CN106032261B - The tenslator of high power hydraulic winch - Google Patents
The tenslator of high power hydraulic winch Download PDFInfo
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- CN106032261B CN106032261B CN201610580567.XA CN201610580567A CN106032261B CN 106032261 B CN106032261 B CN 106032261B CN 201610580567 A CN201610580567 A CN 201610580567A CN 106032261 B CN106032261 B CN 106032261B
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- control valve
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Classifications
-
- 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
-
- 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
-
- 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 kind of tenslator of high power hydraulic winch.Including hydraulic power unit, proportional throttle valve, pressure-compensated valve, counterbalance valve, proportional pressure control valve, three two-way switch valves, two pressure sensings, shuttle valve, velocity sensor, the winch with reduction box, huge discharge hydraulic motor, electronic controller.The electronic controller of this control device can be according to the automatic setting ratio overflow valve of operating mode, achieve the function of balanced valve, tension valve and safety valve, the keying of electronic controller energy automatic control switch valve simultaneously, combined by the different keying of switch valve, the switching of active cable laying oil circuit, active take-up oil circuit, tension force cable laying oil circuit etc. is realized, drastically increases the operability under heavy traffic condition, reliability and the integrated level of control device.In addition, this set control device can realize hydraulic wireline winch working tension and the complex controll of cable length, particularly suitable for the manipulation that various existing tension force requirements have cable length to control desired hydraulic wireline winch in ocean engineering again.
Description
Technical field
The present invention relates to hydraulic drive and control technology, is filled more particularly, to a kind of tension force of high power hydraulic winch
Put.
Background technology
Hydraulic wireline winch is a kind of visual plant in national product, is widely used in ship and other construction industries.With strand
Car nominal load and the continuous improvement to operating rate requirement, drawworks horsepower is increasing, thus required flow is also got over
Come bigger.Hydraulic wireline winch generally uses the proportional direction valve of guiding valve form as its major control element at present, and basic herein
Upper integrated other elements realize tension force, Ioad-sensing control etc..But due to reasons in structure, the proportional direction valve of guiding valve form
It is difficult to big flow (being more than 1000L/min), and often demand 2000L/min is even more for powerful hydraulic wireline winch at this stage
Big flow, for this contradiction, equipment vendors are connected in parallel using the proportional direction valve of two guiding valve forms to meet need more
Ask, but this service condition has the following disadvantages：
1. two proportional direction valve parallel connections are used, due to valve individual manufacturing variation and asynchronous, the appearance of two valve operations
It is excessive and make the operability variation of system to be easily caused a certain valve flow, can seriously cause a wherein valve excessive super due to flow
Cross its power domain and make system malfunction, cause serious production accident.
2. because winch control proportional direction valve integrates other control elements more, being connected in parallel for proportional direction valve causes
Other control elements are also connected in parallel, and are reduced the reliability of system and are added cost.
3. using two proportional direction valve parallel connections, device structure is heavy, bulky, and exterior line connection is complicated.
Although and have in other hydraulic systems big flow inserting form three position four-way directional control valve, it is merely capable of reality
Existing oil circuit simply commutates, it is impossible to meets with tension force function winch active cable laying, actively draws over to one's side, tension force cable laying, passive
Draw over to one's side, the switching of the oil circuit of constant tensile control etc., and it does not possess the function of speed control and tension force, if again on the basis of this
The good advantage of inserted valve integration can not then be played by adding tension valve, balanced valve etc. again, reduced system compactness, added equipment
Cost.
The content of the invention
In order to overcome the existing winch control valve group in above-mentioned background technology under high-power, big flow with operability,
The shortcomings that reliability is poor, it is an object of the invention to provide a kind of tenslator of high power hydraulic winch, it can be used for
High-power, big flow, and in the high hydraulic control device of integrated level, reliability.
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 with reduction box, huge discharge liquid
Pressure motor, electronic controller.
