CN111664135A - Hydraulic system of gear rack lifting platform - Google Patents
Hydraulic system of gear rack lifting platform Download PDFInfo
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- CN111664135A CN111664135A CN202010326462.8A CN202010326462A CN111664135A CN 111664135 A CN111664135 A CN 111664135A CN 202010326462 A CN202010326462 A CN 202010326462A CN 111664135 A CN111664135 A CN 111664135A
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- 238000004891 communication Methods 0.000 claims description 8
- 238000000034 method Methods 0.000 abstract description 9
- 230000008569 process Effects 0.000 abstract description 8
- 239000012530 fluid Substances 0.000 description 20
- 230000001276 controlling effect Effects 0.000 description 13
- 230000009471 action Effects 0.000 description 5
- 230000005540 biological transmission Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 239000007788 liquid Substances 0.000 description 4
- 230000001105 regulatory effect Effects 0.000 description 3
- 230000009194 climbing Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
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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
- F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02B—HYDRAULIC ENGINEERING
- E02B17/00—Artificial islands mounted on piles or like supports, e.g. platforms on raisable legs or offshore constructions; Construction methods therefor
- E02B17/04—Equipment specially adapted for raising, lowering, or immobilising the working platform relative to the supporting construction
- E02B17/08—Equipment specially adapted for raising, lowering, or immobilising the working platform relative to the supporting construction for raising or lowering
- E02B17/0809—Equipment specially adapted for raising, lowering, or immobilising the working platform relative to the supporting construction for raising or lowering the equipment being hydraulically actuated
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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
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
- F15B1/021—Installations or systems with accumulators used for damping
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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
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
- F15B1/024—Installations or systems with accumulators used as a supplementary power source, e.g. to store energy in idle periods to balance pump load
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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
- F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
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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
- F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
- F15B20/007—Overload
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/08—Servomotor systems incorporating electrically operated control means
- F15B21/087—Control strategy, e.g. with block diagram
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The present disclosure provides a hydraulic system of a rack and pinion lift platform, comprising: the system comprises a driving pump module, an oil tank, a first pipeline, a second pipeline and a plurality of motor modules; the driving pump module comprises a first driving pump, a two-position four-way valve, a first balance valve and a second balance valve, wherein an oil outlet of the first driving pump is communicated with a first oil port of the two-position four-way valve, a second oil port of the two-position four-way valve is communicated with an oil inlet of the first balance valve, an oil outlet of the first balance valve is connected to a first pipeline, a hydraulic control port of the first balance valve is communicated with a third oil port of the two-position four-way valve, an oil inlet of the second balance valve is communicated with a third oil port of the two-position four-way valve, an oil outlet of the second balance valve is connected to a second pipeline, and a hydraulic control port of the second balance valve is communicated with; the first oil port of each motor module is connected to the first pipeline, and the second oil port of each motor module is connected to the second pipeline. The hydraulic system can reduce the impact on the hydraulic system in the starting process.
Description
Technical Field
The disclosure relates to the technical field of hydraulic control, in particular to a hydraulic system of a gear rack lifting platform.
Background
The ocean lifting platform is generally suitable for operation in shallow sea areas, and is widely applied to offshore marine oil development due to the advantages of low manufacturing cost, small steel consumption, no influence of environmental conditions, high efficiency and the like. The lifting platform usually adopts a cylindrical spud leg gear rack type lifting device to realize the lifting action.
The related art lifting apparatus includes a plurality of lifting units, each of which is driven by a hydraulic motor module. And each hydraulic motor module comprises a hydraulic motor and a balance valve group, and the hydraulic motor is used for controlling the lifting gear to rotate so as to drive the lifting gear to climb or descend along the pile leg rack, so that the lifting action of the ocean lifting platform is realized. The balance valve group is arranged at an oil inlet and an oil outlet of the hydraulic motor and used for balancing the load weight when the platform and the pile leg descend.
However, because there is manufacturing error in the spud leg rack, in the process of the lifting of the ocean lifting platform, the load on each lifting unit is different, so that the opening sequence of the balance valve group of each lifting unit is inconsistent, the oil pressure at the oil port of each hydraulic motor is different when the hydraulic system is started, and thus, the hydraulic system for controlling the lifting device is impacted greatly in the starting process.
Disclosure of Invention
The embodiment of the disclosure provides a hydraulic system of a gear rack lifting platform, which can enable the oil pressure at the oil port of each motor module to be always consistent and reduce the impact on the hydraulic system in the starting process. The technical scheme is as follows:
the embodiment of the present disclosure provides a hydraulic system of a rack and pinion lift platform, the hydraulic system includes: the system comprises a driving pump module, an oil tank, a first pipeline, a second pipeline and a plurality of motor modules; the driving pump module comprises a first driving pump, a two-position four-way valve, a first balance valve and a second balance valve, wherein an oil inlet of the first driving pump is communicated with the oil tank, an oil outlet of the first driving pump is communicated with a first oil port of the two-position four-way valve, a second oil port of the two-position four-way valve is communicated with an oil inlet of the first balance valve, an oil outlet of the first balance valve is connected to the first pipeline, a hydraulic control port of the first balance valve is communicated with a third oil port of the two-position four-way valve, an oil inlet of the second balance valve is communicated with a third oil port of the two-position four-way valve, an oil outlet of the second balance valve is connected to the second pipeline, a hydraulic control port of the second balance valve is communicated with the second oil port of the two-position four-way valve, and a fourth oil port of the two-position four; the motor module is provided with a first oil port and a second oil port, the first oil port of each motor module is connected to the first pipeline, and the second oil port of each motor module is connected to the second pipeline.
In an implementation manner of the embodiment of the present disclosure, the hydraulic system further includes a third pipeline, the motor module further includes a hydraulic brake for braking the hydraulic motor, the driving pump module further includes a second driving pump, an oil inlet of the second driving pump is communicated with the oil tank, an oil outlet of the second driving pump is connected to the third pipeline, and an oil inlet of the hydraulic brake of each motor module is connected to the third pipeline.
In an implementation manner of the embodiment of the present disclosure, the motor module further includes a variable displacement motor, a shuttle valve, a hydraulic control directional control valve, and a motor variable displacement cylinder for controlling a displacement of the variable displacement motor, an oil inlet of the variable displacement motor is communicated with the first pipeline, an oil outlet of the variable displacement motor is communicated with the second pipeline, a first oil inlet of the shuttle valve is communicated with an oil outlet of the variable displacement motor, a second oil inlet of the shuttle valve is communicated with an oil inlet of the variable displacement motor, the hydraulic control directional control valve has a first oil port, a second oil port, a third oil port, and a fourth oil port, the first oil port of the hydraulic control directional control valve is communicated with the oil outlet of the shuttle valve, the second oil port of the hydraulic control directional control valve is communicated with a rodless cavity of the motor variable displacement cylinder, the third oil port of the hydraulic control directional control valve is communicated with a rod cavity of the motor variable displacement cylinder, and the fourth oil port of the hydraulic control directional control valve is communicated with an, the hydraulic control reversing valve is provided with a first state and a second state, when the hydraulic control reversing valve is in the first state, a first oil port of the hydraulic control reversing valve is communicated with a second oil port of the hydraulic control reversing valve, a third oil port of the hydraulic control reversing valve is communicated with a fourth oil port of the hydraulic control reversing valve, when the hydraulic control reversing valve is in the second state, the first oil port of the hydraulic control reversing valve is communicated with the third oil port of the hydraulic control reversing valve, and the second oil port of the hydraulic control reversing valve is communicated with the fourth oil port of the hydraulic control reversing valve.
