1, leader sequence valve 6.2 and
Large-capacity valve core plug-in unit 6.3), 7, counterbalance valve (including solenoid directional control valve 7.1, overflow valve 7.2 and large-capacity valve core plug-in unit 7.3), 8,
Proportional pressure control valve (includes proportional pilot valve 8.1 and large-capacity valve core plug-in unit 8.2), and 9, first two-way switch valve (includes that electromagnetism changes
To valve 9.1, shuttle valve 9.2 and large-capacity valve core plug-in unit 9.3), 10, second two-way switch valve (includes solenoid directional control valve 10.1, shuttle
Valve 10.2 and large-capacity valve core plug-in unit 10.3), the 11, the 3rd two-way switch valve (includes solenoid directional control valve 11.1 and large-capacity valve core
Plug-in unit 11.2), the 12.1, first pressure transducer 12.2, the second pressure transducer, 13, shuttle valve, 14, velocity sensor, 15,
With the winch of reduction box, 16, huge discharge hydraulic motor, 17, electronic controller, 18, control valve group integrated package.
Detailed description of the invention
The present invention is described further with embodiment below in conjunction with the accompanying drawings.
As it is shown in figure 1, the present invention includes hydraulic power unit, control valve group integrated package 18, velocity sensor 14, band reduction box
Winch 15, huge discharge hydraulic motor 16, electronic controller 17.
The outlet of the high-pressure pump 2 of hydraulic power unit connects proportional throttle valve respectively by the MP hydraulic fluid port on control valve group integrated package 18
The A mouth of 5 and the A mouth of pressure-compensated valve 6, the B mouth of pressure-compensated valve 6 is connected with the B mouth of counterbalance valve 7 and passes through control valve
Group integrated package 18 on MT hydraulic fluid port take back fuel tank through return filter 4, the B mouth of proportional throttle valve 5 respectively with first
The A mouth of the A mouth of two-way switch valve 9 and second two-way switch valve 10 is connected, the A mouth of counterbalance valve 7, proportional pressure control valve
The B mouth of the B mouth of 8 and the 3rd two-way switch valve 11 is connected, the A mouth of proportional pressure control valve 8 and first two-way switch valve 9
B mouth be connected after be connected with the first pressure transducer 12.1 and meet big row by the MB hydraulic fluid port on control valve group integrated package 18
The B chamber of amount hydraulic motor 16, the A mouth of the B mouth of second two-way switch valve 10 and the 3rd two-way switch valve 11 is connected
It is connected with second pressure transducer 12.2 afterwards and connects huge discharge hydraulic motor by the MA hydraulic fluid port on control valve group integrated package 18
The A chamber of 16, the pressure acquisition mouth of shuttle valve 13 is respectively by MA, MB hydraulic fluid port on control valve group integrated package 18 and huge discharge
A, B chamber of hydraulic motor 16 is connected, the outlet phase of the pressure output of shuttle valve 13 and the sequence valve 6.2 of pressure-compensated valve 6
Even；Huge discharge hydraulic motor 16 is connected with the winch 15 of band reduction box, equipped with velocity sensor on the winch 15 of band reduction box
14, electronic controller 17 respectively with the first pressure sensing in command signal, velocity sensor 14, control valve group integrated package 18
In device 12.1 and control valve group integrated package 18, second pressure transducer 12.2 electrically connects.
As in figure 2 it is shown, described control valve group integrated package 18, including proportional throttle valve 5, pressure-compensated valve 6, counterbalance valve 7,
Proportional pressure control valve 8, first two-way switch valve 9, second two-way switch valve 10, the 3rd two-way switch valve 11, the first pressure
Force transducer the 12.1, second pressure transducer 12.2, shuttle valve 13.
Described proportional throttle valve 5, including large-capacity valve core plug-in unit 5.2 and proportional pilot valve 5.1, is used for controlling winch speed.
Described pressure-compensated valve 6, including solenoid directional control valve 6.1, sequence valve 6.2 and large-capacity valve core plug-in unit 6.3, is used for unloading
Lotus and carry out load-transducing.
Described counterbalance valve 7, including solenoid directional control valve 7.1, overflow valve 7.2 and large-capacity valve core plug-in unit 7.3, is used for controlling greatly
Displacement hydraulic motor back pressure.
Described proportional pressure control valve 8, including proportional pilot valve 8.1 and large-capacity valve core plug-in unit 8.2, for tension force control and flat
Weighing apparatus Exceed load.