The outlet of the high-pressure pump of hydraulic power unit connects proportional throttle valve respectively by the MP hydraulic fluid ports on control valve group integrated package
A mouths and pressure-compensated valve A mouths, the B mouths connection of the B mouths of pressure-compensated valve and counterbalance valve and by control valve group integrated package
MT hydraulic fluid ports take back fuel tank by return filter, the B mouths of proportional throttle valve A mouths and with first two-way switch valve respectively
The A mouths of two two-way switch valves are connected, the B mouths of the A mouths of counterbalance valve, the B mouths of proportional pressure control valve and the 3rd two-way switch valve
It is connected, the A mouths of proportional pressure control valve are connected and led to first pressure sensor after being connected with the B mouths of first two-way switch valve
The MB hydraulic fluid ports crossed on control valve group integrated package connect the B chambers of huge discharge hydraulic motor, the B mouths of second two-way switch valve and the 3rd
The A mouths of two-way switch valve are connected with second pressure sensor after being connected and connect by the MA hydraulic fluid ports on control valve group integrated package
The A chambers of huge discharge hydraulic motor, the pressure acquisition mouth of shuttle valve pass through MA, MB hydraulic fluid port on control valve group integrated package and big row respectively
A, B chamber of amount hydraulic motor are connected, and the pressure output of shuttle valve is connected with pressure-compensated valve；Huge discharge hydraulic motor subtracts with band
The winch of fast case is connected, and velocity sensor is housed on the winch with reduction box, and electronic controller passes with command signal, speed respectively
Second pressure sensor is electrically connected in first pressure sensor and control valve group integrated package in sensor, control valve group integrated package
Connect.
The 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 sensor second pressure sensor, shuttle
Valve.
The proportional throttle valve, including big flow valve element plug-in unit and proportional pilot valve.
The pressure-compensated valve, including solenoid directional control valve, sequence valve and big flow valve element plug-in unit.
The counterbalance valve, including solenoid directional control valve, overflow valve and big flow valve element plug-in unit.
The proportional pressure control valve, including proportional pilot valve and big flow valve element plug-in unit.
First two-way switch valve, including solenoid directional control valve, shuttle valve and big flow valve element plug-in unit；Second two opens up
Close valve, including solenoid directional control valve, shuttle valve and big flow valve element plug-in unit；3rd two-way switch valve, including solenoid directional control valve and big
Flow valve element plug-in unit.
The hydraulic power unit, including motor, high-pressure pump, fuel tank, return filter；The inlet port of high-pressure pump connects with fuel tank
Connect, 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, and return filter enters
Hydraulic fluid port is connected by the B mouths of the MT hydraulic fluid ports on control valve group integrated package and counterbalance valve, and high-pressure pump is connected by shaft coupling and motor
Connect.
The electronic controller, from Siemens S7-300 series of PLC controllers, its model 315-2DP.
Compared with background technology, one has an advantageous effect in that：
1) control device is made to have good reliability and operability, two-way plug-in valve in big flow using two-way plug-in valve
Maximum control flow up to more than 10000L/min, and its valve port pressuring drop is smaller, device good energy saving property.
2) using electronic controller according to command signal and the sensor signal automatic decision operating mode of collection, and inserting is controlled
Valve guide's solenoid directional control valve realizes the switching of different oil circuits, with adaptation condition.Valve group opens and closes combination flexibly, uses less valve member
More oil circuit combination is produced, drastically increases the integrated level of device.
3) proportional pressure control valve is automatically controlled according to command signal and the sensor signal of collection using electronic controller, makes it
A point ratio serves as overflow valve, safety valve and balanced valve under different operating modes, further increases the integrated level of system.
4) this control device can follow the moment of torsion arbitrarily set or rate curve to be operated automatically, and can be certainly
Systematic parameter in dynamic record construction, improve the automaticity of system.
The invention is particularly suited to various existing tension force requirements in ocean engineering the hydraulic pressure that cable length control requires again
The manipulation of winch.
Brief description of the drawings
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：1st, motor, 2, high-pressure pump, 3, fuel tank, 4, return filter, 5, proportional throttle valve (including large-capacity valve
Core plug-in unit 5.2 and proportional pilot valve 5.1), 6, pressure-compensated valve (including solenoid directional control valve 6.1, leader sequence valve 6.2 and big stream
Measure valve element plug-in unit 6.3), 7, counterbalance valve (including solenoid directional control valve 7.1, overflow valve 7.2 and big flow valve element plug-in unit 7.3), 8, ratio
Example overflow valve (including proportional pilot valve 8.1 and big flow valve element plug-in unit 8.2), 9, first two-way switch valves (including electromagnetism changes
To valve 9.1, shuttle valve 9.2 and big flow valve element plug-in unit 9.3), 10, second two-way switch valves (including solenoid directional control valve 10.1, shuttle
Valve 10.2 and big flow valve element plug-in unit 10.3), 11, the 3rd two-way switch valves (including solenoid directional control valve 11.1 and large-capacity valve
Core plug-in unit 11.2), 12.1, first pressure sensor 12.2, second pressure sensor, 13, shuttle valve, 14, velocity sensor, 15,
Winch with reduction box, 16, huge discharge hydraulic motor, 17, electronic controller, 18, control valve group integrated package.