In an implementation manner of the embodiment of the present disclosure, the hydraulic system further includes a fourth pipeline, the hydraulic control directional control valves further include hydraulic control ports, the hydraulic control port of each hydraulic control directional control valve is connected to the fourth pipeline, the oil outlet of the second drive pump is connected to the fourth pipeline, when the oil pressure at the hydraulic control port of the hydraulic control directional control valve exceeds a set value, the hydraulic control directional control valve is in the first state, and when the oil pressure at the hydraulic control port of the hydraulic control directional control valve is less than the set value, the hydraulic control directional control valve is in the second state.
In an implementation manner of the embodiment of the present disclosure, the hydraulic system further includes a first switch valve and a second switch valve for controlling on/off of an oil path, the first switch valve is located on the oil path between the oil outlet of the second drive pump and the third pipeline, and the second switch valve is located on the oil path between the second drive pump and the fourth pipeline.
In an implementation manner of the embodiment of the present disclosure, the hydraulic system further includes an accumulator, an oil outlet of the accumulator is connected to an oil path between the oil outlet of the second drive pump and the third pipeline, and an oil outlet of the accumulator is connected to an oil path between the oil outlet of the second drive pump and the fourth pipeline.
In an implementation manner of the embodiment of the present disclosure, the hydraulic system further includes a first overflow valve and a second overflow valve, an oil inlet of the first overflow valve is communicated with an oil outlet of the first drive pump, an oil outlet of the first overflow valve is communicated with the oil tank, an oil inlet of the second overflow valve is communicated with an oil outlet of the second drive pump, and an oil outlet of the second overflow valve is communicated with the oil tank.
In an implementation manner of the embodiment of the present disclosure, the driving pump module further includes a first check valve, a second check valve, a third check valve, a fourth check valve, and a safety valve, an oil inlet of the first check valve is connected to the oil path between the oil outlet of the first balance valve and the first pipeline, an oil outlet of the first check valve is communicated with the oil outlet of the second check valve, an oil inlet of the second check valve is connected to the oil path between the oil outlet of the second balance valve and the second pipeline, an oil outlet of the third check valve is connected to the oil path between the oil outlet of the first balance valve and the first pipeline, an oil inlet of the third check valve is communicated with the oil inlet of the fourth check valve, an oil outlet of the fourth check valve is connected to the oil path between the oil outlet of the second balance valve and the second pipeline, the oil inlet of the safety valve is connected to an oil path between the oil outlet of the first one-way valve and the oil outlet of the second one-way valve, and the oil outlet of the safety valve is connected to an oil path between the oil inlet of the third one-way valve and the oil inlet of the fourth one-way valve.
In an implementation manner of the embodiment of the present disclosure, the drive pump module further includes a fifth one-way valve, an oil inlet of the fifth one-way valve is communicated with an oil outlet of the safety valve, and an oil outlet of the fifth one-way valve is communicated with the oil tank.
In an implementation manner of the embodiment of the present disclosure, the drive pump module further includes a first one-way throttle valve and a second one-way throttle valve, an oil inlet of the first one-way throttle valve is communicated with a third oil port of the two-position four-way valve, an oil outlet of the first one-way throttle valve is communicated with a hydraulic control port of the first balance valve, an oil inlet of the second one-way throttle valve is communicated with a second oil port of the two-position four-way valve, and an oil outlet of the second one-way throttle valve is communicated with a hydraulic control port of the second balance valve.
The beneficial effects brought by the technical scheme provided by the embodiment of the disclosure at least comprise:
the hydraulic system of the embodiment of the disclosure comprises a driving pump module, an oil tank, a first pipeline, a second pipeline and a plurality of motor modules, wherein the driving pump module comprises a first driving pump, a two-position four-way valve, a first balance valve and a second balance valve, an oil inlet of the first driving pump is communicated with the oil tank, an oil outlet of the first driving pump is communicated with a first oil port of the two-position four-way valve, and therefore oil can be pumped to the two-position four-way valve by means of the first driving pump after being sucked into the first driving pump. And a second oil port of the two-position four-way valve is communicated with an oil inlet of the first balance valve, an oil outlet of the first balance valve is connected to the first pipeline, and a hydraulic control port of the first balance valve is communicated with a third oil port of the two-position four-way valve, namely after the oil pumped to the two-position four-way valve is distributed by the two-position four-way valve, if the oil flows out from the second oil port of the two-position four-way valve, the oil can be conveyed to the first balance valve and conveyed to the first pipeline through the first balance valve. Meanwhile, an oil inlet of the second balance valve is communicated with a third oil port of the two-position four-way valve, an oil outlet of the second balance valve is connected to a second pipeline, and a hydraulic control port of the second balance valve is communicated with a second oil port of the two-position four-way valve, namely after the oil pumped to the two-position four-way valve is distributed by the two-position four-way valve, if the oil flows out of the third oil port of the two-position four-way valve, the oil can be conveyed to the second balance valve and conveyed to the second pipeline through the second balance valve.
Because the motor module has first hydraulic fluid port and second hydraulic fluid port, the first hydraulic fluid port of every motor module all connects on first pipeline, and the second hydraulic fluid port of every motor module all connects on the second pipeline. Therefore, after the oil is distributed through the two-position four-way valve, the oil is conveyed to the first pipeline or the second pipeline, and finally passes through the motor module, so that the difference is that the motor module is positively rotated or reversely rotated in two different oil distribution modes, and the climbing or descending action of the lifting platform is realized.
And the hydraulic control port of the first balance valve is communicated with the third oil port of the two-position four-way valve, and the hydraulic control port of the second balance valve is communicated with the second oil port of the two-position four-way valve. For example, after the oil is distributed by the two-position four-way valve, when the second oil port of the two-position four-way valve outputs high-pressure oil, the oil can be conveyed to the first oil port of the motor module through the first balance valve, and because the second balance valve only allows the oil to flow from the oil inlet to the oil outlet under normal conditions, the motor module cannot act, meanwhile, because the hydraulic control port of the second balance valve is communicated with the second oil port of the two-position four-way valve, the high-pressure oil of the second oil port of the two-position four-way valve enables the oil inlet and the oil outlet of the second balance valve to be communicated, so that the oil is allowed to flow in from the first oil port of the motor module, flow out from the second oil port of the motor module and flow back to the two-position four-way valve, so as to control the normal work of the motor module, and the locking.