Described first two-way switch valve 9, including solenoid directional control valve 9.1, shuttle valve 9.2 and large-capacity valve core plug-in unit 9.3；The
Two two-way switch valves 10, including solenoid directional control valve 10.1, shuttle valve 10.2 and large-capacity valve core plug-in unit 10.3；3rd two opens up
Closing valve 11, including solenoid directional control valve 11.1 and large-capacity valve core plug-in unit 11.3, described three two-way switch valves are used to switch oil circuit.
Described hydraulic power unit, including motor 1, high-pressure pump 2, fuel tank 3, return filter 4；The inlet port of high-pressure pump 2
Being connected with fuel tank 3, the oil-out of high-pressure pump 2 is connected with pressure-compensated valve 6, and the oil-out of return filter 4 is with fuel tank 3 even
Connecing, the oil-in of return filter 4 is connected with the A mouth of counterbalance valve 7, and high-pressure pump 2 is connected with motor 1 by shaft coupling 2.
Described electronic controller, selects Siemens S7-300 series of PLC controller, and its model is 315-2DP.
Instruction that electronic controller applies according to operator and the winch rate signal collected, pressure sensor signal control
Each pilot valve electric magnet obtains electric dead electricity, and regulate proportional throttle valve, proportional pressure control valve makes system by the operating mode work set；It addition,
Tension force that electronic controller arbitrarily can also set from motion tracking or speed change curves also carry out automatic record to operational data.
During specific works, first by rule as shown in Figure 3, by speed command, tension force instruction two-way command signal and two
Pressure transducer 12.1,12.2, the three-way sensor signal of velocity sensor 14 output accesses electronic controller, electronic controller
Digital output end respectively with pressure-compensated valve solenoid directional control valve 6.1, counterbalance valve solenoid directional control valve 7.1, two-way switch valve electromagnetism changes
Be connected to valve 9.1,10.1,11.1, electronic controller analog output end respectively with proportional throttle valve proportional pilot valve 5.1,
Proportional pressure control valve proportional pilot valve 8.1 is connected；Electronic controller is sentenced according to Fig. 4 rule according to command signal and sensor signal
Disconnected applying working condition, and obtain electric and proportion electro-magnet signal according to operating mode according to subordinate list rule settings each pilot valve electric magnet dead electricity,
Each control signal exports each control valve according to Fig. 3 relation the most at last.
Below divided working status is illustrated its specific embodiments.
Off-load operating mode: then enter off-load operating mode when electronic controller is not received by any instruction, now except counterbalance valve electromagnetism
Reversal valve 7.1 electric outside, remaining solenoid directional control valve all must not electricity, proportional throttle valve 5 closes, and proportional pressure control valve 8 is set in peace
Total head force value.Pump discharge fluid is opened after pressure-compensated valve 6 through filter flow reversal fuel tank, and system is in Low-pressure load discharge state, than
Example overflow valve is used as relief valve, for setting the maximum tension that wirerope can bear.If wirerope overtension, passing ratio overflow
Valve overflow preventing wirerope overload is destroyed, and owing to counterbalance valve solenoid directional control valve 7.1 obtains electric, therefore proportional overflow valve outlet port fluid can not
Backflow fuel tank and switch valve 11 can be opened to motor low pressure chamber repairing, prevent motor to be emptied.
Actively cable laying operating mode: then enter actively cable laying operating mode when electronic controller receives positive speed command, now except pressure
Force compensating valve solenoid directional control valve 6.1 and two-way switch valve solenoid directional control valve 10.1 electric outside, remaining solenoid directional control valve all must not electricity,
Proportional throttle valve 5 sets its opening degree according to speed command, and pressure-compensated valve 6 is used for ensureing that proportional throttle valve two ends pressure reduction is basic
Constant not by load change affected, now the speed of winch is determined by proportional throttle valve opening, and unnecessary flow passes through pressure compensation
Valve is back to fuel tank.Proportional pressure control valve 8 setting value is that safe pressure deducts second pressure transducer 12.2 signal and presets
The product of Proportional coefficient K, i.e. motor A mouth pressure is the highest, and it is the lowest that proportional pressure control valve sets pressure.Now proportional pressure control valve is used
Make balanced valve, load can be surmounted by active balance, make the steady cable laying of winch, prevent the too fast security incident caused of winch cable laying.