Embodiment
The present invention is described further with reference to the accompanying drawings and examples.
As shown in figure 1, the present invention includes hydraulic power unit, control valve group integrated package 18, velocity sensor 14, with 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 ratio by the MP hydraulic fluid ports on control valve group integrated package 18 and throttled respectively
The A mouths of valve 5 and the A mouths of pressure-compensated valve 6, the B mouths of pressure-compensated valve 6 are connected with the B mouths of counterbalance valve 7 and by control valve group collection
MT hydraulic fluid ports on blocking 18 take back fuel tank by return filter 4, and the B mouths of proportional throttle valve 5 switch with first two-way respectively
The A mouths of the A mouths of valve 9 and second two-way switch valve 10 are connected, the A mouths of counterbalance valve 7, the B mouths of proportional pressure control valve 8 and the 3rd
The B mouths of two-way switch valve 11 are connected, the A mouths of proportional pressure control valve 8 be connected with the B mouths of first two-way switch valve 9 after with
One pressure sensor 12.1 is connected and the B chambers of huge discharge hydraulic motor 16 are connect by the MB hydraulic fluid ports on control valve group integrated package 18,
The B mouths of second two-way switch valve 10 be connected with the A mouths of the 3rd two-way switch valve 11 after with second pressure sensor
12.2 are connected and connect the A chambers of huge discharge hydraulic motor 16, the pressure of shuttle valve 13 by the MA hydraulic fluid ports on control valve group integrated package 18
Acquisition port is connected by MA, MB hydraulic fluid port on control valve group integrated package 18 with A, B chamber of huge discharge hydraulic motor 16 respectively, shuttle
The pressure output of valve 13 is connected with the outlet of the sequence valve 6.2 of pressure-compensated valve 6；Huge discharge hydraulic motor 16 with reduction box
Winch 15 connect, velocity sensor 14 is housed on the winch 15 with reduction box, electronic controller 17 respectively with command signal, speed
Spend second pressure in sensor 14, first pressure sensor 12.1 and control valve group integrated package 18 in control valve group integrated package 18
Force snesor 12.2 electrically connects.
As shown in Fig. 2 the control valve group integrated package 18, including proportional throttle valve 5, pressure-compensated valve 6, counterbalance valve 7, than
Example overflow valve 8, first two-way switch valve 9, second two-way switch valve 10, the 3rd two-way switch valve 11, first pressure pass
Sensor 12.1, second pressure sensor 12.2, shuttle valve 13.
The proportional throttle valve 5, including big flow valve element plug-in unit 5.2 and proportional pilot valve 5.1, for controlling winch fast
Degree.
The pressure-compensated valve 6, including solenoid directional control valve 6.1, sequence valve 6.2 and big flow valve element plug-in unit 6.3, for unloading
Lotus and progress load-transducing.
The counterbalance valve 7, including solenoid directional control valve 7.1, overflow valve 7.2 and big flow valve element plug-in unit 7.3 are big for controlling
Displacement hydraulic motor back pressure.
The proportional pressure control valve 8, including proportional pilot valve 8.1 and big flow valve element plug-in unit 8.2, for tension force and
Balance Exceed load.
First two-way switch valve 9, including solenoid directional control valve 9.1, shuttle valve 9.2 and big flow valve element plug-in unit 9.3；The
Two two-way switch valves 10, including solenoid directional control valve 10.1, shuttle valve 10.2 and big flow valve element plug-in unit 10.3；3rd two opens up
Valve 11, including solenoid directional control valve 11.1 and big flow valve element plug-in unit 11.3 are closed, three two-way switch valves are used to switching oil
Road.
The hydraulic power unit, including motor 1, high-pressure pump 2, fuel tank 3, return filter 4；The inlet port of high-pressure pump 2 with
Fuel tank 3 is connected, and the oil-out of high-pressure pump 2 is connected with pressure-compensated valve 6, and the oil-out of return filter 4 is connected with fuel tank 3, is returned
The oil inlet of oil strainer 4 is connected with the A mouths of counterbalance valve 7, and high-pressure pump 2 is connected by shaft coupling 2 with motor 1.