And the first hydraulic fluid port of every motor module all connects on first pipeline in this embodiment, and the second hydraulic fluid port of every motor module all connects on the second pipeline, also promptly, the first hydraulic fluid port of every motor module all communicates through first pipeline and same set of balanced valves (first balanced valve and second balanced valve), and the second hydraulic fluid port of every motor module all communicates through second pipeline and same set of balanced valves (first balanced valve and second balanced valve), promptly all motor modules share a set of balanced valves in this embodiment. When the balance valve bank is started, the balance valve banks of all the motor modules are started at the same time, so that the condition that the opening sequence of the balance valve banks of all the motor modules in the related technology is different is avoided. And the first hydraulic fluid port of every motor module all connects in parallel on first pipeline, and the second hydraulic fluid port of every motor module all connects in parallel on the second pipeline, because the fluid of this set of balanced valves output can be carried to first pipeline and second pipeline, equally divide fluid to the motor module department of each difference through first pipeline and second pipeline like this, the oil pressure of the oil port department of having guaranteed each motor module is the same all the time to reduce the impact that hydraulic system received among the start-up process.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present disclosure, the drawings needed to be used in the description of the embodiments are briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present disclosure, and it is obvious for those skilled in the art to obtain other drawings based on the drawings without creative efforts.
Fig. 1 is a hydraulic schematic diagram of a hydraulic system of a rack and pinion lifting platform provided in an embodiment of the present disclosure;
fig. 2 is a hydraulic schematic diagram of a motor module provided in an embodiment of the present disclosure.
Detailed Description
To make the objects, technical solutions and advantages of the present disclosure more apparent, embodiments of the present disclosure will be described in detail with reference to the accompanying drawings.
Fig. 1 is a hydraulic schematic diagram of a hydraulic system of a rack and pinion lifting platform provided in an embodiment of the present disclosure. As shown in fig. 1, the hydraulic system includes: a drive pump module, a tank 20, a first line 21, a second line 22 and a plurality of motor modules 3.
As shown in fig. 1, the driving pump module includes a first driving pump 11, a two-position four-way valve 12, a hydraulic control port 131 of a first balance valve 13, and a second balance valve 14, an oil inlet of the first driving pump 11 is communicated with an oil tank 20, an oil outlet of the first driving pump 11 is communicated with a first oil port of the two-position four-way valve 12, a second oil port of the two-position four-way valve 12 is communicated with an oil inlet of the first balance valve 13, an oil outlet of the first balance valve 13 is connected to a first pipeline 21, the hydraulic control port 131 of the first balance valve 13 is communicated with a third oil port of the two-position four-way valve 12, an oil inlet of the second balance valve 14 is communicated with a third oil port of the two-position four-way valve 12, an oil outlet of the second balance valve 14 is connected to a second pipeline 22, the hydraulic control port 141 of the second balance valve 14 is communicated with the second oil port of the two.
As shown in fig. 1, the motor modules 3 have a first oil port and a second oil port, the first oil port 31 of each motor module 3 is connected to the first pipeline 21, and the second oil port 32 of each motor module 3 is connected to the second pipeline 22.
The hydraulic system of the embodiment of the present disclosure includes a driving pump module, an oil tank 20, a first pipeline 21, a second pipeline 22 and a plurality of motor modules 3, wherein the driving pump module includes a first driving pump 11, a two-position four-way valve 12, a hydraulic control port 131 of a first balance valve 13 and a second balance valve 14, an oil inlet of the first driving pump 11 is communicated with the oil tank 20, and an oil outlet of the first driving pump 11 is communicated with a first oil port of the two-position four-way valve 12, so that oil is pumped to the two-position four-way valve 12 by the first driving pump 11 after being sucked into the first driving pump 11. And, the second oil port of the two-position four-way valve 12 is communicated with the oil inlet of the first balance valve 13, the oil outlet of the first balance valve 13 is connected to the first pipeline 21, the hydraulic control port 131 of the first balance valve 13 is communicated with the third oil port of the two-position four-way valve 12, that is, after the oil pumped to the two-position four-way valve 12 is distributed by the two-position four-way valve 12, if the oil flows out from the second oil port of the two-position four-way valve 12, the oil can be conveyed to the hydraulic control port 131 of the first balance valve 13 and conveyed to the first pipeline 21 through the hydraulic control port 131 of the first balance valve 13. Meanwhile, an oil inlet of the second balance valve 14 is communicated with a third oil port of the two-position four-way valve 12, an oil outlet of the second balance valve 14 is connected to the second pipeline 22, and a hydraulic control port 141 of the second balance valve 14 is communicated with a second oil port of the two-position four-way valve 12, that is, after the oil pumped to the two-position four-way valve 12 is distributed by the two-position four-way valve 12, if the oil flows out from the third oil port of the two-position four-way valve 12, the oil can be conveyed to the second balance valve 14 and conveyed to the second pipeline 22 through the second balance valve 14.
Since the motor modules 3 have the first oil port and the second oil port, the first oil port 31 of each motor module 3 is connected to the first pipeline 21, and the second oil port 32 of each motor module 3 is connected to the second pipeline 22. It can be known that, after the oil is distributed by the two-position four-way valve 12, no matter the oil is delivered to the first pipeline 21 or the second pipeline 22, the oil finally passes through the motor module 3, and the difference lies in that the two different oil distribution modes realize the forward rotation or the reverse rotation of the motor module 3, so as to realize the climbing or descending action of the lifting platform.
Further, since the pilot port 131 of the first balance valve 13 communicates with the third port of the two-position four-way valve 12, the pilot port 141 of the second balance valve 14 communicates with the second port of the two-position four-way valve 12. For example, when the oil is distributed by the two-position four-way valve 12, and the second port of the two-position four-way valve 12 outputs high-pressure oil, the oil is delivered to the first oil port 31 of the motor module 3 through the hydraulic control port 131 of the first balance valve 13, since the second balancing valve 14 normally allows oil to flow only from the oil inlet to the oil outlet, the motor module 3 cannot be actuated, and at the same time, since the hydraulic control port 141 of the second balance valve 14 is communicated with the second port of the two-position four-way valve 12, the high-pressure oil at the second port of the two-position four-way valve 12 facilitates the oil inlet and the oil outlet of the second balance valve 14 to be communicated, thereby allowing the oil to flow in from the first oil port 31 of the motor module 3, flow out from the second oil port 32 of the motor module 3 and flow back to the two-position four-way valve 12, so as to control the normal operation of the motor module 3, and the locking of the motor module 3 by means of the two balancing valves can take the load of the platform when the hydraulic system is not activated.
And the first oil port 31 of each motor module 3 in this embodiment is connected to the first pipeline 21, and the second oil port 32 of each motor module 3 is connected to the second pipeline 22, that is, the first oil port 31 of each motor module 3 is communicated with the hydraulic control port 131 of the first balance valve 13 of the same set of balance valve group and the second balance valve 14 through the first pipeline 21, and the second oil port 32 of each motor module 3 is communicated with the hydraulic control port 131 of the first balance valve 13 of the same set of balance valve group and the second balance valve 14 through the second pipeline 22, that is, all the motor modules 3 in this embodiment share one set of balance valve group. When this balanced valves starts like this, be equivalent to all motor module 3's balanced valves all start simultaneously to the condition that the opening sequence of the balanced valves of each motor module 3 differs among the correlation technique can not appear. And the first hydraulic fluid port 31 of every motor module 3 all connects in parallel on first pipeline 21, the second hydraulic fluid port 32 of every motor module 3 all connects in parallel on second pipeline 22, because the fluid of output through this set of balanced valves can be carried to first pipeline 21 and second pipeline 22, can equally divide fluid to the motor module 3 department of each difference through first pipeline 21 and second pipeline 22 like this, the oil pressure of the hydraulic fluid port department of each motor module 3 has also been guaranteed to be the same all the time, thereby reduce the impact that hydraulic system received in the start-up process.