Actively take-up operating mode: then enter actively take-up operating mode when electronic controller receives negative speed command, now except pressure
Force compensating valve solenoid directional control valve 6.1, two-way switch valve solenoid directional control valve 9.1,11.1 electric outside, remaining solenoid directional control valve all must not
Electricity, proportional throttle valve 5 sets its opening degree according to speed command, and pressure-compensated valve 6 is used for ensureing proportional throttle valve two ends pressure reduction
Substantially constant is not affected by load change, and now the speed of winch is determined by proportional throttle valve opening, and unnecessary flow passes through pressure
Recuperation valve is back to fuel tank.Proportional pressure control valve 8 is set as that safe pressure is used as relief valve, can bear for setting wirerope
Hightension.If wirerope overtension, passing ratio overflow valve overflow preventing wirerope overload is destroyed.
Tension force cable laying operating mode: when electronic controller receives tension force instruction and winch speed sensor signal more than setting value then
Enter tension force cable laying operating mode, now except pressure-compensated valve solenoid directional control valve 6.1, counterbalance valve solenoid directional control valve 7.1 and two-way switch valve
Solenoid directional control valve 10.1,11.1 electric outside, remaining solenoid directional control valve all must not electricity, proportional throttle valve 5 is set as maximum open,
Proportional pressure control valve 8 is set by tension force command signal.Now the hydraulic motor of winch is acted on pump condition by load driving, and it can carry
The moment of torsion of confession is set by proportional pressure control valve, and when proportional pressure control valve is set as steady state value, the tension force on wirerope also keeps constant.Liquid
Press pump outlet fluid enters the A mouth of hydraulic motor 16 through two-way switch valve 10.Due to the existence of counterbalance valve 7, hydraulic motor 16
A mouth maintain relatively low pressure to be emptied preventing hydraulic motor from producing.
Tension force take-up operating mode: when electronic controller receives tension force instruction and winch speed sensor signal less than setting value then
Enter tension force take-up operating mode, now except pressure-compensated valve solenoid directional control valve 6.1, counterbalance valve solenoid directional control valve 7.1 and two-way switch valve
Solenoid directional control valve 9.1,11.1 electric outside, remaining solenoid directional control valve all must not electricity, proportional throttle valve 5 is set as maximum open, than
Example overflow valve 8 is set by tension force command signal.Now the hydraulic motor of winch is driven by load and produces one at hydraulic motor B mouth
High pressure, this force value is limited by proportional pressure control valve, and when proportional pressure control valve is set as steady state value, the tension force on wirerope also keeps permanent
Fixed.Hydraulic pump outlet fluid is partly into the B mouth of hydraulic motor 16 through two-way switch valve 9, and a part is through proportional pressure control valve 8
Reflux fuel tank with counterbalance valve 7.Due to the existence of counterbalance valve 7, the A mouth of hydraulic motor 16 maintain a relatively low pressure in case
Only hydraulic motor produces and is emptied.
In sum, the high power hydraulic winch tenslator that the present invention provides can effectively overcome existing weaponry and equipment high-power
Reliability the most workable relatively low shortcoming under (maximum up to 5500Kw), improves operability and the reliability of equipment,
And device integrated level is high, efficiency is high, and automaticity is high, easy to operate.
Above-mentioned detailed description of the invention is used for illustrating the present invention rather than limiting the invention, in the spirit of the present invention
With in scope of the claims, any modifications and changes that the present invention is made, both fall within protection scope of the present invention.
