CN111677700B - Turnover elevator hydraulic system based on load port independent control - Google Patents

Turnover elevator hydraulic system based on load port independent control Download PDF

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Publication number
CN111677700B
CN111677700B CN202010422596.XA CN202010422596A CN111677700B CN 111677700 B CN111677700 B CN 111677700B CN 202010422596 A CN202010422596 A CN 202010422596A CN 111677700 B CN111677700 B CN 111677700B
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valve
oil
port
hydraulic
valve block
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CN111677700A (en
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刘凯磊
李宇
康绍鹏
丁力
叶霞
单文桃
巢渊
程伟
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Jiangsu University of Technology
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Jiangsu University of Technology
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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
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C1/00—Load-engaging elements or devices attached to lifting or lowering gear of cranes or adapted for connection therewith for transmitting lifting forces to articles or groups of articles
    • B66C1/10—Load-engaging elements or devices attached to lifting or lowering gear of cranes or adapted for connection therewith for transmitting lifting forces to articles or groups of articles by mechanical means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/08—Servomotor systems incorporating electrically operated control means

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

The invention provides a turnover elevator hydraulic system based on load port independent control, which comprises an oil tank, a hydraulic oil tank and a control unit, wherein the oil tank is used for storing hydraulic oil required by the hydraulic system; the quantitative pump is used for providing a constant flow of hydraulic oil for the hydraulic system; the first overflow valve is used for constant-pressure overflow of the hydraulic system; the oil supply valve group is used for supplying oil to the hydraulic system and controlling the actuating mechanism to act; the hydraulic lock valve group is used for sealing an oil way; the sequence valve group is used for controlling the extending and retracting sequence of the actuating mechanism; the executing structure comprises a valve hydraulic cylinder, a latch hydraulic cylinder, a turnover hydraulic cylinder, a lifting touch spring cylinder, an induction latch spring cylinder and a top drive lowering spring cylinder; the problem of the hydraulic system of present convertible elevator can not be fine satisfy various functional requirements of convertible elevator is solved, functional requirements such as valve, hasp, upset have been realized, and can drive through hydraulic pressure pipeline and transfer the signal to detect lifting by crane touch signal, response hasp close signal, top, realize the automated control of elevator operation.

Description

Turnover elevator hydraulic system based on load port independent control
Technical Field
The invention relates to the technical field of hydraulic transmission and control, in particular to a hydraulic system for realizing various functional requirements of a turnover elevator by utilizing a load port independent control technology.
Background
The elevator is one of key devices in the process of land oil exploration and development, is mainly used for hoisting pipe tools such as drill pipes, oil pipes, sleeves and the like, and is hung in hoisting rings on two sides of a hook of a hoisting system so as to facilitate the operation of hoisting or lowering drilling tools, oil pipes and sleeves into or out of a borehole. The relatively common elevator form is manual mechanical type, and manual mechanical type elevator adopts full manual work, and its change is frequent, the operating efficiency is low, work is slight big and work safety can not obtain the assurance.
Consequently, the convertible elevator of hydraulic pressure has appeared, its leading principle relies on hydraulic drive to realize the safe of elevator valve and hasp and opens and close, the upset of elevator body, and be equipped with relevant signal detection device, thereby can realize drilling tool and oil pipe, the sheathed tube is automatic to be sent into, it is frequent that manual mechanical type elevator is changed in the operation to have solved effectively, the operating efficiency is low, the poor scheduling problem of security, the convertible elevator of hydraulic pressure has novel structure, high safety and reliability, degree of automation is high, can realize advantages such as remote control, however, because the multifunctionality of the convertible elevator of hydraulic pressure has proposed higher requirement to its hydraulic system: (1) the valve and the latch need to act in sequence and have a middle locking function, and the speed can be controlled at any time in the opening and closing processes; (2) the overturning function of the elevator body is required to be floating in an initial state, and to be in a locking state when overturning is suspended, and the speed can be controlled at any time in the whole overturning process; (3) due to the fact that the operation site is complex, electric wires cannot be arranged around the elevator, and only hydraulic pipelines are available, the lifting touch signal, the induction lock latch closing signal and the top drive lowering signal are required to be induced by adopting hydraulic signals.
At present, a hydraulic system of a turnover elevator cannot well meet various functional requirements of the turnover elevator, so a new hydraulic system of the turnover elevator is urgently needed.
Disclosure of Invention
The invention discloses a turnover type elevator hydraulic system based on load port independent control, which solves the problem that the existing turnover type elevator hydraulic system cannot well meet various functional requirements of a turnover type elevator, realizes the functional requirements of a valve, a lock latch, turnover and the like, and can detect a lifting touch signal, a sensing lock latch closing signal and a top drive lowering signal through a hydraulic pipeline to realize the automatic control of elevator operation.
In order to achieve the purpose, the technical scheme of the invention is realized as follows:
the invention discloses a turnover elevator hydraulic system based on load port independent control, which comprises an oil tank, a constant delivery pump, a first overflow valve, an oil supply valve bank, a hydraulic lock valve bank, a sequence valve bank and an actuating mechanism, wherein the oil tank is used for storing hydraulic oil required by the hydraulic system; the quantitative pump is used for providing a constant flow of hydraulic oil for the hydraulic system; the first overflow valve is used for constant-pressure overflow of the hydraulic system; the oil supply valve group is used for supplying oil to the hydraulic system and controlling the actuating mechanism to act; the hydraulic lock valve group is used for sealing an oil way; the sequence valve group is used for controlling the extending and retracting sequence of the actuating mechanism; the executing structure comprises a valve hydraulic cylinder, a latch hydraulic cylinder, a turnover hydraulic cylinder, a lifting touch spring cylinder, an induction latch spring cylinder and a top drive lowering spring cylinder.
