CN106032261A - Tension Control Device of High Power Hydraulic Winch - Google Patents

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

Tension Control Device of High Power Hydraulic Winch

technical field

The invention relates to hydraulic transmission and control technology, in particular to a tension control device of a high-power hydraulic winch.

Background technique

Hydraulic winch is an important equipment in national production, widely used in ships and other engineering industries. With the continuous improvement of the rated load of the winch and the requirement for the working speed, the power of the winch is getting bigger and bigger, so the flow required is also getting bigger and bigger. At present, hydraulic winches generally use proportional directional valves in the form of slide valves as their main control components, and on this basis, other components are integrated to achieve tension control, load sensing control, etc. However, due to structural reasons, it is difficult for a proportional directional valve in the form of a slide valve to achieve a large flow rate (greater than 1000L/min), and the current high-power hydraulic winch often requires a flow rate of 2000L/min or even greater. For this contradiction, equipment manufacturers Two proportional directional valves in the form of slide valves are usually connected in parallel to meet the demand, but this usage has the following disadvantages:

1. If two proportional directional valves are used in parallel, due to the individual manufacturing differences of the valves and the asynchronous operation of the two valves, it is easy to cause the flow rate of one valve to be too large and the operability of the system to deteriorate. If the flow is too large and exceeds its power domain, the system will malfunction and cause serious production accidents.

2. Since the proportional directional valve for winch control is mostly integrated with other control components, the parallel connection of the proportional directional valve leads to the parallel connection of other control components, which reduces the reliability of the system and increases the cost.

3. Using two proportional directional valves connected in parallel, the equipment structure is bulky, bulky, and the external pipeline connection is complicated.

In other hydraulic systems, although there are three-position four-way reversing valves in the form of large-flow cartridges, they can only realize simple reversing of the oil circuit, and cannot meet the requirements of active cable release, active retraction, and tension control of the winch with tension control functions. Oil circuit switching for cable unwinding, passive retraction, constant tension control, etc., and it does not have the functions of speed control and tension control. If tension valves, balance valves, etc. are added on this basis, the good integration of cartridge valves cannot be used. Advantages reduce system compactness and increase equipment cost.

Contents of the invention

In order to overcome the disadvantages of poor operability and reliability of the existing winch control valve group in the above-mentioned background technology under high power and large flow, the purpose of the present invention is to provide a tension control device for a high-power hydraulic winch, which can be used for High power, large flow, and high integration and reliability in hydraulic control devices.

In order to achieve the above-mentioned purpose of the invention, the technical scheme adopted in the present invention is:

The invention includes a hydraulic pump station, a control valve group integrated block, a speed sensor, a winch with a reduction box, a large-displacement hydraulic motor, and an electronic controller.

The outlet of the high-pressure pump of the hydraulic pump station is respectively connected to the A port of the proportional throttle valve and the A port of the pressure compensation valve through the MP port on the control valve group manifold, and the B port of the pressure compensation valve is connected to the B port of the back pressure valve And through the MT oil port on the manifold block of the control valve group, it is connected back to the oil tank through the oil return filter, and the B port of the proportional throttle valve is respectively connected with the A port of the first two-way on-off valve and the A port of the second two-way on-off valve. The A port of the back pressure valve and the B port of the proportional relief valve are connected with the B port of the third two-way switch valve, and the A port of the proportional relief valve is connected with the B port of the first two-way switch valve. After being connected, it is connected to the first pressure sensor and connected to the B chamber of the large displacement hydraulic motor through the MB oil port on the control valve group manifold, and the B port of the second two-way switch valve is connected to the third two-way switch valve. After the port A is connected, it is connected to the second pressure sensor and connected to the A chamber of the large-displacement hydraulic motor through the MA oil port on the control valve group manifold. , MB oil ports are connected with A and B cavities of the large displacement hydraulic motor, the pressure output port of the shuttle valve is connected with the pressure compensation valve; The speed sensor and the electronic controller are respectively electrically connected with the command signal, the speed sensor, the first pressure sensor in the control valve group manifold and the second pressure sensor in the control valve group manifold.

