CN109114053B - Multi-winch hydraulic system - Google Patents
Multi-winch hydraulic system Download PDFInfo
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- CN109114053B CN109114053B CN201811015785.4A CN201811015785A CN109114053B CN 109114053 B CN109114053 B CN 109114053B CN 201811015785 A CN201811015785 A CN 201811015785A CN 109114053 B CN109114053 B CN 109114053B
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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
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
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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
- B66D1/02—Driving gear
- B66D1/08—Driving gear incorporating fluid motors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
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- 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
- F15B2211/2053—Type of pump
- F15B2211/20538—Type of pump constant capacity
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a multi-winch hydraulic system, and belongs to the technical field of hydraulic control. The hydraulic system comprises a main pump group, three proportional valves, two electromagnetic valves and three hydraulic motors. The three proportional valves are three-position six-way valves, the three proportional valves are in one-to-one correspondence with the three hydraulic motors, the proportional valves can control the pressure and the flow of hydraulic oil output by the main pump group and then output the hydraulic oil to the corresponding hydraulic motors, the hydraulic motors are used for driving the winches, the two electromagnetic valves can control the series-parallel connection of the three proportional valves, the main pump group can change the size and the sequence of the hydraulic oil provided for the three hydraulic motors by changing the series-parallel connection relation among the three proportional valves, the multiple winches can be driven according to the working priorities of the multiple winches, and therefore the multiple winches can be driven by only setting one set of hydraulic system, the manufacturing cost of a marine platform is saved, the structure is simple, and the operation is convenient.
Description
Technical Field
The invention relates to the technical field of hydraulic control, in particular to a multi-winch hydraulic system.
Background
At present, on a maritime work platform, a plurality of winches are generally configured to work cooperatively or independently. Mainly comprising a platform hoisting winch, a traction winch, a tension winch, an auxiliary winch and the like, which are usually driven by a hydraulic system.
The working priority of the winch in the plurality of winches on the maritime work platform is higher, and the working priority of some winches is lower. For the winches with high priority level need to be driven preferentially, therefore, in order to meet the working priority level of each winch, a method is usually adopted in which a set of hydraulic system is provided for each winch, and each set of hydraulic system drives the corresponding winch to work individually, so as to meet the requirement of the priority level of the winch.
In the process of implementing the invention, the inventor finds that the prior art has at least the following problems:
the installation of a hydraulic system for each winch increases the manufacturing cost of the marine platform. Meanwhile, when a plurality of winches are driven to work, the hydraulic systems corresponding to the winches need to be controlled in sequence, the operation is complex, and errors are easy to occur.
Disclosure of Invention
The embodiment of the invention provides a multi-winch hydraulic system which can drive a winch according to the working priority of the winch, saves the manufacturing cost of a platform, is simple to operate and is not easy to make mistakes. The technical scheme is as follows:
the invention provides a multi-winch hydraulic system which comprises a main pump set, three proportional valves, two electromagnetic valves and three hydraulic motors, wherein the three proportional valves are three-position six-way valves, the three proportional valves and the three hydraulic motors are arranged in a one-to-one correspondence manner, the three proportional valves comprise a first proportional valve, a second proportional valve and a third proportional valve, and the two electromagnetic valves comprise a first electromagnetic valve and a second electromagnetic valve;
the PP1 port of the first proportional valve is communicated with the output end of the main pump group, the PT1 port of the first proportional valve is communicated with the PP2 port of the second proportional valve, the PT2 port of the second proportional valve is communicated with the PP3 port of the third proportional valve, and the PT3 port of the third proportional valve is communicated with a fuel tank;
the ports A of the three proportional valves are communicated with the ports A of the corresponding hydraulic motors, the ports B of the three proportional valves are communicated with the ports B of the corresponding hydraulic motors, and the ports T of the three proportional valves are communicated with the oil tank;
the port P1 of the first proportional valve is communicated with the output end of the main pump group, one end of the first electromagnetic valve is communicated with the output end of the main pump group, the other end of the first electromagnetic valve is communicated with one end of the second electromagnetic valve, the other end of the second electromagnetic valve is communicated with the port P3 of the third proportional valve, the other end of the first electromagnetic valve is also communicated with the ports PP2 and P2 of the second proportional valve respectively, and one end of the second electromagnetic valve is also communicated with the port PP3 of the third proportional valve.