Further, an oil suction port T of the fixed displacement pump, an oil return port T of the first overflow valve and an oil return port T of the oil supply valve block are connected with an oil tank through hydraulic pipelines, an oil outlet P of the fixed displacement pump is connected with an oil inlet P of the oil supply valve bank and an oil inlet P of the first overflow valve through hydraulic pipelines, and a first working oil port A of the oil supply valve bank1The second working oil port B of the oil supply valve group is connected with an oil inlet P of the hydraulic lock valve group through a hydraulic pipeline1The hydraulic lock valve group is connected with an oil return port T of the hydraulic lock valve group through a hydraulic pipeline, and a third working oil port A of the oil supply valve group2A rodless cavity oil port A of the turning hydraulic cylinder is connected with the hydraulic pipeline, and a fourth working oil port B of the oil supply valve group2A rod cavity oil port B of the turning hydraulic cylinder is connected with a fifth working oil port A of the oil supply valve group (5) through a hydraulic pipeline3The hydraulic oil port A is connected with the working oil port A which is lifted to touch the spring cylinder, and the sixth working oil port A of the oil supply valve group4A working oil port A of the spring cylinder of the induction lock latch is connected with the hydraulic pipeline, and seventh working oil of the oil supply valve groupMouth A5The hydraulic oil port A is connected with the working oil port A of the top drive lowering spring cylinder through a hydraulic pipeline; the first working oil port A of the hydraulic lock valve group is connected with the oil inlet P of the sequence valve group through a hydraulic pipeline, the second working oil port B of the hydraulic lock valve group is connected with the oil return port T of the sequence valve group through a hydraulic pipeline, and the first working oil port A of the sequence valve group1A rodless cavity oil port A of the latch hydraulic cylinder is connected with the second working oil port B of the sequence valve group through a hydraulic pipeline1A rod cavity oil port B of the latch hydraulic cylinder is connected with the hydraulic pipeline, and a third working oil port B of the sequence valve group2The valve hydraulic cylinder is connected with a rodless cavity oil port A of the valve hydraulic cylinder through a hydraulic pipeline, and a fourth working oil port A of the sequence valve group2And the hydraulic cylinder is connected with a rod cavity oil port B of the valve hydraulic cylinder through a hydraulic pipeline.
Further, the oil supply valve group comprises an oil supply integrated valve block, the oil supply integrated valve block comprises a first load port independent control valve group, a second load port independent control valve group, a pressure sensor, a first pressure reducing valve, a second pressure reducing valve, a first filter, a second filter, a first ball valve, a second ball valve, a first secondary overflow valve, a second secondary overflow valve, a third secondary overflow valve, a first two-position two-way electromagnetic reversing valve, a second two-position two-way electromagnetic reversing valve, a third two-position two-way electromagnetic reversing valve, a first pressure relay, a second pressure relay and a third pressure relay, and an oil inlet P, an oil return port T, a first working oil port A and a second working oil port A are drilled in the oil supply integrated valve block respectively1A second working oil port B1And a third working oil port A2And a fourth working oil port B2The fifth working oil port A3And a sixth working oil port A4And a seventh working oil port A5The first ball valve is installed on the oil supply integrated valve block, an oil inlet P of the first ball valve is connected with the oil inlet P of the oil supply integrated valve block through an internal flow channel of the oil supply integrated valve block, the first filter is installed on the oil supply integrated valve block, the oil inlet P of the first filter is connected with an oil return port T of the first ball valve through the internal flow channel of the oil supply integrated valve block, and the oil return port T of the first filter is connected with the oil supply integrated valve block through the oil supply integrated valve blockThe internal flow passage of the valve block is connected with the oil inlet P of the first pressure reducing valve, the oil return port T of the first pressure reducing valve, the oil inlet P of the pressure sensor, the oil inlet P of the second load port independent control valve group, the oil inlet P of the first load port independent control valve group and the oil inlet P of the second pressure reducing valve are connected through the internal flow passage of the oil supply integrated valve block, the first working oil port A of the second load port independent control valve group is connected through the internal flow passage of the oil supply integrated valve block and the first working oil port A of the oil supply integrated valve block1The second working oil port B of the second load port independent control valve group passes through the internal flow passage of the oil supply integrated valve block and the second working oil port B of the oil supply integrated valve block1The first working oil port A of the first load port independent control valve group passes through the internal flow passage of the oil supply integrated valve block and the third working oil port A of the oil supply integrated valve block2The second working oil port B of the first load port independent control valve group passes through the internal flow passage of the oil supply integrated valve block and the fourth working oil port B of the oil supply integrated valve block2Link to each other, first two lead to solenoid directional valves, second two lead to solenoid directional valves and third two lead to solenoid directional valves install the oil supply integration valve piece, just the oil inlet P of third two lead to solenoid directional valves passes through the inside runner of oil supply integration valve piece with the oil return T of second relief pressure valve links to each other, oil return T of third two lead to solenoid directional valves, the oil inlet P of first secondary overflow valves, the oil inlet P of third pressure relay, the oil inlet P of second two lead to solenoid directional valves and the fifth work hydraulic fluid port A of oil supply integration valve piece3The oil return port T of the second two-position two-way electromagnetic directional valve, the oil inlet P of the second secondary overflow valve group, the oil inlet P of the second pressure relay, the oil inlet P of the first two-position two-way electromagnetic directional valve and the sixth working oil port A of the oil supply integrated valve block are connected with each other through the internal flow passage of the oil supply integrated valve block4The oil return port T of the first two-position two-way electromagnetic directional valve, the oil inlet P of the third secondary overflow valve group, the oil inlet P of the first pressure relay and the second oil inlet of the oil supply integrated valve block are connected through the internal flow passage of the oil supply integrated valve blockSeven working oil ports A5The internal flow passage through the oil supply integrated valve block is connected, the second ball valve is installed on the oil supply integrated valve block, an oil return port T of the second ball valve is connected with an oil return port T of the oil supply integrated valve block through the internal flow passage of the oil supply integrated valve block, the second filter is installed on the oil supply integrated valve block, the oil return port T of the second filter is connected with an oil inlet P of the second ball valve through the internal flow passage of the oil supply integrated valve block, and an oil inlet P of the second filter, an oil return port T of the second load port independent control valve group, an oil return port T of the first secondary overflow valve group, an oil return port T of the second secondary overflow valve group and an oil return port T of the third secondary overflow valve group are connected through the internal flow passage of the oil supply integrated valve block.