The electronic controller, from Siemens S7-300 series of PLC controllers, its model 315-2DP.
Instruction that electronic controller applies according to operator and winch speed signal, the pressure sensor signal collected
Control each pilot valve electromagnet to obtain electric dead electricity, and adjust proportional throttle valve, proportional pressure control valve make system by setting operating mode work；
In addition, electronic controller can also be carried out automatically from the tension force or speed change curves that motion tracking is arbitrarily set and to operational data
Record.
During specific works, first by rule as shown in Figure 3, by speed command, tension force instruction two-way command signal and two
Individual pressure sensor 12.1,12.2, the three-way sensor signal access electronic controller that velocity sensor 14 exports, Electronic Control
Device digital output end is electric with pressure-compensated valve solenoid directional control valve 6.1, counterbalance valve solenoid directional control valve 7.1, two-way switch valve respectively
Magnetic reversal valve 9.1,10.1,11.1 is connected, 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 advised according to command signal and sensor signal according to Fig. 4
Then judge applying working condition, and electric and proportion electro-magnet is obtained according to each pilot valve electromagnet dead electricity of subordinate list rule settings according to operating mode
Signal, most each control signal is output to each control valve according to Fig. 3 relations at last.
Divided working status is illustrated into its specific embodiment below.
Off-load operating mode：Then enter off-load operating mode when electronic controller is not received by any instruction, now except counterbalance valve
Solenoid directional control valve 7.1 is obtained outside electric, and remaining solenoid directional control valve must not be electric, and proportional throttle valve 5 is closed, and proportional pressure control valve 8 is set in
Safe pressure value.Low-pressure load discharge state is in through filter flow reversal fuel tank, system after pump discharge fluid opening pressure-compensated valve 6,
Proportional pressure control valve is used as safety valve, the maximum tension that can be born for setting wirerope.The passing ratio if wirerope overtension
Overflow valve overflow preventing wirerope overload is destroyed, because counterbalance valve solenoid directional control valve 7.1 must be electric, therefore proportional overflow valve outlet fluid
It can not flow back fuel tank and switch valve 11 can be opened to motor low pressure chamber repairing, prevent motor to be emptied.
Active cable laying operating mode：Then enter active cable laying operating mode when electronic controller receives positive speed command, now
Except pressure-compensated valve solenoid directional control valve 6.1 and two-way switch valve solenoid directional control valve 10.1 it is electric in addition to, remaining solenoid directional control valve is not
Must be electric, proportional throttle valve 5 sets its opening degree according to speed command, and pressure-compensated valve 6 is used to ensure the side pressure of proportional throttle valve two
Poor substantially constant is not influenceed by load change, and now the speed of winch is determined by proportional throttle valve opening, and unnecessary flow passes through
Pressure-compensated valve is back to fuel tank.The setting value of proportional pressure control valve 8 is that safe pressure subtracts second signal of pressure sensor 12.2
With the product of Proportional coefficient K set in advance, i.e. motor A mouths pressure is higher, and proportional pressure control valve setting pressure is lower.Now ratio
Overflow valve is used as balanced valve, and energy active balance surmounts load, makes the steady cable laying of winch, safety caused by preventing winch cable laying too fast
Accident.
Active take-up operating mode：Then enter active take-up operating mode when electronic controller receives negative speed command, now
Except pressure-compensated valve solenoid directional control valve 6.1, two-way switch valve solenoid directional control valve 9.1,11.1 it is electric in addition to, remaining solenoid directional control valve is equal
Must not be electric, proportional throttle valve 5 sets its opening degree according to speed command, and pressure-compensated valve 6 is used to ensure proportional throttle valve both ends
Pressure difference substantially constant is not influenceed by load change, and now the speed of winch is determined by proportional throttle valve opening, and unnecessary flow leads to
Excess pressure recuperation valve is back to fuel tank.Proportional pressure control valve 8 is set as that safe pressure is used as safety valve, can be held for setting wirerope
The maximum tension received.Passing ratio overflow valve overflow preventing wirerope overload is destroyed if wirerope overtension.