The control valve group manifold includes a proportional throttle valve, a pressure compensation valve, a back pressure valve, a proportional relief valve, the first two-way on-off valve, the second two-way on-off valve, and the third two-way on-off valve , the first pressure sensor, the second pressure sensor, the shuttle valve.

The proportional throttle valve includes a large flow spool insert and a proportional pilot valve.

The pressure compensation valve includes an electromagnetic reversing valve, a sequence valve and a large-flow spool insert.

The back pressure valve includes an electromagnetic reversing valve, a relief valve and a large-flow spool insert.

The proportional relief valve includes a proportional pilot valve and a large-flow spool insert.

The first two-way switch valve includes an electromagnetic reversing valve, a shuttle valve and a large-flow spool plug-in; the second two-way switch valve includes an electromagnetic reversing valve, a shuttle valve and a large-flow spool plug-in; the third A two-way on-off valve, including an electromagnetic reversing valve and a large flow spool plug-in.

The hydraulic pump station includes a motor, a high-pressure pump, an oil tank, and an oil return filter; the oil suction port of the high-pressure pump is connected to the oil tank, the oil outlet of the high-pressure pump is connected to the pressure compensation valve, and the oil outlet of the oil return filter is connected to the oil tank Connection, the oil inlet of the oil return filter is connected to the B port of the back pressure valve through the MT oil port on the control valve group manifold, and the high pressure pump is connected to the motor through a coupling.

Described electronic controller selects Siemens S7-300 series PLC controller for use, and its model is 315-2DP.

Compared with the background technology, one beneficial effect is:

1) The use of two-way cartridge valves makes the control device have good reliability and operability at large flow rates. The maximum control flow rate of two-way cartridge valves can reach more than 10,000L/min, and the pressure drop at the valve port is small. The device has good energy saving performance.

2) The electronic controller is used to automatically judge the working condition according to the command signal and the collected sensor signal, and control the cartridge valve pilot electromagnetic reversing valve to realize the switching of different oil circuits to adapt to the working condition. The opening and closing combination of the valve group is flexible, and the use of fewer valves produces more oil circuit combinations, which greatly improves the integration of the device.

3) The electronic controller is used to automatically control the proportional relief valve according to the command signal and the collected sensor signal, so that it can act as the relief valve, safety valve and balance valve in proportion under different working conditions, which further improves the integration of the system.

4) The control device can automatically follow any set torque or speed curve to work, and can automatically record the system parameters during construction, which improves the degree of automation of the system.

The invention is particularly suitable for the manipulation of various hydraulic winches in marine engineering that require both tension control and cable length control.

Description of drawings

Fig. 1 is a system structure diagram of the present invention.

Figure 2 is a schematic diagram of the control valve group manifold.

Figure 3 is a schematic diagram of the signal wiring of the electronic controller.

Fig. 4 is a flow chart for judging the working condition of the electronic controller.

In the figure: 1. Electric motor, 2. High-pressure pump, 3. Fuel tank, 4. Oil return filter, 5. Proportional throttle valve (including large flow spool insert 5.2 and proportional pilot valve 5.1), 6. Pressure compensation valve ( Including electromagnetic reversing valve 6.1, pilot sequence valve 6.2 and large flow spool insert 6.3), 7. Back pressure valve (including electromagnetic directional valve 7.1, overflow valve 7.2 and large flow spool insert 7.3), 8. Proportional overflow Flow valve (including proportional pilot valve 8.1 and large flow spool insert 8.2), 9. The first two-way switch valve (including electromagnetic reversing valve 9.1, shuttle valve 9.2 and large flow spool insert 9.3), 10. The second A two-way on-off valve (including electromagnetic reversing valve 10.1, shuttle valve 10.2 and large flow spool plug-in 10.3), 11, the third two-way on-off valve (including electromagnetic reversing valve 11.1 and high-flow spool plug-in 11.2), 12.1, first pressure sensor 12.2, second pressure sensor, 13, shuttle valve, 14, speed sensor, 15, winch with reduction box, 16, large displacement hydraulic motor, 17, electronic controller, 18, control valve group Manifold.

detailed description

The present invention will be further described below in conjunction with the accompanying drawings and embodiments.