Further, the main pump group comprises a motor and an electric proportional valve, and the electric proportional valve is used for controlling the pressure and the flow of hydraulic oil output by the motor.
Furthermore, the main pump unit further comprises a safety valve, an oil inlet of the safety valve is communicated with an output end of the motor, an oil outlet of the safety valve is communicated with the oil tank, and a control oil port of the safety valve is communicated with an oil inlet of the safety valve.
Further, the threshold value of the safety valve is determined based on the maximum working pressure of the three hydraulic motor-driven winches and the pressure loss of the hydraulic system along the way.
Furthermore, the hydraulic system further comprises a first two-way pressure compensator and a first shuttle valve, an oil inlet of the first two-way pressure compensator is communicated with an output end of the main pump set, an oil outlet of the first two-way pressure compensator is communicated with a P port of the first proportional valve, and a first control oil port of the first two-way pressure compensator is communicated with an oil inlet of the first two-way pressure compensator;
an oil inlet of the first shuttle valve is communicated with the port A of the first proportional valve, an oil outlet of the first shuttle valve is communicated with the port B of the first proportional valve, and a control oil port of the first shuttle valve is communicated with a second control oil port of the first two-way pressure compensator.
Furthermore, the hydraulic system further comprises a second two-way pressure compensator and a second shuttle valve, an oil inlet of the second two-way pressure compensator is communicated with the other end of the first electromagnetic valve, an oil outlet of the second two-way pressure compensator is communicated with a port P of the second proportional valve, and a first control oil port of the second two-way pressure compensator is communicated with an oil inlet of the second two-way pressure compensator;
an oil inlet of the second shuttle valve is communicated with the port A of the second proportional valve, an oil outlet of the second shuttle valve is communicated with the port B of the second proportional valve, and a control oil port of the second shuttle valve is communicated with a second control oil port of the second two-way pressure compensator.
Furthermore, the hydraulic system further comprises a third two-way pressure compensator and a third shuttle valve, an oil inlet of the third two-way pressure compensator is communicated with the other end of the second electromagnetic valve, an oil outlet of the third two-way pressure compensator is communicated with a port P of the third proportional valve, and a first control oil port of the third two-way pressure compensator is communicated with an oil inlet of the third two-way pressure compensator;
an oil inlet of the third shuttle valve is communicated with the port A of the third proportional valve, an oil outlet of the third shuttle valve is communicated with the port B of the third proportional valve, and a control oil port of the third shuttle valve is communicated with a second control oil port of the third two-way pressure compensator.
Furthermore, each hydraulic system further comprises three overflow valves respectively connected with the three hydraulic motors in parallel, an oil inlet of each overflow valve is communicated with the port A of the hydraulic motor, an oil outlet of each overflow valve is communicated with the port B of the hydraulic motor, a first control oil port of each overflow valve is communicated with an oil inlet of each overflow valve, and a second control oil port of each overflow valve is communicated with an oil outlet of each overflow valve.
Further, when the first electromagnetic valve is electrified, the first proportional valve and the second proportional valve are connected in parallel, and when the first electromagnetic valve is not electrified, the first proportional valve and the second proportional valve are connected in series;
when the second electromagnetic valve is electrified, the second proportional valve and the third proportional valve are connected in parallel, and when the second electromagnetic valve is not electrified, the second proportional valve and the third proportional valve are connected in series.
Further, all three hydraulic motors are bidirectional constant-displacement motors.