Furthermore, the hydraulic lock valve group comprises a hydraulic lock valve block, the hydraulic lock valve block comprises a first hydraulic control one-way valve and a second hydraulic control one-way valve, an oil inlet P, an oil return port T, a first working oil port A and a second working oil port B are respectively drilled on the hydraulic lock valve block, the first hydraulic control one-way valve and the second hydraulic control one-way valve are both installed on the hydraulic lock valve block, and an oil inlet P of the second hydraulic control one-way valve1Control oil port X of first hydraulic control one-way valve2The working oil port A of the second hydraulic control one-way valve is connected with an oil inlet P of the hydraulic lock valve block through an internal flow passage of the hydraulic lock valve block1The first working oil port A of the hydraulic lock valve block is connected with the internal flow passage of the hydraulic lock valve block, and the oil inlet P of the first hydraulic control one-way valve2And a control oil port X of the second hydraulic control check valve1The oil return port T of the hydraulic lock valve block is connected with the internal flow passage of the hydraulic lock valve block, and the working oil port A of the first hydraulic control one-way valve2And the second working oil port B of the hydraulic lock valve block is connected with the internal flow passage of the hydraulic lock valve block.
Furthermore, the sequence valve group comprises a sequence valve block, the sequence valve block comprises a first sequence valve and a second sequence valve, and an oil inlet P, an oil return port T and a first working oil port A are respectively drilled on the sequence valve block1A second working oil port B1And a third working oil port B2And a fourth working oil port A2The second sequence valve is arranged on the sequence valve block, and an oil inlet P of the second sequence valve1And a fourth working oil port B of the sequence valve block2The oil inlet P of the sequence valve block is connected with the oil inlet P of the sequence valve block through an internal flow passage of the sequence valve block, and the working oil port A of the second sequence valve1A first working oil port A of the sequence valve block1The sequence valve block is connected with the first sequence valve through an internal flow passage of the sequence valve block, the first sequence valve is arranged on the sequence valve block, and an oil inlet P of the first sequence valve2And a second working oil port B of the sequence valve block1And the oil return port T of the sequence valve block is connected with the internal flow passage of the sequence valve block, and the working oil port A of the first sequence valve2A fourth working oil port A passing through the hydraulic pipeline and the sequence valve block2Are connected.
Further, the first load port independent control valve group and the second load port independent control valve group are the same in composition and all comprise load port independent control valve blocks, each load port independent control valve block comprises a first two-position two-way normally open proportional valve, a second two-position two-way normally open proportional valve, a first two-position two-way normally closed proportional valve and a second two-position two-way normally closed proportional valve, an oil inlet P, an oil return port T, a first working oil port A and a second working oil port B are respectively drilled on each load port independent control valve block, the first two-position two-way normally open proportional valve, the second two-position two-way normally open proportional valve, the first two-position two-way normally closed proportional valve and the second two-position two-way normally closed proportional valve are all installed on each load port independent control valve block, and the oil inlet P of the second two-way normally closed proportional valve is installed on each load port independent control valve block1An oil inlet P of a first two-position two-way normally closed proportional valve2The working oil port A of the second two-position two-way normally closed proportional valve is connected with the oil inlet P of the load port independent control valve block through the internal flow passage of the load port independent control valve block1Working oil port A of second two-position two-way normally-open proportional valve3The first working oil port A of the load port independent control valve block is connected with the internal flow passage of the load port independent control valve block, and the working oil port A of the first two-position two-way normally-closed proportional valve2Working oil port A of first two-position two-way normally open proportional valve4Independently controlled from the load portA second working oil port B of the valve making block is connected with an internal flow passage of the load port independent control valve block, and an oil inlet P of a second two-position two-way normally open proportional valve3Oil inlet P of first two-position two-way normally open proportional valve4And the oil return port T of the load port independent control valve block is connected with an internal flow passage of the load port independent control valve block.
Furthermore, the first secondary overflow valve group, the second secondary overflow valve group and the third secondary overflow valve group are the same in composition and respectively comprise a secondary overflow valve block, the secondary overflow valve block comprises a second overflow valve and a check valve, an oil inlet P and a working oil port A are respectively drilled on the secondary overflow valve block, the check valve is installed on the secondary overflow valve block, the second overflow valve is installed on the secondary overflow valve block, and the working oil port A of the check valve is1And a working oil port A of a second overflow valve1The working oil port A of the secondary overflow valve block is connected with the working oil port A of the secondary overflow valve block through an internal flow passage on the secondary overflow valve block, and the oil inlet P of the one-way valve1An oil inlet P of a second overflow valve1And the oil inlet P of the secondary overflow valve block is connected with an internal flow passage on the secondary overflow valve block.
Further, the first sequence valve and the second sequence valve have the same composition, and the composition of the first sequence valve and the second sequence valve is the same as that of the first secondary overflow valve group, the second secondary overflow valve group and the third secondary overflow valve group.
The beneficial technical effects are as follows:
1. the invention provides a turnover elevator hydraulic system based on load port independent control, which comprises an oil tank, a constant delivery pump, a first overflow valve, an oil supply valve bank, a hydraulic lock valve bank, a sequence valve bank and an actuating mechanism, wherein the oil tank is used for storing hydraulic oil required by the hydraulic system; the quantitative pump is used for providing a constant flow of hydraulic oil for the hydraulic system; the first overflow valve is used for constant-pressure overflow of the hydraulic system; the oil supply valve group is used for supplying oil to the hydraulic system and controlling the actuating mechanism to act; the hydraulic lock valve group is used for sealing an oil way; the sequence valve group is used for controlling the extending and retracting sequence of the actuating mechanism; the execution structure comprises a valve hydraulic cylinder, a latch hydraulic cylinder, a turnover hydraulic cylinder, a lifting touch spring cylinder, an induction latch spring cylinder and a top drive lowering spring cylinder, the problem that the hydraulic system of the conventional turnover elevator cannot well meet various functional requirements of the turnover elevator is solved, the functional requirements of the valve, the latch, the turnover and the like are met, lifting touch signals, induction latch closing signals and top drive lowering signals can be detected through hydraulic pipelines, and automatic control of elevator operation is realized;
2. in the invention, the sequence valve, the hydraulic lock valve and the two-position two-way electromagnetic proportional valve are used for controlling the valve hydraulic cylinder and the latch hydraulic cylinder, thereby realizing the functions of sequence control, middle position locking, speed control and the like of the valve and the latch;
3. according to the invention, the four two-position two-way electromagnetic proportional valves are used for controlling the turnover hydraulic cylinder, so that the functions of floating at the beginning, locking at the time of suspension, speed control and the like are realized;
4. the invention uses the small spring cylinder, the secondary overflow valve and the pressure relay to complete the detection of the lifting touch signal, the induction lock latch closing signal and the top drive lowering signal, thereby realizing various functions of the hydraulic turnover elevator.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, 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 invention, 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 schematic diagram of a turnover elevator hydraulic system based on load port independent control according to the present invention;
FIG. 2 is a schematic diagram of an oil supply valve block of the turnover elevator hydraulic system based on independent control of a load port;
FIG. 3 is a schematic diagram of a load port independent control valve block of the turnover elevator hydraulic system based on load port independent control according to the present invention;
FIG. 4 is a schematic diagram of a hydraulic lock valve block of the turnover elevator hydraulic system based on load port independent control according to the present invention;
FIG. 5 is a schematic diagram of a sequence valve block of the turnover elevator hydraulic system based on load port independent control according to the present invention;
fig. 6 is a schematic diagram of a secondary overflow valve block of the turnover elevator hydraulic system based on load port independent control.