In the embodiment of the present disclosure, as shown in fig. 1, the first driving pump 11 may be driven by a driving motor, wherein an output shaft of the driving motor is coaxially connected to a transmission shaft of the first driving pump 11, so as to output power of the driving motor to the first driving pump 11, and the transmission shaft of the first driving pump 11 drives an impeller of the first driving pump 11 to rotate, so as to convey oil at an oil inlet of the first driving pump 11 to an oil outlet of the first driving pump 11.
Wherein the two-position, four-way valve 12 may be a solenoid directional valve having an electromagnet that is in a first position when energized and in a second position when de-energized. When the electromagnetic directional valve is at different positions, different oil ports are communicated or separated.
Illustratively, referring to fig. 1, the two-position four-way valve 12 has a first oil port, a second oil port, a third oil port and a fourth oil port, the two-position four-way valve 12 has two positions, when the two-position four-way valve 12 is in the first position, such as the right position shown in the two-position four-way valve 12 in fig. 1, the first oil port of the two-position four-way valve 12 is communicated with the second oil port of the two-position four-way valve 12, and the allowed oil flow direction is: flows from the first port of the two-position four-way valve 12 to the second port of the two-position four-way valve 12; when the two-position four-way valve 12 is in the second position, such as the left position shown in the two-position four-way valve 12 in fig. 1, the fourth oil port of the two-position four-way valve 12 is communicated with the third oil port of the two-position four-way valve 12, and the allowed oil flowing direction is: from the third port of the two-position, four-way valve 12 to the fourth port of the two-position, four-way valve 12.
As shown in fig. 1, in this embodiment, in combination with the hydraulic system, when a +10V voltage signal is applied to two ends of the two-position four-way valve 12, the two-position four-way valve 12 is located at the first position, the oil outputted by the first driving pump 11 passes through the two-position four-way valve 12 and then flows to the second port of the two-position four-way valve 12 through the first port of the two-position four-way valve 12, and then flows to the first ports 31 of the different motor modules 3 through the first pipeline 21 after passing through the hydraulic control port 131 of the first balancing valve 13, and flows out from the second ports 32 of the different motor modules 3 after passing through the different motor modules 3, and at the same time, the high-pressure oil at the second port of the two-position four-way valve 12 flows to the hydraulic control port 141 of the second balancing valve 14, so as to make the liquid inlet of the second balancing valve 14 and the liquid inlet of the second balancing valve 14 conductive, and then make the oil flowing out from the second, and then returns to the third port of the two-position four-way valve 12 through the second balance valve 14, and returns to the oil tank 20 from the fourth port of the two-position four-way valve 12, thereby realizing the control of the forward rotation of the motor module 3.
As shown in fig. 1, in this embodiment, in combination with the hydraulic system, when a voltage signal of-10V is applied to two ends of the two-position four-way valve 12, the two-position four-way valve 12 is located at the second position, the oil outputted by the first driving pump 11 passes through the two-position four-way valve 12 and then flows to the third port of the two-position four-way valve 12 through the first port of the two-position four-way valve 12, and then flows to the second ports 32 of the different motor modules 3 through the second pipeline 22 after passing through the second balancing valve 14, and flows out from the first ports 31 of the different motor modules 3 after passing through the different motor modules 3, meanwhile, the high-pressure oil at the third port of the two-position four-way valve 12 flows to the hydraulic control port 131 of the first balancing valve 13, so as to make the liquid outlet of the first balancing valve 13 and the liquid inlet of the first balancing valve 13 conductive, and then make the oil flowing out from the first ports 31 of the different, and returns to the second port of the two-position four-way valve 12 through the hydraulic control port 131 of the first balance valve 13, and returns to the oil tank 20 from the fourth port of the two-position four-way valve 12, thereby realizing reverse rotation of the control motor module 3.
As shown in fig. 1, the drive pump module may further include a first one-way throttle valve 16 and a second one-way throttle valve 17, an oil inlet of the first one-way throttle valve 16 is communicated with a third oil port of the two-position four-way valve 12, an oil outlet of the first one-way throttle valve 16 is communicated with a hydraulic control port 131 of the first balanced valve 13, an oil inlet of the second one-way throttle valve 17 is communicated with a second oil port of the two-position four-way valve 12, and an oil outlet of the second one-way throttle valve 17 is communicated with a hydraulic control port 141 of the second balanced valve. By providing the first check throttle valve 16 between the third port of the two-position four-way valve 12 and the pilot port 131 of the first balance valve 13, the flow rate and the oil hydraulic pressure delivered from the two-position four-way valve 12 to the pilot port 131 of the first balance valve 13 can be adjusted, preventing a large impact from being caused to the pilot port 131 of the first balance valve 13. By providing the second check throttle valve 17 between the second port of the two-position four-way valve 12 and the pilot port 141 of the second balance valve 14, the flow rate and the oil hydraulic pressure delivered from the two-position four-way valve 12 to the pilot port 141 of the second balance valve 14 can be adjusted, preventing a large impact from being caused to the pilot port 131 of the first balance valve 13.
In the embodiment of the present disclosure, the hydraulic system may further include a third pipeline 23, the motor module 3 further includes a hydraulic brake 33 for braking the hydraulic motor, the driving pump module further includes a second driving pump 15, an oil inlet of the second driving pump 15 is communicated with the oil tank 20, an oil outlet of the second driving pump 15 is connected to the third pipeline 23, and an oil inlet of the hydraulic brake 33 of each motor module 3 is connected to the third pipeline 23.
Since the oil outlet of the second drive pump 15 is connected to the third pipeline 23, and the oil inlet of the hydraulic brake 33 of each motor module 3 is connected to the third pipeline 23, that is, the oil inlet of the hydraulic brake 33 of each motor module 3 is communicated with the second drive pump 15 through the first pipeline 21, that is, the oil inlets of the hydraulic brakes 33 of all the motor modules 3 are connected in parallel to the third pipeline 23 in this embodiment. When this second drive pump 15 starts like this, can equally divide into the hydraulic brake 33 of each different motor module 3 with fluid through third pipeline 23, also guaranteed that the oil pressure of the hydraulic brake 33's of each motor module 3 oil inlet is the same all the time, also make the hydraulic brake 33 homoenergetic of each motor module 3 start simultaneously, reduce the impact that hydraulic system received in the start-up process. And the hydraulic brake 33 of each motor module 3 is independently pumped by the second driving pump 15, is not influenced by the pressure of the oil circuit of the driving lifting unit, and enhances the reliability of the hydraulic system.