The technical scheme provided by the embodiment of the invention has the following beneficial effects:
through setting up a hydraulic system, this hydraulic system includes main pump package, three proportional valve, two solenoid valves and three hydraulic motor, and three proportional valve is three-position six-way valve, and three proportional valve and three hydraulic motor one-to-one set up. The proportional valve can control the pressure and the flow of the hydraulic oil output by the main pump group and then output the hydraulic oil to a corresponding hydraulic motor, and the hydraulic motor is used for driving a winch. Two electromagnetic valves can control the series-parallel connection between the three proportional valves. By changing the series-parallel relation among the three proportional valves, the size and the sequence of the hydraulic oil supplied to the three hydraulic motors by the main pump set can be changed. For example, when the first proportional valve, the second proportional valve and the third proportional valve are sequentially connected in series, the hydraulic oil output by the main pump unit flows to the first hydraulic motor to drive the first winch, the redundant hydraulic oil flows to the second hydraulic motor to drive the second winch, and the redundant hydraulic oil flows to the third hydraulic motor to drive the third winch. Therefore, the invention can drive the plurality of winches according to the working priority of the winches by only providing one set of hydraulic system, thereby saving the manufacturing cost of the maritime work platform, and having simple structure and convenient operation.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings needed to be used in the description of the embodiments will be briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without creative efforts.
FIG. 1 is a hydraulic schematic diagram of a multiple-winch hydraulic system according to an embodiment of the present invention.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, embodiments of the present invention will be described in detail with reference to the accompanying drawings.
The invention provides a multi-winch hydraulic system, and fig. 1 is a hydraulic schematic diagram of the multi-winch hydraulic system provided by the embodiment of the invention, and as shown in fig. 1, the hydraulic system comprises a main pump group 10, three proportional valves, two electromagnetic valves and three hydraulic motors. The three proportional valves are three-position six-way valves, the three proportional valves are arranged in one-to-one correspondence with the three hydraulic motors, the three proportional valves comprise a first proportional valve 21, a second proportional valve 22 and a third proportional valve 23, the two electromagnetic valves comprise a first electromagnetic valve 31 and a second electromagnetic valve 32, and the three hydraulic motors comprise a first hydraulic motor 41, a second hydraulic motor 42 and a third hydraulic motor 43.
The port PP1 of the first proportional valve 21 communicates with the output port of the main pump group 10, the port PT1 of the first proportional valve 21 communicates with the port PP2 of the second proportional valve 22, the port PT2 of the second proportional valve 22 communicates with the port PP3 of the third proportional valve 23, and the port PT3 of the third proportional valve 23 communicates with the tank.
The ports A of the three proportional valves are communicated with the ports A of the corresponding hydraulic motors, the ports B of the three proportional valves are communicated with the ports B of the corresponding hydraulic motors, and the ports T of the three proportional valves are communicated with the oil tank.
Specifically, the a1 port of the first proportional valve 21 communicates with the a1 port of the first hydraulic motor 41, and the B1 port of the first proportional valve 21 communicates with the B1 port of the first hydraulic motor 41. The port a2 of the second proportional valve 22 communicates with the port a2 of the second hydraulic motor 42, and the port B2 of the second proportional valve 22 communicates with the port B2 of the second hydraulic motor 42. The port A3 of the third proportional valve 23 communicates with the port A3 of the third hydraulic motor 43, and the port B3 of the third proportional valve 23 communicates with the port B3 of the third hydraulic motor 43.
The port P1 of the first proportional valve 21 is communicated with the output end of the main pump group 10, one end of the first electromagnetic valve 31 is communicated with the output end of the main pump group 10, the other end of the first electromagnetic valve 31 is communicated with one end of the second electromagnetic valve 32, the other end of the second electromagnetic valve 32 is communicated with the port P3 of the third proportional valve 23, the other end of the first electromagnetic valve 31 is also communicated with the ports PP2 and P2 of the second proportional valve 22, and one end of the second electromagnetic valve 32 is also communicated with the port PP3 of the third proportional valve 23.