Wherein, 2-an actuating mechanism, 21-a valve hydraulic cylinder, 22-a latch hydraulic cylinder, 23-a turnover hydraulic cylinder, 24-a lifting touch spring cylinder, 25-an induction latch spring cylinder, 26-a top drive lowering spring cylinder, 3-a sequence valve bank, 31-a sequence valve block, 311-a first sequence valve, 312-a second sequence valve, 3111-a third overflow valve, 3112-a second one-way valve, 4-a hydraulic lock valve bank, 41-a hydraulic lock valve block, 411-a first hydraulic control one-way valve, 412-a second hydraulic control one-way valve, 5-an oil supply valve bank, 51-an oil supply integration valve block, 51 a-a first load port independent control valve bank, 51 b-a second load port independent control valve bank, 51 c-a pressure sensor, 51 d-a first pressure reducing valve and 51 e-a second pressure reducing valve, 51 f-a first filter, 51 g-a second filter, 51 h-a first ball valve, 51 i-a second ball valve, 51 j-a first secondary overflow valve bank, 51 k-a second secondary overflow valve bank, 51 l-a third secondary overflow valve bank, 51 m-a first two-position two-way solenoid valve, 51 n-a second two-position two-way solenoid valve, 51 p-a third two-position two-way solenoid valve, 51 q-a first pressure relay, 51 r-a second pressure relay, 51 s-a third pressure relay, 511-a load port independent control valve block, 5111-a first two-position two-way normally open proportional valve, 5112-a second two-way normally open proportional valve, 5113-a first two-position two-way normally closed proportional valve, 5114-a second two-position two-way normally closed proportional valve, 512-a secondary overflow valve block, 5121-a second overflow valve, 5122-a first check valve, 6-a first overflow valve, 7-a fixed displacement pump and 8-an oil tank.
Detailed Description
Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the accompanying drawings are illustrative only for the purpose of explaining the present invention, and are not to be construed as limiting the present invention.
It should be noted that the terms "first", "second", and the like are used to define the components, and are only used for convenience of distinguishing the corresponding components, and the terms have no special meanings unless otherwise stated, and therefore, the scope of the present invention should not be construed as being limited.
Embodiments of the present invention will be described in detail below with reference to the accompanying drawings.
The invention discloses a turnover type elevator hydraulic system based on load port independent control, and referring to fig. 1-6, the turnover type elevator hydraulic system based on load port independent control comprises an oil tank 8, a constant delivery pump 7, a first overflow valve 6, an oil supply valve group 5, a hydraulic lock valve group 4, a sequence valve group 3 and an actuating mechanism 2, wherein the oil tank 8 is used for storing hydraulic oil required by the hydraulic system; the fixed displacement pump 7 is used for providing a constant flow of hydraulic oil for a hydraulic system; the first overflow valve 6 is used for constant pressure overflow of the hydraulic system; the oil supply valve group 5 is used for supplying oil to the hydraulic system and controlling the actuating mechanism to act; the hydraulic lock valve group 4 is used for sealing an oil way; the sequence valve group 3 is used for controlling the extending and retracting sequence of the actuating mechanism; the actuator 2 includes a ram cylinder 21, a latch cylinder 22, a tilt cylinder 23, a hoist touch spring cylinder 24, an inductive latch spring cylinder 25 and a top drive lower spring cylinder 26.
As an embodiment of the present invention, specifically, referring to fig. 1, an oil suction port T of a fixed displacement pump 7, an oil return port T of a first overflow valve 6, and an oil return port T of an oil supply valve block 5 are connected to an oil tank 8 through hydraulic pipelines, an oil outlet P of the fixed displacement pump 7 is connected to an oil inlet P of the oil supply valve block 5 and an oil inlet P of the first overflow valve 6 through hydraulic pipelines, and a first working oil port a of the oil supply valve block 5 is connected to a first working oil port a1A second working oil port B of the oil supply valve group 5 is connected with an oil inlet P of the hydraulic lock valve group 4 through a hydraulic pipeline1A third working oil port A of the oil supply valve group 5 is connected with an oil return port T of the hydraulic lock valve group 4 through a hydraulic pipeline2A fourth working oil port B of the oil supply valve group 5 is connected with a rodless cavity oil port A of the turning hydraulic cylinder 23 through a hydraulic pipeline2A fifth working oil port A of the oil supply valve group 5 is connected with a rod cavity oil port B of the turning hydraulic cylinder 23 through a hydraulic pipeline3Work by touching the spring cylinder 24 with the lifting crane through hydraulic linesThe oil ports A are connected, and a sixth working oil port A of the oil supply valve group 54A seventh working oil port A of the oil supply valve group 5 is connected with the working oil port A of the induction lock bolt spring cylinder 25 through a hydraulic pipeline5The hydraulic cylinder is connected with a working oil port A of the top drive downward-placing spring cylinder 9 through a hydraulic pipeline; the first working oil port A of the hydraulic lock valve group 4 and the oil inlet P of the sequence valve group 3 are connected through a hydraulic pipeline, the second working oil port B of the hydraulic lock valve group 4 and the oil return port T of the sequence valve group 3 are connected through a hydraulic pipeline, and the first working oil port A of the sequence valve group 31A second working oil port B of the sequence valve group 3 is connected with a rodless cavity oil port A of the latch hydraulic cylinder 22 through a hydraulic pipeline1A third working oil port B of the sequence valve group 3 is connected with a rod cavity oil port B of the latch hydraulic cylinder 22 through a hydraulic pipeline2A rodless cavity oil port A of the valve hydraulic cylinder 21 is connected with the fourth working oil port A of the sequence valve group 3 through a hydraulic pipeline2The hydraulic system can meet the functional requirements of the valve, the latch, the turnover and the like by connecting the hydraulic pipeline with the oil port B of the rod cavity of the valve hydraulic cylinder 21, and can detect a lifting touch signal, a sensing latch closing signal and a top drive lowering signal through the hydraulic pipeline to realize the automatic control of the elevator operation.