Wherein, the motor module 3 may include a hydraulic motor and a hydraulic brake 33, the hydraulic brake 33 is used for braking the rotating shaft of the hydraulic motor, the oil inlet of the hydraulic motor may be the first oil port 31 of the motor module 3, the oil outlet of the hydraulic motor may be the second oil port 32 of the motor module 3, namely, the oil sent to the first oil port 31 and the second oil port of the motor module 3 by the first driving pump 11 may enter the oil inlet and the oil outlet of the hydraulic motor to drive the hydraulic motor to rotate, thereby driving the lifting device to control the motion of the lifting platform.
As shown in fig. 1, a transmission shaft of the second drive pump 15 may be coaxially connected with a transmission shaft of the first drive pump 11, so that power on an output shaft of the drive motor may also be transmitted to the second drive pump 15, and drive an impeller of the second drive pump 15 to rotate, thereby conveying oil at an oil inlet of the second drive pump 15 to an oil outlet of the second drive pump 15.
In the embodiment of the present disclosure, the oil outlet of the second driving pump 15 may also be communicated with the pilot port 12e of the two-position four-way valve 12, and under the condition that the two-position four-way valve 12 is powered on or powered off, the oil output by the second driving pump 15 is conveyed to the pilot port 12e of the two-position four-way valve 12, and may also be used to cooperate with the two-position four-way valve 12 to switch two positions of the two-position four-way valve 12.
Fig. 2 is a hydraulic schematic diagram of a motor module provided in an embodiment of the present disclosure. As shown in fig. 2, the motor module 3 further includes a variable displacement motor 34, a shuttle valve 35, a pilot operated directional valve 36, and a motor variable displacement cylinder 37 for controlling the displacement of the variable displacement motor 34. That is, in the present embodiment, the hydraulic motor of the motor module 3 is the variable displacement motor 34, and therefore the hydraulic brake 33 in the motor module 3 is used to brake the variable displacement motor 34. The variable displacement motor 34 is a variable displacement hydraulic motor, and the displacement of the variable displacement motor is adjusted by a motor variable cylinder 37 matched with the variable displacement motor 34, namely, the motor variable cylinder 37 can adjust the displacement of the variable displacement motor 34.
As shown in fig. 1, the oil inlet of the variable displacement motor 34 is communicated with the first pipeline 21, the oil outlet of the variable displacement motor 34 is communicated with the second pipeline 22, the first oil inlet 35a of the shuttle valve 35 is communicated with the oil outlet of the variable displacement motor 34, and the second oil inlet 35b of the shuttle valve 35 is communicated with the oil inlet of the variable displacement motor 34. Namely, the oil inlet of the variable displacement motor 34 is the first oil port 31 of the motor module 3, the oil outlet of the variable displacement motor 34 is the second oil port 32 of the motor module 3, and the oil pumped by the first driving pump 11 is conveyed to the variable displacement motor 34 through the two-position four-way valve 12 to control the variable displacement motor 34 to rotate, so that the lifting gear of the driving gear climbs or descends along the leg rack, and the lifting action of the ocean lifting platform is realized.
When high-pressure oil is introduced into the first oil inlet 35a of the shuttle valve 35 and the oil at the second oil inlet is low-pressure oil, the first oil inlet 35a of the shuttle valve 35 is communicated with the oil outlet 35c of the shuttle valve 35, and the first oil inlet 35b of the shuttle valve 35 is closed, that is, the shuttle valve 35 only allows the oil to flow from the first oil inlet 35a of the shuttle valve 35 to the oil outlet 35c of the shuttle valve 35. When high-pressure oil is introduced into the first oil inlet 35b of the shuttle valve 35 and the oil at the first oil inlet is low-pressure oil, the first oil inlet 35b of the shuttle valve 35 is communicated with the oil outlet 35c of the shuttle valve 35, and the first oil inlet 35a of the shuttle valve 35 is closed, that is, the shuttle valve 35 only allows the oil to flow from the first oil inlet 35b of the shuttle valve 35 to the oil outlet 35c of the shuttle valve 35. Therefore, in the present embodiment, by providing the first oil inlet 35a of the shuttle valve 35 and the oil inlet of the second shuttle valve 35 at both sides of the variable displacement motor 34, it is possible to guide the high-pressure oil entering the variable displacement motor 34 to the oil outlet 35c of the shuttle valve 35.
As shown in fig. 1, the hydraulic control directional control valve 36 has a first oil port, a second oil port, a third oil port and a fourth oil port, the first oil port 36a of the hydraulic control directional control valve 36 is communicated with the oil outlet 35c of the shuttle valve 35, the second oil port 36b of the hydraulic control directional control valve 36 is communicated with the rodless cavity of the motor variable cylinder 37, the third oil port 36c of the hydraulic control directional control valve 36 is communicated with the rod cavity of the motor variable cylinder 37, the fourth oil port 36d of the hydraulic control directional control valve 36 is communicated with the oil return cavity of the variable motor 34, the hydraulic control directional control valve 36 has a first state and a second state, when the hydraulic control directional control valve 36 is in the first state, the first oil port 36a of the hydraulic control directional control valve 36 is communicated with the second oil port 36b of the hydraulic control directional control valve 36, the third oil port 36c of the hydraulic control directional control valve 36 is communicated with the fourth oil port 36d of the hydraulic control directional control valve 36, when the directional control valve 36 is in the second state, the first oil port 36a, the second oil port 36b of the pilot operated directional control valve 36 and the fourth oil port 36d of the pilot operated directional control valve 36.
In this embodiment, referring to fig. 1, when the hydraulic control directional control valve 36 is in operation, if the hydraulic control directional control valve 36 is in the first state, the first oil port 36a of the hydraulic control directional control valve 36 is communicated with the second oil port 36b of the hydraulic control directional control valve 36, that is, the oil flowing out from the oil outlet 35c of the shuttle valve 35 is conveyed to the rodless chamber of the motor variable cylinder 37, the oil pushes the piston rod of the motor variable cylinder 37 to extend leftward, and pushes the oil in the rod chamber of the motor variable cylinder 37 to flow to the oil return chamber of the hydraulic motor through the fourth oil port 36d of the hydraulic control directional control valve 36, and finally return to the oil tank. At this time, the piston rod of the motor variable cylinder 37 is extended to the longest left to push the swash plate angle of the variable motor 34 to the minimum state, and the variable motor 34 is controlled to be at the minimum displacement.
If the pilot-controlled directional control valve 36 is in the second state, at this time, the second oil port 36b of the pilot-controlled directional control valve 36 is communicated with the fourth oil port 36d of the pilot-controlled directional control valve 36, the first oil port 36a of the pilot-controlled directional control valve 36 is communicated with the second oil port 36c of the pilot-controlled directional control valve 36, that is, the oil flowing out from the oil outlet 35c of the shuttle valve 35 is conveyed to the rod chamber of the variable motor cylinder 37, the oil pushes the piston rod of the variable motor cylinder 37 to be recovered rightwards, and pushes the oil in the rodless chamber of the variable motor cylinder 37 to flow to the oil return chamber of the hydraulic motor through the fourth oil port 36d of the pilot-controlled directional control valve 36, and finally flows back. At this time, the piston rod of the motor variable cylinder 37 is contracted to the right to the shortest extent to restore the swash plate angle of the variable motor 34 to the maximum state, thereby controlling the variable motor 34 to the maximum displacement.