As shown in FIG. 1 , the present invention includes a hydraulic pump station, a control valve group manifold 18 , a speed sensor 14 , a winch 15 with a reduction box, a large-displacement hydraulic motor 16 , and an electronic controller 17 .

The outlet of the high-pressure pump 2 of the hydraulic pump station is respectively connected to the A port of the proportional throttle valve 5 and the A port of the pressure compensation valve 6 through the MP port on the control valve group manifold 18, and the B port of the pressure compensation valve 6 is connected to the back pressure port. The B port of the valve 7 is connected and connected to the oil tank through the MT oil port on the control valve group manifold 18 through the oil return filter 4, and the B port of the proportional throttle valve 5 is connected to the A port of the first two-way switch valve 9 respectively. It is connected to port A of the second two-way switch valve 10, port A of the back pressure valve 7, and port B of the proportional relief valve 8 are connected to port B of the third two-way switch valve 11, and the proportional relief valve The A port of 8 is connected with the B port of the first two-way switch valve 9 and then connected with the first pressure sensor 12.1 and connected with the B chamber of the large-displacement hydraulic motor 16 through the MB oil port on the control valve group manifold 18, Port B of the second two-way on-off valve 10 is connected to port A of the third two-way on-off valve 11, and then connected to the second pressure sensor 12.2 and connected to the large exhaust port through the MA oil port on the manifold block 18 of the control valve group. The chamber A of the volume hydraulic motor 16 and the pressure collection port of the shuttle valve 13 are respectively connected to the chambers A and B of the large displacement hydraulic motor 16 through the MA and MB oil ports on the control valve group manifold 18. The pressure of the shuttle valve 13 The output port is connected to the outlet of the sequence valve 6.2 of the pressure compensation valve 6; the large displacement hydraulic motor 16 is connected to the winch 15 with a reduction box, the winch 15 with a reduction box is equipped with a speed sensor 14, and the electronic controller 17 communicates with the command signal respectively. , the speed sensor 14, the first pressure sensor 12.1 in the control valve group manifold 18 and the second pressure sensor 12.2 in the control valve manifold 18 are electrically connected.

As shown in Figure 2, the control valve group manifold 18 includes a proportional throttle valve 5, a pressure compensation valve 6, a back pressure valve 7, a proportional relief valve 8, a first two-way switch valve 9, a second Two-way switching valve 10, a third two-way switching valve 11, a first pressure sensor 12.1, a second pressure sensor 12.2, and a shuttle valve 13.

The proportional throttle valve 5 includes a large flow spool insert 5.2 and a proportional pilot valve 5.1, which are used to control the speed of the winch.

The pressure compensation valve 6 includes an electromagnetic reversing valve 6.1, a sequence valve 6.2 and a large flow spool insert 6.3, which are used for unloading and load sensing.

The back pressure valve 7 includes an electromagnetic reversing valve 7.1, a relief valve 7.2 and a large flow spool insert 7.3, which are used to control the back pressure of a large displacement hydraulic motor.

The proportional relief valve 8 includes a proportional pilot valve 8.1 and a large flow spool insert 8.2, which are used for tension control and balancing overrunning loads.

The first two-way switch valve 9 includes an electromagnetic reversing valve 9.1, a shuttle valve 9.2 and a large flow spool insert 9.3; the second two-way on-off valve 10 includes an electromagnetic reversing valve 10.1, a shuttle valve 10.2 and a large flow valve. The flow spool plug-in 10.3; the third two-way on-off valve 11 includes an electromagnetic reversing valve 11.1 and a large-flow spool plug-in 11.3, and the three two-way on-off valves are all used to switch the oil circuit.