The embodiment of the invention is provided with a hydraulic system, which comprises a main pump set, three proportional valves, two electromagnetic valves and three hydraulic motors, wherein the three proportional valves are three-position six-way valves, and the three proportional valves and the three hydraulic motors are arranged in a one-to-one correspondence manner. The proportional valve can control the pressure and the flow of the hydraulic oil output by the main pump group and then output the hydraulic oil to a corresponding hydraulic motor, and the hydraulic motor is used for driving a winch. Two electromagnetic valves can control the series-parallel connection between the three proportional valves. By changing the series-parallel relation among the three proportional valves, the size and the sequence of the hydraulic oil supplied to the three hydraulic motors by the main pump set can be changed. For example, when the first proportional valve, the second proportional valve and the third proportional valve are sequentially connected in series, the hydraulic oil output by the main pump unit flows to the first hydraulic motor to drive the first winch, the redundant hydraulic oil flows to the second hydraulic motor to drive the second winch, and the redundant hydraulic oil flows to the third hydraulic motor to drive the third winch. Therefore, the invention can drive the plurality of winches according to the working priority of the winches by only providing one set of hydraulic system, thereby saving the manufacturing cost of the maritime work platform, and having simple structure and convenient operation.
In the present embodiment, all three hydraulic motors are bidirectional constant displacement motors.
Further, the main pump group 10 includes an electric motor 11 and an electro proportional valve (not shown in the drawings) for controlling the pressure and flow rate of hydraulic oil output from the electric motor 11. And the electro proportional valve can receive the control signal, and the pressure and the flow of the hydraulic oil output by the main pump group 10 can be remotely controlled by sending the control signal to the electro proportional valve.
Further, the main pump group 10 further includes a safety valve 12, an oil inlet of the safety valve 12 is communicated with an output end of the motor 11, an oil outlet of the safety valve 12 is communicated with an oil tank, and a control oil port of the safety valve 12 is communicated with an oil inlet of the safety valve 12. By arranging the safety valve 12, the pressure of the hydraulic oil output by the output end of the main pump unit 10 can be controlled not to exceed a preset value, and the effect of protecting the safe operation of equipment is achieved.
Alternatively, the threshold value of the safety valve 12 may be determined from the maximum working pressure of the three hydraulic motor driven drawworks and the pressure loss of the hydraulic system along the way.
Specifically, the sum of the maximum working pressure of the first winch 41, the second winch 42, and the third winch 43 and the pressure loss along the hydraulic system is the threshold value of the safety valve 12.
Further, the hydraulic system further comprises a first two-way pressure compensator 51 and a first shuttle valve 61, an oil inlet of the first two-way pressure compensator 51 is communicated with an output end of the main pump group 10, an oil outlet of the first two-way pressure compensator 51 is communicated with a port P1 of the first proportional valve 21, and a first control oil port of the first two-way pressure compensator 51 is communicated with an oil inlet of the first two-way pressure compensator 51.
The oil inlet of the first shuttle valve 61 is communicated with the port A1 of the first proportional valve 21, the oil outlet of the first shuttle valve 61 is communicated with the port B1 of the first proportional valve 21, and the control oil port of the first shuttle valve 61 is communicated with the second control oil port of the first two-way pressure compensator 51. The pressure at the output end and the input end of the first proportional valve can be kept constant by arranging the first two-way pressure compensator and the first shuttle valve.
Further, the hydraulic system further comprises a second two-way pressure compensator 52 and a second shuttle valve 62, an oil inlet of the second two-way pressure compensator 52 is communicated with the other end of the first electromagnetic valve 31, an oil outlet of the second two-way pressure compensator 52 is communicated with a port P2 of the second proportional valve 22, and a first control oil port of the second two-way pressure compensator 52 is communicated with an oil inlet of the second two-way pressure compensator 52.
The oil inlet of the second shuttle valve 62 is communicated with the port A2 of the second proportional valve 22, the oil outlet of the second shuttle valve 62 is communicated with the port B2 of the second proportional valve 22, and the control oil port of the second shuttle valve 62 is communicated with the second control oil port of the second two-way pressure compensator 52. The pressure at the output and input of the second proportional valve can be kept constant by providing a second two-way pressure compensator and a second shuttle valve.
Further, the hydraulic system further includes a third two-way pressure compensator 53 and a third shuttle valve 63, an oil inlet of the third two-way pressure compensator 53 is communicated with the other end of the second electromagnetic valve 32, an oil outlet of the third two-way pressure compensator 53 is communicated with a port P3 of the third proportional valve 23, and a first control oil port of the third two-way pressure compensator 53 is communicated with an oil inlet of the third two-way pressure compensator 53.