As an embodiment of the present invention, the oil supply valve group 5 includes an oil supply integration valve block 51, referring to fig. 2, the oil supply integration valve block 51 includes a first load port independent control valve group 51a, a second load port independent control valve group 51b, a pressure sensor 51c, a first pressure reducing valve 51d, a second pressure reducing valve 51e, a first filter 51f, a second filter 51g, a first ball valve 51h, a second ball valve 51i, a first secondary overflow valve 51j, a second secondary overflow valve 51k, a third secondary overflow valve 51l, a first two-position two-way electromagnetic directional valve 51m, a second two-position two-way electromagnetic directional valve 51n, a third two-position two-way electromagnetic directional valve 51P, a first pressure relay 51q, a second pressure relay 51r, and a third pressure relay 51s, an oil inlet P, an oil return port T, and a first working oil port a are drilled on the oil supply integration valve block 511A second working oil port B1And a third working oil port A2And a fourth working oil port B2The fifth working oil port A3And a sixth working oil port A4And seventh operationOil port A5The first ball valve 51h is mounted on the oil supply integration valve block 51 by a screw, and an oil inlet P of the first ball valve 51h is connected with an oil inlet P of the oil supply integration valve block 51 through an internal flow passage of the oil supply integration valve block 51, the first filter 51f is mounted on the oil supply integration valve block 51 by a screw, and the oil inlet P of the first filter 51f is connected with an oil return port T of the first ball valve 51h through an internal flow passage of the oil supply integration valve block 51, the oil return port T of the first filter 51f is connected with an oil inlet P of the first pressure reducing valve 51d through an internal flow passage of the oil supply integration valve block 51, the oil return port T of the first pressure reducing valve 51d, the oil inlet P of the pressure sensor 51c, the oil inlet P of the second load port independent control valve group 51b, the oil inlet P of the first load port independent control valve group 51a, and the oil inlet P of the second pressure reducing valve 51e are connected through an internal flow passage of the oil supply integration valve block 51, the first working port a of the second load port independent control valve group 51b passes through the internal flow passage of the oil supply integration valve block 51 and the first working port a of the oil supply integration valve block 511The second working port B of the second load port independent control valve group 51B is connected with the second working port B of the oil supply integration valve block 51 through the internal flow passage of the oil supply integration valve block 511The first working port a of the first load port independent control valve group 51a is connected with the third working port a of the oil supply integration valve block 51 through the internal flow passage of the oil supply integration valve block 512The second working port B of the first load port independent control valve group 51a is connected with the fourth working port B of the oil supply integration valve block 51 through the internal flow passage of the oil supply integration valve block 512The first two-position two-way electromagnetic directional valve 51m, the second two-position two-way electromagnetic directional valve 51n and the third two-position two-way electromagnetic directional valve 51P are installed on the oil supply integrated valve block 51 through screws, an oil inlet P of the third two-position two-way electromagnetic directional valve 51P is connected with an oil return port T of the second reducing valve 51e through an internal flow passage of the oil supply integrated valve block 51, an oil return port T of the third two-position two-way electromagnetic directional valve 51P, an oil inlet P of the first secondary overflow valve group 51j, an oil inlet P of the third pressure relay 51s, an oil inlet P of the second two-position two-way electromagnetic directional valve 51n and a fifth working oil port A of the oil supply integrated valve block 513An oil return port of the second two-position two-way electromagnetic directional valve 51n is connected through an internal flow passage of the oil supply integrated valve block 51T, an oil inlet P of a second secondary overflow valve group 51k, an oil inlet P of a second pressure relay 51r, an oil inlet P of a first two-position two-way electromagnetic directional valve 51m and a sixth working oil port A of an oil supply integrated valve block 514Connected through an internal flow passage of the oil supply integration valve block 51, an oil return port T of the first two-position two-way electromagnetic directional valve 51m, an oil inlet P of the third secondary overflow valve group 51l, an oil inlet P of the first pressure relay 51q and a seventh working oil port A of the oil supply integration valve block 515The internal flow passage through the oil supply integration valve block 51 is connected, the second ball valve 51i is installed on the oil supply integration valve block 51 through a screw, and the oil return port T of the second ball valve 51i is connected with the oil return port T of the oil supply integration valve block 51 through the internal flow passage of the oil supply integration valve block 51, the second filter 51g is installed on the oil supply integration valve block 51, and the oil return port T of the second filter 51g is connected with the oil inlet P of the second ball valve 51i through the internal flow passage of the oil supply integration valve block 51, the oil inlet P of the second filter 51g, the oil return port T of the second load port independent control valve group 51b, the oil return port T of the first load port independent control valve group 51a, the oil return port T of the first secondary overflow valve group 51j, the oil return port T of the second secondary overflow valve group 51k and the oil return port T of the third secondary overflow valve group 51l are connected through the internal flow passage of the integration oil supply valve block 51, preferably, the first secondary overflow valve group 51j, the second secondary overflow valve group 51k and the third secondary overflow valve group 51l have the same composition, referring to fig. 6, each secondary overflow valve group 512 includes a secondary overflow valve block 512, the secondary overflow valve block 512 includes a second overflow valve 5121 and a first check valve 5122, an oil inlet P and a working oil port a are drilled in the secondary overflow valve block 512, the first check valve 5122 is mounted on the secondary overflow valve block 512 by screws, the second overflow valve 5121 is mounted on the secondary overflow valve block 512 by screws, and the working oil port a of the first check valve 5122 is drilled in the second overflow valve block 512 by screws1And a working oil port A of the second overflow valve 51211The working oil port A of the secondary overflow valve block 512 is connected with the inner flow passage on the secondary overflow valve block 512, and the oil inlet P of the first check valve 51221And an oil inlet P of a second overflow valve 51211And an oil inlet P of the secondary overflow valve block 512 is connected with an internal flow passage on the secondary overflow valve block 512.