The hydraulic pump station includes a motor 1, a high-pressure pump 2, an oil tank 3, and an oil return filter 4; the oil suction port of the high-pressure pump 2 is connected to the oil tank 3, and the oil outlet of the high-pressure pump 2 is connected to the pressure compensation valve 6, and the oil return The oil outlet of the filter 4 is connected with the oil tank 3 , the oil inlet of the oil return filter 4 is connected with the A port of the back pressure valve 7 , and the high pressure pump 2 is connected with the motor 1 through the coupling 2 .

Described electronic controller selects Siemens S7-300 series PLC controller for use, and its model is 315-2DP.

The electronic controller controls the electromagnets of the pilot valves to be energized and de-energized according to the instructions imposed by the operator and the collected winch speed signals and pressure sensor signals, and adjusts the proportional throttle valve and proportional relief valve to make the system operate according to the set working conditions. Work; In addition, the electronic controller can also automatically track the tension or speed change curve set arbitrarily and automatically record the working data.

During the specific work, at first according to the rules shown in Figure 3, the speed command, the two-way command signal of the tension command and two pressure sensors 12.1, 12.2, the three-way sensor signal output by the speed sensor 14 are connected to the electronic controller, and the electronic controller The digital output terminals are respectively connected with the electromagnetic reversing valve 6.1 of the pressure compensation valve, the electromagnetic reversing valve 7.1 of the back pressure valve, and the electromagnetic reversing valves 9.1, 10.1, and 11.1 of the two-way switch valve. The analog output terminals of the electronic controller are respectively connected with the proportional Throttle valve proportional pilot valve 5.1 and proportional relief valve proportional pilot valve 8.1 are connected; the electronic controller judges the working conditions according to the rules in Figure 4 according to the command signal and sensor signal, and sets each pilot valve according to the rules in the attached table according to the working conditions The electromagnet loses power and is energized and the proportional electromagnet signal finally outputs each control signal to each control valve according to the relationship in Figure 3.

Its specific implementation scheme will be described below in terms of working conditions.

Unloading working condition: When the electronic controller does not receive any instructions, it enters the unloading working condition. At this time, except the electromagnetic reversing valve 7.1 of the back pressure valve is energized, the rest of the electromagnetic reversing valves are not energized, and the proportional throttle valve 5 is closed, and the proportional relief valve 8 is set at a safe pressure value. The oil at the pump outlet opens the pressure compensation valve 6 and returns to the oil tank through the filter. The system is in a low-pressure unloading state. The proportional relief valve is used as a safety valve to set the maximum tension that the steel cable can bear. If the tension of the steel cable is too large, the overflow of the proportional relief valve will prevent the cable from being overloaded and damaged. Since the electromagnetic reversing valve 7.1 of the back pressure valve is energized, the oil at the outlet of the proportional relief valve cannot return to the oil tank and the switch valve 11 will be opened. The low-pressure chamber of the motor is replenished with oil to prevent the motor from sucking air.

Active cable unwinding working condition: When the electronic controller receives a positive speed command, it enters the active cable unwinding working condition. At this time, except that the pressure compensation valve electromagnetic reversing valve 6.1 and the two-way switching valve electromagnetic reversing valve 10.1 are energized, The rest of the electromagnetic reversing valves are not powered. The proportional throttle valve 5 sets its opening according to the speed command. The pressure compensation valve 6 is used to ensure that the pressure difference between the two ends of the proportional throttle valve is basically constant and will not be affected by the load change. At this time, the drawworks The speed is determined by the opening of the proportional throttle valve, and the excess flow is returned to tank through the pressure compensating valve. The setting value of the proportional relief valve 8 is the safety pressure minus the product of the signal of the second pressure sensor 12.2 and the preset proportional coefficient K, that is, the higher the pressure at the port A of the motor, the lower the setting pressure of the proportional relief valve. At this time, the proportional overflow valve is used as a balance valve, which can effectively balance the excess load, make the winch unwind the cable smoothly, and prevent safety accidents caused by the winch unwinding the cable too fast.