Tension force cable laying operating mode：When electronic controller receives, tension force instructs and winch speed sensor signal is more than setting value
Shi Ze enters 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 is obtained outside electric, and remaining solenoid directional control valve must not be electric, and proportional throttle valve 5 is set as maximum
Opening, proportional pressure control valve 8 are set by tension force command signal.Now the hydraulic motor of winch by load driving effect in pump condition,
Its moment of torsion that can be provided is set by proportional pressure control valve, and when proportional pressure control valve is set as steady state value, the tension force on wirerope is also kept
It is constant.Hydraulic pump outlet fluid enters the A mouths of hydraulic motor 16 through two-way switch valve 10.Due to the presence of counterbalance valve 7, hydraulic pressure horse
A mouths up to 16 maintain a relatively low pressure to prevent hydraulic motor from producing to be emptied.
Tension force take-up operating mode：When electronic controller receives, tension force instructs and winch speed sensor signal is less than setting value
Shi Ze enters 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 is obtained outside electric, and remaining solenoid directional control valve must not be electric, and proportional throttle valve 5 is set as that maximum is opened
Mouthful, proportional pressure control valve 8 is set by tension force command signal.Now the hydraulic motor of winch is produced by load driving in hydraulic motor B mouths
A raw high pressure, this pressure value is limited by proportional pressure control valve, when proportional pressure control valve is set as steady state value, the tension force on wirerope
Keep constant.Hydraulic pump outlet fluid is partly into the B mouths of hydraulic motor 16 through two-way switch valve 9, and a part is overflow through ratio
Flow valve 8 and the backflow fuel tank of counterbalance valve 7.Due to the presence of counterbalance valve 7, the A mouths of hydraulic motor 16 maintain a relatively low pressure with
Prevent hydraulic motor from producing to be emptied.
In summary, high power hydraulic winch tenslator provided by the invention can effectively overcome existing weaponry and equipment big
Reliability is relatively low under power (maximum up to 5500Kw) or even inoperable shortcoming, improve the operability of equipment with it is reliable
Property, and device integrated level is high, efficiency high, automaticity is high, easy to operate.
Above-mentioned embodiment is used for illustrating the present invention, rather than limits the invention, the present invention's
In spirit and scope of the claims, to any modifications and changes of the invention made, protection model of the invention is both fallen within
Enclose.
Subordinate list：Set each pilot valve electromagnet dead electricity and obtain electric and proportion electro-magnet signal
Claims (9)
1. the tenslator of high power hydraulic winch, it is characterised in that：Including hydraulic power unit, control valve group integrated package
(18), velocity sensor (14), the winch (15) with reduction box, huge discharge hydraulic motor (16), electronic controller (17)；
The outlet of the high-pressure pump (2) of hydraulic power unit connects ratio by the MP hydraulic fluid ports on control valve group integrated package (18) and throttled respectively
The A mouths of valve (5) and the A mouths of pressure-compensated valve (6), the B mouths of pressure-compensated valve (6) are connected with the B mouths of counterbalance valve (7) and pass through control
MT hydraulic fluid ports on valve group integrated package (18) processed take back fuel tank by return filter (4), the B mouths of proportional throttle valve (5) respectively with
The A mouths of first two-way switch valve (9) and the A mouths of second two-way switch valve (10) are connected, the A mouths of counterbalance valve (7), ratio
The B mouths of overflow valve (8) are connected with the B mouths of the 3rd two-way switch valve (11), the A mouths of proportional pressure control valve (8) and first two
The B mouths of logical switch valve (9) are connected and by control valve group integrated package (18) after being connected with first pressure sensor (12.1)
MB hydraulic fluid ports connect the B chambers of huge discharge hydraulic motor (16), the B mouths and the 3rd two-way switch valve of second two-way switch valve (10)
(11) A mouths are connected with second pressure sensor (12.2) after being connected and by the MA oil on control valve group integrated package (18)
Mouth connects the A chambers of huge discharge hydraulic motor (16), and the pressure acquisition mouth of shuttle valve (13) is respectively by control valve group integrated package (18)
MA, MB hydraulic fluid port be connected with A, B chamber of huge discharge hydraulic motor (16), the pressure output and pressure-compensated valve of shuttle valve (13)
(6) it is connected；Huge discharge hydraulic motor (16) is connected with the winch (15) with reduction box, equipped with speed on the winch (15) with reduction box
Spend sensor (14), electronic controller (17) respectively with command signal, velocity sensor (14), control valve group integrated package (18)
First pressure sensor (12.1) and control valve group integrated package (18) in the electrical connection of second pressure sensor (12.2).