As an embodiment of the present invention, the working principle of the secondary overflow valve group is that when hydraulic oil enters from the oil inlet P of the secondary overflow valve block 512 and exits from the working oil port a, the hydraulic oil cannot pass through the first check valve 5122, and only when the pressure of the hydraulic oil flowing into the secondary overflow valve block 512 reaches the set pressure value of the second overflow valve 5121, the second overflow valve 5121 is opened, and the hydraulic oil can pass through the second overflow valve 5121 and exit from the working oil port a of the secondary overflow valve block 512, so that a high-pressure overflow effect can be achieved; when hydraulic oil enters from the working oil port a and exits from the oil inlet P, the hydraulic oil flows out from the oil inlet P of the secondary overflow valve block 512 through the first check valve 5122, and does not flow through the second overflow valve 5121.
As an embodiment of the present invention, the operating principle of the oil supply valve group 5 is as follows: hydraulic oil flows through an oil inlet P of the oil supply integration valve block 51, passes through the first ball valve 51h, the first filter 51f and the first pressure reducing valve 51d, and is divided into four branches: the first path flows into the pressure sensor 51c, and can detect the system pressure of the hydraulic system; the second path flows into the second load port independent control valve group 51b, and the hydraulic oil flowing out of the second load port independent control valve group 51b flows from the first working oil port a of the oil supply integrated valve block 511Or the second working oil port B1The hydraulic oil flows out, the oil is supplied to the latch hydraulic cylinder 22 and the valve hydraulic cylinder 21, the hydraulic oil flowing back from the latch hydraulic cylinder 22 and the valve hydraulic cylinder 21 flows through the second load port independent control valve group 51b, the second filter 51g and the second ball valve 51i, and flows back to the oil tank through the oil return port T of the oil supply integrated valve block 51, so that the control of the latch hydraulic cylinder 22 and the valve hydraulic cylinder 21 by the second load port independent control valve group 51b is realized; the third path flows into the first load port independent control valve group 51a, and the hydraulic oil flowing from the first load port independent control valve group 51a flows from the third working oil port A of the oil supply integrated valve block 512Or the fourth working oil port B2The hydraulic oil flows out and is supplied to the overturning hydraulic cylinder 23, and the hydraulic oil flowing back from the overturning hydraulic cylinder 23 flows back to the oil tank through the oil return port T of the oil supply integrated valve block 51 by passing through the first load port independent control valve group 51a, the second filter 51g and the second ball valve 51i, so that the control of the first load port independent control valve group 51a on the overturning hydraulic cylinder 23 is realized; the fourth path of the current flows through a second reducing valve 51e, a third two-position two-way electromagnetic directional valve 51p and a second two-position two-way electromagnetic directional valveThe hydraulic oil respectively flows into a fifth working oil port A of the oil supply integrated valve block 51 through the two-position two-way electromagnetic directional valve 51m3And a sixth working oil port A4And a seventh working oil port A5When the third two-position two-way electromagnetic directional valve 51p is powered on and becomes a passage, and the second two-position two-way electromagnetic directional valve 51n and the first two-position two-way electromagnetic directional valve 51m are powered off and become a circuit break, the hydraulic oil passes through the third two-position two-way electromagnetic directional valve 51p and passes through the fifth working oil port a of the oil supply integrated valve block 513Supplying oil to the lifting touch spring cylinder 24, when the third two-position two-way electromagnetic directional valve 51p and the second two-position two-way electromagnetic directional valve 51n are simultaneously electrified to be changed into a passage, and the first two-position two-way electromagnetic directional valve 51m is electrified to be changed into a circuit breaking state, hydraulic oil passes through the third two-position two-way electromagnetic directional valve 51p and the second two-position two-way electromagnetic directional valve 51n and passes through a sixth working oil port A of the oil supply integrated valve block 514Supplying oil to the induction latch spring cylinder 25, after the third two-position two-way electromagnetic directional valve 51p, the second two-position two-way electromagnetic directional valve 51n and the first two-position two-way electromagnetic directional valve 51m are simultaneously electrified and changed into a passage, the hydraulic oil passes through the third two-position two-way electromagnetic directional valve 51p, the second two-position two-way electromagnetic directional valve 51n and the first two-position two-way electromagnetic directional valve 51m, and passes through a seventh working oil port A of the oil supply integrated valve block 514Supplying oil to the induction latch spring cylinder 26, and in an initial state, respectively supplying oil to the lifting contact spring cylinder 24, the induction latch spring cylinder 25 and the spring cylinder 26 below the top drive through the third two-position two-way electromagnetic directional valve 51p, the second two-position two-way electromagnetic directional valve 51n and the first two-position two-way electromagnetic directional valve 51m, so as to ensure that all three spring cylinders are extended, taking the induction latch spring cylinder 25 as an example, in the initial state, setting the pressure of the second reducing valve 51e and the pressure of the second secondary overflow valve 51k, enabling the set pressure of the second reducing valve 51e to be smaller than the set pressure of the second secondary overflow valve 51k, opening the third two-position two-way electromagnetic directional valve 51p and the second two-position two-way electromagnetic directional valve 51n, and supplying oil to the sixth working oil port a of the oil supply integrated valve block 514The oil supply is performed, and the third two-position two-way electromagnetic directional valve 51p and the second two-position two-way electromagnetic directional valve 51n are closed after the oil supply is completed due to the oil supply pressure set by the second pressure reducing valve 51eThe pressure of the oil supply is lower than the set oil supply pressure of the second secondary overflow valve 51k, so that the second secondary overflow valve 51k is closed, the oil in the sensing latch spring cylinder 25 is locked and cannot flow out, when the sensing latch spring cylinder 25 is touched, the pressure of a rodless cavity of the sensing latch spring cylinder is increased, the pressure of the oil inlet P of the second secondary overflow valve 51k is increased, the second pressure relay 51r of the oil inlet P of the second secondary overflow valve 51k detects the information, converts the information into an electric signal and feeds the electric signal back to the controller, signal conversion and signal feedback are completed, when the pressure is continuously increased and reaches the set pressure of the second secondary overflow valve 51k, the second secondary overflow valve 51k is opened, and the oil flows back to the oil tank through the second filter 51g and the second ball valve 51i and the oil return port T of the oil supply integrated valve block 51.