Active cable take-up working condition: When the electronic controller receives a negative speed command, it enters the active cable take-up working condition. At this time, the electromagnetic reversing valve 6.1 of the pressure compensation valve and the electromagnetic reversing valve 9.1 and 11.1 of the two-way switching valve are energized. In addition, the rest of the electromagnetic reversing valves are not powered, the proportional throttle valve 5 sets its opening according to the speed command, and the pressure compensation valve 6 is used to ensure that the pressure difference between the two ends of the proportional throttle valve is basically constant and will not be affected by load changes. The speed of the winch is determined by the opening of the proportional throttle valve, and the excess flow is returned to the tank through the pressure compensating valve. Proportional overflow valve 8 is set as safety pressure and is used as safety valve, is used for setting the maximum tension force that steel cable can bear. If the tension of the steel cable is too high, the proportional overflow valve will overflow to prevent the cable from being overloaded and damaged.

Tension cable release working condition: When the electronic controller receives the tension command and the winch speed sensor signal is greater than the set value, it enters the tension cable release working condition. At this time, except for the pressure compensation valve electromagnetic reversing valve 6.1, the back pressure valve Valve 7.1 and two-way switching valve electromagnetic reversing valve 10.1, 11.1 are energized, other electromagnetic reversing valves are not energized, the proportional throttle valve 5 is set to the maximum opening, and the proportional overflow valve 8 is set by the tension command signal. At this time, the hydraulic motor of the drawworks is driven by the load to act on the pump, and the torque it can provide is set by the proportional relief valve. When the proportional relief valve is set to a constant value, the tension on the cable is also kept constant. Oil at the outlet of the hydraulic pump enters port A of the hydraulic motor 16 through the two-way switch valve 10 . Due to the existence of the back pressure valve 7, the A port of the hydraulic motor 16 maintains a lower pressure to prevent the hydraulic motor from generating cavitation.

Tension cable take-up working condition: When the electronic controller receives the tension command and the winch speed sensor signal is less than the set value, it enters the tension cable take-up working condition. Valve 7.1 and two-way on-off valve electromagnetic reversing valve 9.1, 11.1 are energized, other electromagnetic reversing valves are not energized, the proportional throttle valve 5 is set to the maximum opening, and the proportional overflow valve 8 is set by the tension command signal. At this time, the hydraulic motor of the drawworks is driven by the load to generate a high pressure at the B port of the hydraulic motor. This pressure value is limited by the proportional relief valve. When the proportional relief valve is set to a constant value, the tension on the cable also remains constant. Part of the oil at the outlet of the hydraulic pump enters the B port of the hydraulic motor 16 through the two-way switch valve 9, and part of it flows back to the oil tank through the proportional overflow valve 8 and the back pressure valve 7. Due to the existence of the back pressure valve 7, the A port of the hydraulic motor 16 maintains a lower pressure to prevent the hydraulic motor from generating cavitation.

To sum up, the high-power hydraulic winch tension control device provided by the present invention can effectively overcome the shortcomings of existing equipment with low reliability or even failure to work under high power (up to 5500Kw), and improve the operability and reliability of the equipment. Sex, and the device has high integration, high efficiency, high degree of automation and convenient operation.

The above specific embodiments are used to explain the present invention, rather than to limit the present invention. Within the spirit of the present invention and the protection scope of the claims, any modification and change made to the present invention will fall into the protection scope of the present invention.

Attached table: Set each pilot valve electromagnet power-off and power-on and proportional electromagnet signal

Claims (9)