The oil inlet of the third shuttle valve 63 is communicated with the port A3 of the third proportional valve 23, the oil outlet of the third shuttle valve 63 is communicated with the port B3 of the third proportional valve, and the control oil port of the third shuttle valve 63 is communicated with the second control oil port of the third two-way pressure compensator 53. The pressure at the output and input of the third proportional valve can be kept constant by providing a third two-way pressure compensator and a third shuttle valve.
Further, each hydraulic system further includes a first relief valve 71, a second relief valve 72, and a third relief valve 73. An oil inlet of the first relief valve 71 is communicated with the port a1 of the first hydraulic motor 41, an oil outlet of the first relief valve 71 is communicated with the port B1 of the first hydraulic motor 41, a first control oil port of the first relief valve 71 is communicated with the oil inlet of the first relief valve 71, and a second control oil port of the first relief valve 71 is communicated with the oil outlet of the first relief valve 71. An oil inlet of the second overflow valve 72 is communicated with the port A2 of the second hydraulic motor 42, an oil outlet of the second overflow valve 72 is communicated with the port B2 of the second hydraulic motor 42, a first control oil port of the second overflow valve 72 is communicated with the oil inlet of the second overflow valve 72, and a second control oil port of the second overflow valve 72 is communicated with the oil outlet of the second overflow valve 72. An oil inlet of the third overflow valve 73 is communicated with the port A3 of the third hydraulic motor 43, an oil outlet of the third overflow valve 73 is communicated with the port B3 of the third hydraulic motor 43, a first control oil port of the third overflow valve 73 is communicated with the oil inlet of the third overflow valve 73, and a second control oil port of the third overflow valve 73 is communicated with the oil inlet of the third overflow valve 73. Through setting up the overflow valve, can prevent hydraulic motor overload overflow.
In the present embodiment, when the first electromagnetic valve 31 is energized, the first proportional valve 21 and the second proportional valve 22 are connected in parallel, and when the first electromagnetic valve 31 is de-energized, the first proportional valve 21 and the second proportional valve 22 are connected in series.
When the second electromagnetic valve 32 is powered, the second proportional valve 22 and the third proportional valve 23 are connected in parallel, and when the second electromagnetic valve 32 is powered off, the second proportional valve 22 and the third proportional valve 23 are connected in series.
Assuming that a first hydraulic motor is used for driving a first winch, a second hydraulic motor is used for driving a second winch, and a third hydraulic motor is used for driving a third winch, the working principle of a multi-winch hydraulic system provided by the embodiment of the invention is briefly described in the following with reference to fig. 1:
first, when the first winch has a higher priority than the second winch, the second winch has a higher priority than the third winch.
When the first electromagnetic valve 31 and the second electromagnetic valve 32 are controlled to lose power, the first proportional valve 21, the second proportional valve 22 and the third proportional valve 23 are sequentially connected in series, the hydraulic oil output by the main pump group 10 firstly flows to the first proportional valve 21 and is output to the first hydraulic motor 41 through the port A1 and the port B1 of the first proportional valve 21, and the first hydraulic motor 41 drives the first winch to work. The rest of the hydraulic oil flows to the second proportional valve 22 and is output to the second hydraulic motor 42 through the port a2 and the port B2 of the second proportional valve 22, and the second hydraulic motor 42 drives the second winch to work again. The remaining hydraulic oil flows to the third proportional valve 23 and is output to the third hydraulic motor 43 through the port a3 and the port B3 of the third proportional valve 23, and the third hydraulic motor 43 drives the third winch to work again.
And II, when the priority of the first winch is the same as that of the second winch and the priority of the first winch is higher than that of the third winch.