As an embodiment of the present invention, the first and second load port independent control valve groups 51a and 51b have the same composition and each include a load port independent control valve block 511, see fig. 3, the load port independent control valve block 511 includes a first two-position two-way normally open proportional valve 5111, a second two-position two-way normally open proportional valve 5112, a first two-position two-way normally closed proportional valve 5113 and a second two-position two-way normally closed proportional valve 5114, specifically, the load port independent control valve block 511 is drilled with an oil inlet P and an oil return port T, the first working oil port A and the second working oil port B, the first two-position two-way normally open proportional valve 5111, the second two-position two-way normally open proportional valve 5112, the first two-position two-way normally closed proportional valve 5113 and the second two-position two-way normally closed proportional valve 5114 are all installed on the load port independent control valve block 511 through screws, and the second two-position two-way normally closed proportional valve 5114 has an oil inlet P.1An oil inlet P of a first two-position two-way normally closed proportional valve 51132An oil inlet P of the load port independent control valve block 511 is connected with an internal flow passage of the load port independent control valve block 511, and a working oil port A of a second two-position two-way normally-closed proportional valve 51141And a working oil port A of a second two-position two-way normally-open proportional valve 51123A first working oil port A of the first two-position two-way normally-closed proportional valve 5114 is connected with the first working oil port A of the load port independent control valve block 511 through an internal flow passage of the load port independent control valve block 5112And a working oil port A of a first two-position two-way normally-open proportional valve 51114The second working oil port B of the load port independent control valve block 511 is connected with an internal flow passage of the load port independent control valve block 511, and an oil inlet P of a second two-position two-way normally-open proportional valve 51123Oil inlet P of first two-position two-way normally-open proportional valve 51114And the oil return port T of the load port independent control valve block 511 are connected through an internal flow passage of the load port independent control valve block 511.
As an embodiment of the present invention, the first load port independent control valve group 51a and the second load port independent control valve group 51B have the same working principle, and when the load port independent control valve group is in an initial state, that is, when all four proportional solenoid valves are de-energized, since the first two-position two-way normally open proportional valve 5111 and the second two-position two-way normally open proportional valve 5112 are normally open, the first working oil port a, the second working oil port B and the oil return port T of the load port independent control valve group are communicated, a Y-type neutral position function can be realized, and further, the hydraulic cylinder can float; when the controller senses an input signal of the electric control switch, the controller sends an electric control signal to four electromagnetic valves of the load port independent control valve group according to corresponding logic control, so that proportional electromagnets of the second two-position two-way normally-closed proportional valve 5114 and the second two-position two-way normally-opened proportional valve 5112 are electrified, proportional electromagnets of the first two-position two-way normally-opened proportional valve 5111 and the first two-position two-way normally-closed proportional valve 5113 are electrified, the second two-position two-way normally-closed proportional valve 5114 and the second two-position two-way normally-opened proportional valve 5113 are both arranged at the right position, and the P is enabled to be switched to the right position1、A1Is turned on and P3、A3Close, therefore, the oil entering the load port independent control valve group through the oil inlet P of the load port independent control valve block passes through the second two-position two-way normally-closed proportional valve 5114, and the oil is supplied to the hydraulic cylinder through the first working oil port a of the load port independent control valve block, and the first two-position two-way normally-open proportional valve 5111 and the second two-position two-way normally-closed proportional valve 5114 are both in a power-off state, the oil flowing back from the hydraulic cylinder enters the load port independent control valve group through the second working oil port B of the load port independent control valve block, passes through the first two-position two-way normally-open proportional valve 5111, and flows back to the oil tank through the oil return port T of the load port independent control valve block, thereby realizing that the oil inlet P of the load port independent control valve group flows back to the oil inlet a of the first working oil port a through the oil return port PSupplying oil, and returning oil from the second working oil port B to the oil return port T; when oil supply from an oil inlet P of the load port independent control valve group to a second working oil port B is to be realized, and oil return from a first working oil port A to an oil return port T is to be realized, the oil supply from the oil inlet P to the second working oil port B can be realized only by electrifying the proportional solenoid valves of the first two-position two-way normally-open proportional valve 5111 and the first two-position two-way normally-closed proportional valve 5113 and electrifying the proportional electromagnets of the second two-position two-way normally-open proportional valve 5114 and the second two-position two-way normally-open proportional valve 5112, and returning oil from the first working oil port A to the oil return port T; when the controller judges that the working hydraulic cylinder reaches a specified position according to information fed back by the pressure relay, according to corresponding logic control, proportional electromagnets of the first two-position two-way normally-open proportional valve 5111 and the second two-position two-way normally-open proportional valve 5112 are electrified, proportional electromagnets of the first two-position two-way normally-closed proportional valve 5113 and the second two-position two-way normally-closed proportional valve 5114 are deenergized, the first two-position two-way normally-open proportional valve 5111 and the second two-position two-way normally-open proportional valve 5112 are both positioned at the right position, oil cannot enter the hydraulic cylinder, oil in the hydraulic cylinder cannot return to the oil tank, a piston rod of the hydraulic cylinder is locked, and an O-type middle-position function is realized; the load port independent control system adopts the electromagnetic proportional valve, so that the opening of the valve port of the electromagnetic proportional valve can be changed by adjusting the input current, the flow entering the hydraulic cylinder is adjusted, the speed is adjusted, the valve port of the electromagnetic proportional valve controlling the outlet of the hydraulic cylinder is opened to the maximum without throttling while the throttling and the speed adjusting are performed on the inlet of the hydraulic cylinder, and partial throttling loss can be saved, thereby saving energy.