2. the tenslator of high power hydraulic winch according to claim 1, it is characterised in that：The 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), first pressure sensor (12.1), second
Pressure sensor (12.2), shuttle valve (13).
3. the tenslator of high power hydraulic winch according to claim 2, it is characterised in that：The ratio throttling
Valve (5), including big flow valve element plug-in unit (5.2) and proportional pilot valve (5.1).
4. the tenslator of high power hydraulic winch according to claim 2, it is characterised in that：The pressure compensation
Valve (6), including solenoid directional control valve (6.1), sequence valve (6.2) and big flow valve element plug-in unit (6.3).
5. the tenslator of high power hydraulic winch according to claim 2, it is characterised in that：The counterbalance valve
, including solenoid directional control valve (7.1), overflow valve (7.2) and big flow valve element plug-in unit (7.3) (7).
6. the tenslator of high power hydraulic winch according to claim 2, it is characterised in that：The proportional overflow
Valve (8), including proportional pilot valve (8.1) and big flow valve element plug-in unit (8.2).
7. the tenslator of high power hydraulic winch according to claim 2, it is characterised in that：Described first two
Logical switch valve (9), including solenoid directional control valve (9.1), shuttle valve (9.2) and big flow valve element plug-in unit (9.3)；Second two-way switch
Valve (10), including solenoid directional control valve (10.1), shuttle valve (10.2) and big flow valve element plug-in unit (10.3)；3rd two-way switch valve
, including solenoid directional control valve (11.1) and big flow valve element plug-in unit (11.3) (11).
8. the tenslator of high power hydraulic winch according to claim 1, it is characterised in that：The hydraulic pump
Stand, including motor (1), high-pressure pump (2), fuel tank (3), return filter (4)；The inlet port of high-pressure pump (2) connects with fuel tank (3)
Connect, the oil-out of high-pressure pump (2) is connected with pressure-compensated valve (6), and the oil-out of return filter (4) is connected with fuel tank (3), is returned
The oil inlet of oil strainer (4) is connected by the MT hydraulic fluid ports on control valve group integrated package (18) with the B mouths of counterbalance valve (7), high pressure
Pump (2) is connected by shaft coupling with motor (1).
9. the tenslator of high power hydraulic winch according to claim 1, it is characterised in that：The Electronic Control
Device (17), from Siemens S7-300 series of PLC controllers, its model 315-2DP.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610580567.XA CN106032261B (en) | 2016-07-20 | 2016-07-20 | The tenslator of high power hydraulic winch |
Applications Claiming Priority (1)
| 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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| Publication Number | Publication Date |
|---|---|
| CN106032261A CN106032261A (en) | 2016-10-19 |
| CN106032261B true CN106032261B (en) | 2018-02-16 |
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| CN201610580567.XA Expired - Fee Related CN106032261B (en) | 2016-07-20 | 2016-07-20 | The tenslator of high power hydraulic winch |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| CN107986180B (en) * | 2017-12-21 | 2023-05-09 | 青岛天时海洋石油装备有限公司 | Automatic overload protection system and working method thereof |
| CN108002268B (en) * | 2017-12-21 | 2023-05-09 | 青岛天时海洋石油装备有限公司 | Overload protection system and working method thereof |
| 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 |
| CN108612712B (en) * | 2018-04-10 | 2020-06-12 | 山西大学 | Electro-hydraulic proportional flow valve for active pilot control and control method |
| 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 |
| 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 |
| CN113107929B (en) * | 2021-04-15 | 2023-06-30 | 中国铁建重工集团股份有限公司 | Load sensitive hydraulic circuit |
| 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 |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1409661A (en) * | 1971-10-09 | 1975-10-08 | Philpott Arthur | Transmission assembly |
| CN1190598C (en) * | 2003-06-07 | 2005-02-23 | 杭州浙大德泰电液系统工程有限公司 | Transverse hydraulic control system on dredge boat stem |
| CN203753367U (en) * | 2013-12-25 | 2014-08-06 | 宁波捷胜海洋开发有限公司 | Hydraulic system for hauling machines of fishing boat |
| CN105329796B (en) * | 2015-12-08 | 2017-08-11 | 南通大学 | A kind of compressed air hoist active compensation device and control method |
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2016
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