In the embodiment of the present disclosure, the ocean lifting platform may include a lifting condition of the spud leg and a lifting condition of the ocean platform. And when the spud leg goes up and down the operating mode, hydraulic motor can be in little discharge capacity operating mode, and when platform goes up and down the operating mode, hydraulic motor can be in big discharge capacity operating mode. Therefore, the variable displacement motor 34 can be controlled to be in a proper displacement by controlling the working state of the pilot-controlled check valve in combination with the specific working condition of the ocean lifting platform. The embodiment of the disclosure adopts a variable motor 34 control mode, the output flow of the driving pump is not changed, and the speed is adjusted by changing the displacement of the variable motor 34, so that the flow output of the hydraulic system is greatly reduced, and the cost is reduced.
As shown in fig. 1, the hydraulic system may further include a fourth pipeline 24, the pilot-controlled directional valves 36 further have pilot-controlled ports, a pilot-controlled port 36e of each pilot-controlled directional valve 36 is connected to the fourth pipeline 24, an oil outlet of the second drive pump 15 is connected to the fourth pipeline 24, when the oil pressure at the pilot-controlled port 36e of the pilot-controlled directional valve 36 exceeds a set value, the pilot-controlled directional valve 36 is in the first state, and when the oil pressure at the pilot-controlled port 36e of the pilot-controlled directional valve 36 is less than the set value, the pilot-controlled directional valve 36 is in the second state. In this embodiment, the switching between the first state and the second state of the pilot-controlled directional control valve 36 is realized by introducing the oil with a certain oil pressure into the pilot port 36e of the pilot-controlled directional control valve 36, that is, when the oil pressure of the oil introduced into the pilot port 36e of the pilot-controlled directional control valve 36 exceeds a set value, the pressure of the oil can overcome the spring force of the pilot-controlled directional control valve 36, so that the pilot-controlled directional control valve 36 is in the second state, and when the oil pressure of the oil introduced into the pilot port 36e of the pilot-controlled directional control valve 36 is less than the set value, the pressure of the oil is not enough to overcome the spring force of the pilot-controlled directional control valve 36, so that the pilot-.
In the embodiment of the present disclosure, since the pilot port 36e of each pilot-controlled directional control valve 36 is connected to the fourth pipeline 24, that is, the pilot ports 36e of all the pilot-controlled directional control valves 36 are connected to the fourth pipeline 24 in parallel. Thus, when the second drive pump 15 is started, the oil can be equally distributed to the hydraulic control ports 36e of the different hydraulic control directional valves 36 through the fourth pipeline 24, the oil pressure of the hydraulic control ports 36e of the hydraulic control directional valves 36 is always ensured to be the same, the hydraulic control directional valves 36 can be switched simultaneously, and the impact on a hydraulic system in the process of regulating the flow of the variable motor 34 is reduced. And each hydraulic control reversing valve 36 is independently driven by the second driving pump 15 to pump oil, and is not influenced by the pressure of part of oil ways of the driving lifting unit, so that the reliability of the hydraulic system is enhanced.
As shown in fig. 1, the hydraulic system may further include a first on-off valve 41 and a second on-off valve 42 for controlling on/off of an oil path, the first on-off valve 41 being located on the oil path between the oil outlet of the second drive pump 15 and the third pipeline 23, and the second on-off valve 42 being located on the oil path between the second drive pump 15 and the fourth pipeline 24. By arranging the first switch valve 41 on the oil path between the oil outlet of the second drive pump 15 and the third pipeline 23, when the second drive pump 15 is required to control the hydraulic brake 33 to start, the first switch valve 41 can be used for controlling the communication of the oil path between the oil outlet of the second drive pump 15 and the third pipeline 23; when the hydraulic brake 33 is not required to be controlled to be started by the second driving pump 15, the first switch valve 41 is used for controlling the disconnection of the oil path between the oil outlet of the second driving pump 15 and the third pipeline 23, and the false starting is prevented. By arranging the second switch valve 42 on the oil path between the oil outlet of the second drive pump 15 and the fourth pipeline 24, when the second drive pump 15 is required to control the switching state of the hydraulic control reversing valve 36, the second switch valve 42 can be used for controlling the communication of the oil path between the oil outlet of the second drive pump 15 and the fourth pipeline 24; when the second drive pump 15 is not required to control the switching state of the hydraulic control reversing valve 36, the second switch valve 42 is used for controlling the disconnection of the oil path between the oil outlet of the second drive pump 15 and the fourth pipeline 24, and the false start is prevented.
Illustratively, the first switch valve 41 and the second switch valve 42 may be both switch four-way valves, each switch four-way valve has a first oil port, a second oil port, a third oil port and a fourth oil port, the switch four-way valves have two states, when the switch four-way valves are in the first state, the first oil port of the switch four-way valve is communicated with the second oil port of the switch four-way valve, and the third oil port of the switch four-way valve is communicated with the fourth oil port of the switch four-way valve; when the switch four-way valve is in the second state, a first oil port of the switch four-way valve is communicated with a third oil port of the switch four-way valve, and a second oil port of the switch four-way valve is communicated with a fourth oil port of the switch four-way valve. The four-way switch valve can be an electromagnetic reversing valve, the electromagnetic reversing valve is provided with an electromagnet, when the electromagnet is powered on, the electromagnetic reversing valve is in a first state, and when the electromagnet is powered off, the electromagnetic reversing valve is in a second state. When the electromagnetic directional valve is in different states, different oil ports are communicated or separated.
In this embodiment, as shown in fig. 1, the output oil port of the second driving pump 15 may be simultaneously communicated with the first oil ports of the two switching four-way valves, and the second oil ports of the two switching four-way valves are not connected or blocked, wherein the third oil port of the switching four-way valve as the first switching valve 41 is communicated with the third pipeline 23, the third oil port of the switching four-way valve as the second switching valve 42 is communicated with the fourth pipeline 24, and the fourth oil ports of the two switching four-way valves are communicated with the oil tank 20. The electromagnet of the four-way valve is controlled to be electrified or not so as to control whether the second driving pump 15 is communicated with the third pipeline 23 or the fourth pipeline 24 or not.
Taking the first switch valve 41 as an example, as shown in fig. 1, when the second driving pump 15 is required to control the hydraulic brakes 33 of the motor modules 3 to start simultaneously, at this time, the electromagnet of the switch four-way valve serving as the first switch valve 41 is controlled to be powered on, the switch four-way valve is switched to the second state, that is, the switch four-way valve is in the right position shown in fig. 1, at this time, the first oil port of the switch four-way valve is communicated with the third oil port of the switch four-way valve, and the oil pumped by the second driving pump 15 can be conveyed to the hydraulic brakes 33 through the switch four-way valve.
Alternatively, a third check throttle valve 18, which is a valve for controlling the flow of fluid by changing the throttle section or the throttle length, may be provided between the third port of the switching four-way valve as the first switching valve 41 and the third line 23. The third choke valve 18 is provided for regulating the flow of oil pumped by the second drive pump 15 to the hydraulic brake 33, thereby regulating the flow of oil entering the hydraulic brake 33 appropriately.