1. The tension control device of a high-power hydraulic winch, characterized in that it includes a hydraulic pump station, a control valve group manifold (18), a speed sensor (14), a winch with a reduction box (15), a large displacement hydraulic motor ( 16), electronic controller (17); The outlet of the high-pressure pump (2) of the hydraulic pump station is respectively connected to the A port of the proportional throttle valve (5) and the A port of the pressure compensation valve (6) through the MP port on the control valve group manifold (18). The B port of the valve (6) is connected to the B port of the back pressure valve (7) and connected back to the oil tank through the MT oil port on the control valve group manifold (18) through the oil return filter (4), and the proportional throttle valve ( 5) port B is respectively connected to port A of the first two-way switch valve (9) and port A of the second two-way switch valve (10), and port A of the back pressure valve (7) and the proportional overflow Port B of the valve (8) is connected to port B of the third two-way switch valve (11), and port A of the proportional relief valve (8) is connected to port B of the first two-way switch valve (9) After that, it is connected to the first pressure sensor (12.1) and connected to the B chamber of the large displacement hydraulic motor (16) through the MB oil port on the control valve group manifold (18), and the B chamber of the second two-way switch valve (10). The port is connected to the A port of the third two-way switch valve (11) and then connected to the second pressure sensor (12.2) and connected to the large displacement hydraulic motor ( 16), the pressure collection ports of the shuttle valve (13) are respectively connected to the A and B chambers of the large displacement hydraulic motor (16) through the MA and MB oil ports on the control valve group manifold (18), and the shuttle The pressure output port of the valve (13) is connected to the pressure compensating valve (6); the large displacement hydraulic motor (16) is connected to the winch (15) with the reduction box, and the speed sensor (14) is installed on the winch (15) with the reduction box ), the electronic controller (17) is respectively connected with the command signal, the speed sensor (14), the first pressure sensor (12.1) in the control valve manifold (18) and the second pressure sensor (18) in the control valve manifold (18) The sensor (12.2) is electrically connected. 2. The tension control device of a high-power hydraulic winch according to claim 1, characterized in that: the control valve group manifold (18) includes a proportional throttle valve (5), a pressure compensation valve (6), and a back pressure valve (7), proportional relief valve (8), the first two-way on-off valve (9), the second two-way on-off valve (10), the third two-way on-off valve (11), the first pressure Sensor (12.1), second pressure sensor (12.2), shuttle valve (13). 3. The tension control device of a high-power hydraulic winch according to claim 2, characterized in that: the proportional throttle valve (5) includes a large-flow spool insert (5.2) and a proportional pilot valve (5.1). 4. The tension control device of a high-power hydraulic winch according to claim 2, characterized in that: the pressure compensation valve (6) includes an electromagnetic reversing valve (6.1), a sequence valve (6.2) and a large flow valve core Plugins (6.3). 5. The tension control device of a high-power hydraulic winch according to claim 2, characterized in that: the back pressure valve (7) includes an electromagnetic reversing valve (7.1), an overflow valve (7.2) and a large flow valve Core insert (7.3). 6. The tension control device of a high-power hydraulic winch according to claim 2, characterized in that: the proportional relief valve (8) includes a proportional pilot valve (8.1) and a large flow spool insert (8.2). 7. The tension control device of a high-power hydraulic winch according to claim 2, characterized in that: the first two-way switching valve (9) includes an electromagnetic reversing valve (9.1), a shuttle valve (9.2) and Large flow spool insert (9.3); the second two-way switch valve (10), including electromagnetic reversing valve (10.1), shuttle valve (10.2) and large flow spool insert (10.3); the third two-way switch The valve (11) includes an electromagnetic reversing valve (11.1) and a large flow spool insert (11.3). 8. The tension control device of the high-power hydraulic winch according to claim 1, characterized in that: the hydraulic pump station includes an electric motor (1), a high-pressure pump (2), an oil tank (3), and an oil return filter ( 4); the oil suction port of the high-pressure pump (2) is connected to the oil tank (3), the oil outlet of the high-pressure pump (2) is connected to the pressure compensation valve (6), and the oil outlet of the oil return filter (4) is connected to the oil tank ( 3) Connection, the oil inlet of the oil return filter (4) is connected to the B port of the back pressure valve (7) through the MT oil port on the control valve group manifold (18), and the high pressure pump (2) is connected through the coupling (2) Connect with the motor (1). 9. The tension control device of a high-power hydraulic winch according to claim 1, characterized in that: the electronic controller (17) is a Siemens S7-300 series PLC controller, and its model is 315-2DP.