Subordinate list: set each pilot valve electric magnet dead electricity and obtain electric and proportion electro-magnet signal
Claims (9)
1. the tenslator of high power hydraulic winch, it is characterized in that: include hydraulic power unit, control valve group integrated package (18), velocity sensor (14), winch (15) with reduction box, huge discharge hydraulic motor (16), electronic controller (17)；
nullThe outlet of the high-pressure pump (2) of hydraulic power unit connects the A mouth of proportional throttle valve (5) and the A mouth of pressure-compensated valve (6) respectively by the MP hydraulic fluid port in control valve group integrated package (18)，The B mouth of pressure-compensated valve (6) is connected with the B mouth of counterbalance valve (7) and the MT hydraulic fluid port that passes through in control valve group integrated package (18) takes back fuel tank through return filter (4)，The B mouth of proportional throttle valve (5) is connected with the A mouth of first two-way switch valve (9) and the A mouth of second two-way switch valve (10) respectively，The A mouth of counterbalance valve (7)、The B mouth of the B mouth of proportional pressure control valve (8) and the 3rd two-way switch valve (11) is connected，The A mouth of proportional pressure control valve (8) and the B mouth of first two-way switch valve (9) are connected with the first pressure transducer (12.1) after being connected and are connect the B chamber of huge discharge hydraulic motor (16) by the MB hydraulic fluid port in control valve group integrated package (18)，The A mouth of the B mouth of second two-way switch valve (10) and the 3rd two-way switch valve (11) is connected with second pressure transducer (12.2) after being connected and is connect the A chamber of huge discharge hydraulic motor (16) by the MA hydraulic fluid port in control valve group integrated package (18)，The pressure acquisition mouth of shuttle valve (13) is respectively by the MA in control valve group integrated package (18)、MB hydraulic fluid port and the A of huge discharge hydraulic motor (16)、B chamber is connected，The pressure output of shuttle valve (13) is connected with pressure-compensated valve (6)；Huge discharge hydraulic motor (16) is connected with the winch (15) of band reduction box, equipped with velocity sensor (14) on winch (15) with reduction box, electronic controller (17) electrically connects with second pressure transducer (12.2) in the first pressure transducer (12.1) in command signal, velocity sensor (14), control valve group integrated package (18) and control valve group integrated package (18) respectively.
The tenslator of high power hydraulic winch the most according to claim 1, it is characterized in that: described control valve group integrated package (18), including proportional throttle valve (5), pressure-compensated valve (6), counterbalance valve (7), proportional pressure control valve (8), first two-way switch valve (9), second two-way switch valve (10), 3rd two-way switch valve (11), first pressure transducer (12.1), the second pressure transducer (12.2), shuttle valve (13).
The tenslator of high power hydraulic winch the most according to claim 2, it is characterised in that: described proportional throttle valve (5), including large-capacity valve core plug-in unit (5.2) and proportional pilot valve (5.1).
The tenslator of high power hydraulic winch the most according to claim 2, it is characterized in that: described pressure-compensated valve (6), including solenoid directional control valve (6.1), sequence valve (6.2) and large-capacity valve core plug-in unit (6.3).
The tenslator of high power hydraulic winch the most according to claim 2, it is characterized in that: described counterbalance valve (7), including solenoid directional control valve (7.1), overflow valve (7.2) and large-capacity valve core plug-in unit (7.3).
The tenslator of high power hydraulic winch the most according to claim 2, it is characterised in that: described proportional pressure control valve (8), including proportional pilot valve (8.1) and large-capacity valve core plug-in unit (8.2).
The tenslator of high power hydraulic winch the most according to claim 2, it is characterized in that: described first two-way switch valve (9), including solenoid directional control valve (9.1), shuttle valve (9.2) and large-capacity valve core plug-in unit (9.3)；Second two-way switch valve (10), including solenoid directional control valve (10.1), shuttle valve (10.2) and large-capacity valve core plug-in unit (10.3)；3rd two-way switch valve (11), including solenoid directional control valve (11.1) and large-capacity valve core plug-in unit (11.3).
The tenslator of high power hydraulic winch the most according to claim 1, it is characterised in that: described hydraulic power unit, including motor (1), high-pressure pump (2), fuel tank (3), return filter (4)；The inlet port of high-pressure pump (2) is connected with fuel tank (3), the oil-out of high-pressure pump (2) is connected with pressure-compensated valve (6), the oil-out of return filter (4) is connected with fuel tank (3), the oil-in of return filter (4) is connected with the B mouth of counterbalance valve (7) by the MT hydraulic fluid port in control valve group integrated package (18), and high-pressure pump (2) is connected with motor (1) by shaft coupling (2).