Optionally, a pressure reducing valve may be further disposed on an oil path between the first oil port of the four-way valve for opening and closing the second opening and closing valve 42 and the second driving pump 15, for reducing the pressure of the oil pumped by the second driving pump 15 to the pilot operated directional control valve 36, so as to improve safety.
As shown in fig. 1, the hydraulic system may further include an accumulator 51, an oil outlet of the accumulator 51 being connected to the oil passage between the oil outlet of the second drive pump 15 and the third pipe line 23, and an oil outlet of the accumulator 51 being connected to the oil passage between the oil outlet of the second drive pump 15 and the fourth pipe line 24. In the embodiment of the present disclosure, the accumulator 51 may serve as an auxiliary power source, the oil output by the accumulator 51 may provide control oil for the hydraulic brake 33 and the motor variable cylinder 37, and the impact of the oil path of the hydraulic system may be reduced to the maximum extent by providing the accumulator 51.
In the embodiment of the present disclosure, as shown in fig. 1, a normally open ball valve 52 may be disposed at the oil outlet of the energy accumulator 51, and when the oil outlet of the energy accumulator 51 needs to be quickly closed, the normally open ball valve 52 may be closed to achieve the purpose of quickly blocking the oil outlet of the energy accumulator 51. Meanwhile, a normally closed ball valve 53 can be arranged on an oil path between the energy accumulator 51 and the oil tank 20, the normally closed ball valve 53 is in a closed state when in a normal working state so as to seal the oil path between the energy accumulator 51 and the oil tank 20, and the normally closed ball valve 53 can be opened to drain oil in the energy accumulator 51 when the energy accumulator 51 needs to be overhauled. A relief valve 54 may be provided in the oil passage between the accumulator 51 and the tank 20, and when the oil pressure in the oil passage between the accumulator 51 and the tank 20 is excessive, a part of the oil may be released to the tank 20 by the relief valve 54, thereby protecting the accumulator 51. A pressure sensor 55 may be provided in the oil passage between the accumulator 51 and the tank 20, and the pressure sensor 55 may be used to measure the pressure in the oil passage between the accumulator 51 and the tank 20.
As shown in fig. 1, the hydraulic system may further include a first overflow valve 61 and a second overflow valve 62, an oil inlet of the first overflow valve 61 is communicated with the oil outlet of the first drive pump 11, an oil outlet of the first overflow valve 61 is communicated with the oil tank 20, an oil inlet of the second overflow valve 62 is communicated with the oil outlet of the second drive pump 15, and an oil outlet of the second overflow valve 62 is communicated with the oil tank 20. By arranging the first overflow valve 61 on the oil path between the first drive pump 11 and the two-position four-way valve 12, when the pressure of the oil pumped by the first drive pump 11 is too large, the first overflow valve 61 can discharge part of the oil to the oil tank 20, so that the excessive oil pressure on the oil path of the hydraulic system is avoided, and the safety is improved. Through set up second overflow valve 62 in the oil-out department of second drive pump 15, when the oil hydraulic pressure that second drive pump 15 pump sent was too big, second overflow valve 62 can be through leaking some fluid to tank 20 to avoid the oil pressure on hydraulic system's the oil circuit too big, improve the security.
As shown in fig. 1, the drive pump module further includes a first check valve 71, a second check valve 72, a third check valve 73, a fourth check valve 74 and a safety valve 75, an oil inlet of the first check valve 71 is connected to the oil path between the oil outlet of the first balance valve 13 and the first pipeline 21, an oil outlet of the first check valve 71 is communicated with the oil outlet of the second check valve 72, an oil inlet of the second check valve 72 is connected to the oil path between the oil outlet of the second balance valve 14 and the second pipeline 22, an oil outlet of the third check valve 73 is connected to the oil path between the oil outlet of the first balance valve 13 and the first pipeline 21, an oil inlet of the third check valve 73 is communicated with an oil inlet of the fourth check valve 74, an oil outlet of the fourth check valve 74 is connected to the oil path between the oil outlet of the second balance valve 14 and the second pipeline 22, an oil inlet of the safety valve 75 is connected to the oil path between the oil outlet of the first check valve 71 and the oil outlet of the second check valve 72, an oil outlet of the relief valve 75 is connected to an oil path between an oil inlet of the third check valve 73 and an oil inlet of the fourth check valve 74.
Optionally, the drive pump module further comprises a fifth one-way valve 76, an oil inlet of the fifth one-way valve 76 is communicated with an oil outlet of the relief valve 75, and an oil outlet of the fifth one-way valve 76 is communicated with the oil tank 20.
In the embodiment of the present disclosure, when the oil delivered to the first oil port of the variable motor 34 is high-pressure oil, the pressure of the oil path of the hydraulic system is too high, and if the oil pressure of the oil exceeds the pressure limit value of the safety valve 75, the oil passes through the first check valve 71 to the safety valve 75, passes through the safety valve 75, and is replenished to the pipeline at the second oil port of the variable motor 34 from the fourth check valve 74, and the surplus oil flows back to the oil tank 20 through the fifth check valve 76. When the oil delivered to the second port of the variable motor 34 is high-pressure oil, the pressure of the oil line of the hydraulic system is too high, and if the oil pressure of the oil exceeds the pressure limiting value of the safety valve 75, the oil passes through the second check valve 72 to the safety valve 75, passes through the safety valve 75, is supplemented to the pipeline at the first port of the variable motor 34 from the third check valve 73, and the redundant oil flows back to the oil tank 20 through the fifth check valve 76. By providing the safety valve 75 and five check valves, high pressure shock during operation of the hydraulic system can be reduced, and the hydraulic system can operate smoothly.
The above description is meant to be illustrative of the principles of the present disclosure and not to be taken in a limiting sense, and any modifications, equivalents, improvements and the like that are within the spirit and scope of the present disclosure are intended to be included therein.
Claims (10)
1. A hydraulic system for a rack and pinion lift platform, the hydraulic system comprising: a drive pump module, a tank (20), a first conduit (21), a second conduit (22) and a plurality of motor modules (3);
the driving pump module comprises a first driving pump (11), a two-position four-way valve (12), a hydraulic control port (131) of a first balance valve (13) and a second balance valve (14), wherein an oil inlet of the first driving pump (11) is communicated with the oil tank (20), an oil outlet of the first driving pump (11) is communicated with a first oil port (12a) of the two-position four-way valve (12), a second oil port (12b) of the two-position four-way valve (12) is communicated with an oil inlet of the first balance valve (13), an oil outlet of the first balance valve (13) is connected to the first pipeline (21), the hydraulic control port (131) of the first balance valve (13) is communicated with a third oil port (12c) of the two-position four-way valve (12), an oil inlet of the second balance valve (14) is communicated with a third oil port (12c) of the two-position four-way valve (12), and an oil outlet of the second balance valve (14) is connected to the second pipeline (22), a hydraulic control port (141) of the second balance valve (14) is communicated with a second oil port (12b) of the two-position four-way valve (12), and a fourth oil port (12d) of the two-position four-way valve (12) is communicated with the oil tank (20);
the motor module (3) is provided with a first oil port and a second oil port, the first oil port (31) of each motor module (3) is connected to the first pipeline (21), and the second oil port (32) of each motor module (3) is connected to the second pipeline (22).