When the first electromagnetic valve 31 is controlled to be electrified and the second electromagnetic valve 32 is controlled to be deenergized, the first proportional valve 21 and the second proportional valve 22 are connected in parallel, and the third proportional valve 23 is connected in series with the first proportional valve 21 and the second proportional valve 22 which are connected in parallel. The hydraulic oil output by the main pump group 10 simultaneously flows to the first proportional valve 21 and the second proportional valve 22, and is output to the first hydraulic motor 41 through the port A1 and the port B1 of the first proportional valve 21, the first hydraulic motor 41 drives the first winch to work, and is output to the second hydraulic motor 42 through the port A2 and the port B2 of the second proportional valve 22, and the second hydraulic motor 42 drives the second winch to work. After the first winch and the second winch are driven to work, the rest hydraulic oil flows to the third proportional valve 23 again, and is output to the third hydraulic motor 43 through the port A3 and the port B3 of the third proportional valve 23, and the third hydraulic motor 43 drives the third winch to work again.
And thirdly, when the priority of the first winch is higher than that of the second winch, and the priority of the second winch is the same as that of the third winch.
When the first electromagnetic valve 31 is controlled to be de-energized and the second electromagnetic valve 32 is controlled to be energized, the second proportional valve 22 and the third proportional valve 23 are connected in parallel, and the first proportional valve 21 is connected in series with the second proportional valve 22 and the third proportional valve 23 which are connected in parallel. The hydraulic oil output by the main pump group 10 firstly flows to the first proportional valve 21 and is output to the first hydraulic motor 41 through the port a1 and the port B1 of the first proportional valve 21, and the first hydraulic motor 41 drives the first winch to work. The rest of the hydraulic oil flows to the second proportional valve 22 and the third proportional valve 23 simultaneously, is output to the second hydraulic motor 42 through the port A2 and the port B2 of the second proportional valve 22, the second hydraulic motor 42 drives the second winch to work, and is output to the third hydraulic motor 43 through the port A3 and the port B3 of the third proportional valve 23, and the third hydraulic motor 43 drives the third winch to work.
And fourthly, when the priorities of the first winch, the second winch and the third winch are the same.
When the first electromagnetic valve 31 and the second electromagnetic valve 32 are controlled to be electrified, the first proportional valve 21, the second proportional valve 22 and the third proportional valve 23 are connected in parallel, the hydraulic oil output by the main pump group 10 simultaneously flows to the first proportional valve 21, the second proportional valve 22 and the third proportional valve 23 and is output to the first hydraulic motor 41 through the port A1 and the port B1 of the first proportional valve 21, and the first hydraulic motor 41 drives the first winch to work. The output of the port A2 and the port B2 of the second proportional valve 22 is sent to the second hydraulic motor 42, and the second hydraulic motor 42 drives the second winch to work. The output of the port A3 and the port B3 of the third proportional valve 23 is transmitted to a third hydraulic motor 43, and the third hydraulic motor 43 drives a third winch to work.
The present invention is not limited to the above preferred embodiments, and any modifications, equivalent replacements, improvements, etc. within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (10)
1. A multi-winch hydraulic system comprises a main pump set, three proportional valves, two electromagnetic valves and three hydraulic motors, and is characterized in that the three proportional valves are three-position six-way valves, the three proportional valves and the three hydraulic motors are arranged in a one-to-one correspondence mode, the three proportional valves comprise a first proportional valve, a second proportional valve and a third proportional valve, and the two electromagnetic valves comprise a first electromagnetic valve and a second electromagnetic valve;
the PP1 port of the first proportional valve is communicated with the output end of the main pump group, the PT1 port of the first proportional valve is communicated with the PP2 port of the second proportional valve, the PT2 port of the second proportional valve is communicated with the PP3 port of the third proportional valve, and the PT3 port of the third proportional valve is communicated with a fuel tank;
the ports A of the three proportional valves are communicated with the ports A of the corresponding hydraulic motors, the ports B of the three proportional valves are communicated with the ports B of the corresponding hydraulic motors, and the ports T of the three proportional valves are communicated with the oil tank;
the port P1 of the first proportional valve is communicated with the output end of the main pump group, one end of the first electromagnetic valve is communicated with the output end of the main pump group, the other end of the first electromagnetic valve is communicated with one end of the second electromagnetic valve, the other end of the second electromagnetic valve is communicated with the port P3 of the third proportional valve, the other end of the first electromagnetic valve is also communicated with the ports PP2 and P2 of the second proportional valve respectively, and one end of the second electromagnetic valve is also communicated with the port PP3 of the third proportional valve.