The tenslator of high power hydraulic winch the most according to claim 1, it is characterised in that: described electronic controller (17), select Siemens S7-300 series of PLC controller, its model is 315-2DP.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610580567.XA CN106032261B (en) | 2016-07-20 | 2016-07-20 | The tenslator of high power hydraulic winch |
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|---|---|---|---|
| CN201610580567.XA CN106032261B (en) | 2016-07-20 | 2016-07-20 | The tenslator of high power hydraulic winch |
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| CN106032261B CN106032261B (en) | 2018-02-16 |
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| CN108002268A (en) * | 2017-12-21 | 2018-05-08 | 青岛天时海洋石油装备有限公司 | Overload protective device and its method of work |
| CN108035945A (en) * | 2018-01-07 | 2018-05-15 | 浙江高宇液压机电有限公司 | Control valve group for the output of quantitative system flow proportional |
| CN108178082A (en) * | 2017-11-14 | 2018-06-19 | 武汉船用机械有限责任公司 | For the motor control valve group of active compensation of undulation |
| CN108612712A (en) * | 2018-04-10 | 2018-10-02 | 山西大学 | The electro-hydraulic proportional flow valve and control method of active pilot stage control |
| CN108757608A (en) * | 2018-08-20 | 2018-11-06 | 四川宏华石油设备有限公司 | A kind of top drive hydraulic control system |
| CN109162312A (en) * | 2018-09-28 | 2019-01-08 | 徐州徐工基础工程机械有限公司 | A kind of capstan winch torque self-adjusting system, method and diaphragm wall hydraulic chute forming machine |
| CN111532893A (en) * | 2020-06-12 | 2020-08-14 | 中铁电气化局集团有限公司石家庄机械装备分公司 | Constant tension wire barrow of contact net |
| CN112594255A (en) * | 2021-01-26 | 2021-04-02 | 太原理工大学 | High-power load simulation system based on cartridge valve and use method |
| CN113107929A (en) * | 2021-04-15 | 2021-07-13 | 中国铁建重工集团股份有限公司 | Load-sensitive hydraulic circuit |
| CN114314395A (en) * | 2021-12-28 | 2022-04-12 | 江苏政田重工股份有限公司 | Constant tension control system for steel wire rope of hydraulic winch |
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| DE2249479C2 (en) * | 1971-10-09 | 1982-11-04 | Ready Pen Ltd., Derby | Device for controlling the speed and / or the torque of an output shaft |
| CN1456818A (en) * | 2003-06-07 | 2003-11-19 | 杭州浙大德泰电液系统工程有限公司 | Transverse hydraulic control system on dredge boat stem |
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| CN108178082A (en) * | 2017-11-14 | 2018-06-19 | 武汉船用机械有限责任公司 | For the motor control valve group of active compensation of undulation |
| CN108178082B (en) * | 2017-11-14 | 2019-11-15 | 武汉船用机械有限责任公司 | Motor control valve group for active compensation of undulation |
| CN108002268A (en) * | 2017-12-21 | 2018-05-08 | 青岛天时海洋石油装备有限公司 | Overload protective device and its method of work |
| CN107986180A (en) * | 2017-12-21 | 2018-05-04 | 青岛天时海洋石油装备有限公司 | Automatic overload protective device and its method of work |
| CN108035945B (en) * | 2018-01-07 | 2024-04-09 | 浙江高宇液压机电有限公司 | Control valve group for quantitative system flow proportion output |
| CN108035945A (en) * | 2018-01-07 | 2018-05-15 | 浙江高宇液压机电有限公司 | Control valve group for the output of quantitative system flow proportional |
| CN108612712A (en) * | 2018-04-10 | 2018-10-02 | 山西大学 | The electro-hydraulic proportional flow valve and control method of active pilot stage control |
| CN108757608A (en) * | 2018-08-20 | 2018-11-06 | 四川宏华石油设备有限公司 | A kind of top drive hydraulic control system |
| CN109162312A (en) * | 2018-09-28 | 2019-01-08 | 徐州徐工基础工程机械有限公司 | A kind of capstan winch torque self-adjusting system, method and diaphragm wall hydraulic chute forming machine |
| CN111532893A (en) * | 2020-06-12 | 2020-08-14 | 中铁电气化局集团有限公司石家庄机械装备分公司 | Constant tension wire barrow of contact net |
| CN112594255A (en) * | 2021-01-26 | 2021-04-02 | 太原理工大学 | High-power load simulation system based on cartridge valve and use method |
| CN112594255B (en) * | 2021-01-26 | 2022-05-17 | 太原理工大学 | High-power load simulation system based on cartridge valve and use method |
| CN113107929A (en) * | 2021-04-15 | 2021-07-13 | 中国铁建重工集团股份有限公司 | Load-sensitive hydraulic circuit |
| CN114314395A (en) * | 2021-12-28 | 2022-04-12 | 江苏政田重工股份有限公司 | Constant tension control system for steel wire rope of hydraulic winch |
| CN114314395B (en) * | 2021-12-28 | 2024-06-07 | 江苏政田重工股份有限公司 | Constant tension control system for hydraulic winch steel wire rope |
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