2. The hydraulic system of a rack and pinion lifting platform according to claim 1, characterized in that it further comprises a third line (23), said motor module (3) further comprises a hydraulic brake (33) for braking a hydraulic motor, said drive pump module further comprises a second drive pump (15), an oil inlet of said second drive pump (15) communicates with said oil tank (20), an oil outlet of said second drive pump (15) is connected to said third line (23), and an oil inlet of the hydraulic brake (33) of each said motor module (3) is connected to said third line (23).
3. The hydraulic system of a rack and pinion lift platform according to claim 2, wherein the motor module (3) further comprises a variable displacement motor (34), a shuttle valve (35), a pilot operated directional control valve (36) and a motor variable cylinder (37) for controlling the displacement of the variable displacement motor (34),
the oil inlet of the variable motor (34) is communicated with the first pipeline (21), the oil outlet of the variable motor (34) is communicated with the second pipeline (22), the first oil inlet (35a) of the shuttle valve (35) is communicated with the oil outlet of the variable motor (34), the second oil inlet (35b) of the shuttle valve (35) is communicated with the oil inlet of the variable motor (34),
the hydraulic control reversing valve (36) is provided with a first oil port, a second oil port, a third oil port and a fourth oil port, the first oil port (36a) of the hydraulic control reversing valve (36) is communicated with an oil outlet (35c) of the shuttle valve (35), the second oil port (36b) of the hydraulic control reversing valve (36) is communicated with a rodless cavity of the motor variable cylinder (37), the third oil port (36c) of the hydraulic control reversing valve (36) is communicated with a rod cavity of the motor variable cylinder (37), the fourth oil port (36d) of the hydraulic control reversing valve (36) is communicated with an oil return cavity of the variable motor (34),
the hydraulic control reversing valve (36) is provided with a first state and a second state, when the hydraulic control reversing valve (36) is in the first state, a first oil port (36a) of the hydraulic control reversing valve (36) is communicated with a second oil port (36b) of the hydraulic control reversing valve (36), a third oil port (36c) of the hydraulic control reversing valve (36) is communicated with a fourth oil port (36d) of the hydraulic control reversing valve (36), when the hydraulic control reversing valve (36) is in the second state, the first oil port (36a) of the hydraulic control reversing valve (36) is communicated with the third oil port (36c) of the hydraulic control reversing valve (36), and the second oil port (36b) of the hydraulic control reversing valve (36) is communicated with the fourth oil port (36d) of the hydraulic control reversing valve (36).
4. The hydraulic system of a rack and pinion lifting platform according to claim 3, further comprising a fourth line (24), wherein the hydraulically controlled directional control valves (36) further have hydraulic control ports, wherein the hydraulic control port (36e) of each hydraulically controlled directional control valve (36) is connected to the fourth line (24), and wherein the oil outlet of the second drive pump (15) is connected to the fourth line (24),
when the oil pressure at the hydraulic control port (36e) of the hydraulic control reversing valve (36) exceeds a set value, the hydraulic control reversing valve (36) is in a first state, and when the oil pressure at the hydraulic control port (36e) of the hydraulic control reversing valve (36) is smaller than the set value, the hydraulic control reversing valve (36) is in a second state.
5. The hydraulic system of a rack and pinion lift platform according to claim 4, characterized in that it further comprises a first switch valve (41) and a second switch valve (42) for controlling the opening and closing of the oil circuit, said first switch valve (41) being located on the oil circuit between the oil outlet of the second drive pump (15) and the third line (23), said second switch valve (42) being located on the oil circuit between the second drive pump (15) and the fourth line (24).
6. Hydraulic system of a rack and pinion lifting platform according to claim 4, characterised in that it further comprises an accumulator (51), the oil outlet of said accumulator (51) being connected on the oil path between the oil outlet of said second drive pump (15) and said third line (23), and the oil outlet of said accumulator (51) being connected on the oil path between the oil outlet of said second drive pump (15) and said fourth line (24).
7. The hydraulic system of a rack and pinion lift platform of claim 2, further comprising a first spill valve (61) and a second spill valve (62), an oil inlet of the first spill valve (61) being in communication with an oil outlet of the first drive pump (11), an oil outlet of the first spill valve (61) being in communication with the oil tank (20), an oil inlet of the second spill valve (62) being in communication with an oil outlet of the second drive pump (15), an oil outlet of the second spill valve (62) being in communication with the oil tank (20).
8. The hydraulic system of a rack and pinion lift platform according to claim 1, characterized in that the drive pump module further comprises a first check valve (71), a second check valve (72), a third check valve (73), a fourth check valve (74), and a safety valve (75), an oil inlet of the first check valve (71) is connected on an oil path between an oil outlet of the first balance valve (13) and the first pipeline (21), an oil outlet of the first check valve (71) is communicated with an oil outlet of the second check valve (72), an oil inlet of the second check valve (72) is connected on an oil path between an oil outlet of the second balance valve (14) and the second pipeline (22), an oil outlet of the third check valve (73) is connected on an oil path between an oil outlet of the first balance valve (13) and the first pipeline (21), the oil inlet of the third check valve (73) is communicated with the oil inlet of the fourth check valve (74), the oil outlet of the fourth check valve (74) is connected to an oil path between the oil outlet of the second balance valve (14) and the second pipeline (22), the oil inlet of the safety valve (75) is connected to an oil path between the oil outlet of the first check valve (71) and the oil outlet of the second check valve (72), and the oil outlet of the safety valve (75) is connected to an oil path between the oil inlet of the third check valve (73) and the oil inlet of the fourth check valve (74).
9. The hydraulic system of a rack and pinion lift platform of claim 8, wherein the drive pump module further includes a fifth one-way valve (76), an oil inlet of the fifth one-way valve (76) being in communication with an oil outlet of the relief valve (75), an oil outlet of the fifth one-way valve (76) being in communication with the oil tank (20).
10. The hydraulic system of a rack and pinion lifting platform according to any one of claims 1 to 9, wherein the driving pump module further comprises a first one-way throttle valve (16) and a second one-way throttle valve (17), an oil inlet of the first one-way throttle valve (16) is communicated with the third oil port (12c) of the two-position four-way valve (12), an oil outlet of the first one-way throttle valve (16) is communicated with the hydraulic control port (131) of the first balance valve (13), an oil inlet of the second one-way throttle valve (17) is communicated with the second oil port (12b) of the two-position four-way valve (12), and an oil outlet of the second one-way throttle valve (17) is communicated with the hydraulic control port (141) of the second balance valve (14).
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| CN202010326462.8A CN111664135A (en) | 2020-04-23 | 2020-04-23 | Hydraulic system of gear rack lifting platform |
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| CN202010326462.8A CN111664135A (en) | 2020-04-23 | 2020-04-23 | Hydraulic system of gear rack lifting platform |
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| CN116928162A (en) * | 2023-09-15 | 2023-10-24 | 启东中远海运海洋工程有限公司 | Hydraulic system with energy recovery function for ocean lifting platform |
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