2. The hydraulic system of claim 1, wherein the main pump group includes a motor and an electro proportional valve for controlling pressure and flow of hydraulic oil output by the motor.
3. The hydraulic system of claim 2, wherein the main pump group further comprises a safety valve, an oil inlet of the safety valve is communicated with the output end of the motor, an oil outlet of the safety valve is communicated with the oil tank, and a control oil port of the safety valve is communicated with the oil inlet of the safety valve.
4. A hydraulic system according to claim 3, characterized in that the threshold value of the safety valve is determined on the basis of the maximum working pressure of the three hydraulic-motor-driven winches and the pressure loss over the course of the hydraulic system.
5. The hydraulic system according to claim 1, further comprising a first two-way pressure compensator and a first shuttle valve, wherein an oil inlet of the first two-way pressure compensator is communicated with an output end of the main pump group, an oil outlet of the first two-way pressure compensator is communicated with a port P of the first proportional valve, and a first control oil port of the first two-way pressure compensator is communicated with an oil inlet of the first two-way pressure compensator;
an oil inlet of the first shuttle valve is communicated with the port A of the first proportional valve, an oil outlet of the first shuttle valve is communicated with the port B of the first proportional valve, and a control oil port of the first shuttle valve is communicated with a second control oil port of the first two-way pressure compensator.
6. The hydraulic system of claim 1, further comprising a second two-way pressure compensator and a second shuttle valve, wherein an oil inlet of the second two-way pressure compensator is communicated with the other end of the first electromagnetic valve, an oil outlet of the second two-way pressure compensator is communicated with a port P of the second proportional valve, and a first control oil port of the second two-way pressure compensator is communicated with an oil inlet of the second two-way pressure compensator;
an oil inlet of the second shuttle valve is communicated with the port A of the second proportional valve, an oil outlet of the second shuttle valve is communicated with the port B of the second proportional valve, and a control oil port of the second shuttle valve is communicated with a second control oil port of the second two-way pressure compensator.
7. The hydraulic system of claim 1, further comprising a third two-way pressure compensator and a third shuttle valve, wherein an oil inlet of the third two-way pressure compensator is communicated with the other end of the second electromagnetic valve, an oil outlet of the third two-way pressure compensator is communicated with a port P of the third proportional valve, and a first control oil port of the third two-way pressure compensator is communicated with an oil inlet of the third two-way pressure compensator;
an oil inlet of the third shuttle valve is communicated with the port A of the third proportional valve, an oil outlet of the third shuttle valve is communicated with the port B of the third proportional valve, and a control oil port of the third shuttle valve is communicated with a second control oil port of the third two-way pressure compensator.
8. The hydraulic system according to claim 1, wherein each hydraulic system further comprises three overflow valves respectively connected in parallel with the three hydraulic motors, an oil inlet of each overflow valve is communicated with the port a of the hydraulic motor, an oil outlet of each overflow valve is communicated with the port B of the hydraulic motor, a first control oil port of each overflow valve is communicated with an oil inlet of each overflow valve, and a second control oil port of each overflow valve is communicated with an oil outlet of each overflow valve.
9. The hydraulic system of claim 1, wherein the first proportional valve and the second proportional valve are connected in parallel when the first solenoid valve is energized and in series when the first solenoid valve is de-energized;
when the second electromagnetic valve is electrified, the second proportional valve and the third proportional valve are connected in parallel, and when the second electromagnetic valve is not electrified, the second proportional valve and the third proportional valve are connected in series.
10. The hydraulic system of claim 1, wherein all three of the hydraulic motors are bi-directional fixed displacement motors.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811015785.4A CN109114053B (en) | 2018-08-31 | 2018-08-31 | Multi-winch hydraulic system |
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| CN110131226B (en) * | 2019-06-11 | 2024-03-01 | 徐州海伦哲特种车辆有限公司 | Walking control valve of crawler-type hydraulic walking system and walking system |
| CN114380227B (en) * | 2022-01-18 | 2024-01-26 | 中国水产科学研究院渔业机械仪器研究所 | Wave compensation system of hydraulic trawl winch |
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