As an embodiment of the present invention, the hydraulic lock valve group 4 includes a hydraulic lock valve block 41, referring to fig. 4, the hydraulic lock valve block includes a first hydraulic control check valve 411 and a second hydraulic control check valve 412, an oil inlet P, an oil return port T, a first working oil port a and a second working oil port B are respectively drilled on the hydraulic lock valve block 41, the first hydraulic control check valve 411 and the second hydraulic control check valve 412 are both mounted on the hydraulic lock valve block 41 by screws, and an oil inlet P of the second hydraulic control check valve 412 is installed on the oil inlet P of the hydraulic lock valve block 411The control port X of the first hydraulic control check valve 4112And internal flow of the oil inlet P of the hydraulic lock valve block 41 through the hydraulic lock valve block 41The working oil port A of the second hydraulic control one-way valve 412 is connected with the other working oil port A1The first working oil port A of the hydraulic lock valve block 41 is connected with the internal flow passage of the hydraulic lock valve block 41, and the oil inlet P of the first hydraulic control one-way valve 4112And a control port X of the second hydraulic control check valve 4121An oil return port T of the hydraulic lock valve block 41 is connected with an internal flow passage of the hydraulic lock valve block 41, and a working oil port A of the first hydraulic control one-way valve 4112And is connected with the second working port B of the hydraulic lock valve block 41 through an internal flow passage of the hydraulic lock valve block 41.
As an embodiment of the present invention, the working principle of the hydraulic lock valve set 4 is as follows: when no oil flows in from the oil inlet P or the oil return port T of the hydraulic lock valve block 41, the one-way throttle valve has a reverse blocking function, so that oil paths from the first working oil port a of the hydraulic lock valve block 41 to the oil inlet P of the hydraulic lock valve block 41 and from the second working oil port B of the hydraulic lock valve block 41 to the oil return port T of the hydraulic lock valve block 41 are not communicated, the oil flowing back from the hydraulic cylinder cannot flow back to the oil tank, and the hydraulic cylinder is locked; when oil flows, the oil flowing from the oil inlet P of the hydraulic lock valve block 41 is divided into two paths: p flowing all the way to the second hydraulic check valve 4121A mouth; the other way flows to the control oil port X of the first hydraulic control one-way valve 4112Due to the fact that from P1To A1Is conducted, so the oil passes through the second pilot operated check valve 412 and flows to the hydraulic cylinder through the first working port a of the hydraulic lock valve block 41 to the first pilot operated check valve 411 to control the port X2The oil opens the first pilot operated check valve 411 to enable a2To P2And therefore, oil flowing back from the hydraulic cylinder passes through the second working oil port B of the hydraulic lock valve block 41, passes through the first hydraulic control one-way valve 411, and finally flows back to the oil tank through the oil return port T of the hydraulic lock valve block 41, and similarly, when the oil flows in from the oil return port T of the hydraulic lock valve block 41, oil supply from the oil return port T of the hydraulic lock valve block 41 to the second working oil port B can be realized, and oil return is performed from the first working oil port a to the oil inlet P of the hydraulic lock valve block 41.
As an embodiment of the invention, the sequence valve block 3 comprises a sequence valve block 31, see fig. 5, the sequence valve block 31 comprising a first sequence valve 311 and a second sequence valve 312,an oil inlet P, an oil return port T and a first working oil port A are respectively drilled on the sequence valve block 311A second working oil port B1And a third working oil port B2And a fourth working oil port A2The second sequence valve 312 is installed on the sequence valve block 31 through screws, and an oil inlet P of the second sequence valve 3121And a fourth working port B of the sequence valve block 312An oil inlet P of the sequence valve block 31 is connected with an internal flow passage of the sequence valve block 31, and a working oil port A of the second sequence valve 3121And a first working port A of the sequence valve block 311Connected by an internal flow passage of the sequence valve block 31, the first sequence valve 311 is mounted on the sequence valve block 31 by a screw, and an oil inlet P of the first sequence valve 3112And a second working port B of the sequence valve block 311An oil return port T of the sequence valve block 31 is connected with an internal flow passage of the sequence valve block 31, and a working oil port A of the first sequence valve 3112Through the hydraulic pipeline and the fourth working port A of the sequence valve block 312Specifically, the first sequence valve 311 and the second sequence valve 312 have the same composition as the first secondary overflow valve group 51j, the second secondary overflow valve group 51k and the third secondary overflow valve group 51l, referring to fig. 6, the first sequence valve 311 and the second sequence valve 312 include a secondary overflow valve block 512, the secondary overflow valve block 512 includes a second overflow valve 5121 and a first check valve 5122, an oil inlet P and a working oil port a are respectively drilled on the secondary overflow valve block 512, the first check valve 5122 is mounted on the secondary overflow valve block 512 through screws, the second overflow valve 5121 is mounted on the secondary overflow valve block 512 through screws, and the working oil port a of the check valve 5122 is mounted on the working oil port a of the second overflow valve block 512 through screws1And a working oil port A of the second overflow valve 51211The working oil port A of the secondary overflow valve block 512 is connected with the inner flow passage on the secondary overflow valve block 512, and the oil inlet P of the first check valve 51221And an oil inlet P of a second overflow valve 51211And an oil inlet P of the secondary overflow valve block 512 is connected with an internal flow passage on the secondary overflow valve block 512.
As an embodiment of the present invention, the operation principle of the sequence valve group 3 is as follows: when oil flows in from the oil inlet P of the sequence valve block 31, the oil is divided into two paths: one way to the second sequence valve 312; the other path passes through a sequence valve blockThe fourth working port B of 312The hydraulic oil flowing to the rodless cavity of the valve hydraulic cylinder 21 flows to the second sequence valve 312, when the pressure of the hydraulic oil flowing to the second sequence valve 312 does not reach the set pressure of the second sequence valve 312, the second sequence valve 312 is closed, the hydraulic oil cannot pass through, only when the hydraulic oil flowing to the rodless cavity of the valve hydraulic cylinder 21 enables the piston rod of the valve hydraulic cylinder 21 to push against the head, the oil pressure in the rodless cavity of the valve hydraulic cylinder 21 is enabled to rise, and then the oil pressure of the second sequence valve 312 rises, when the set pressure of the second sequence valve 312 is reached, the second sequence valve 312 is opened, and the hydraulic oil passes through the second sequence valve 312 and passes through the first working oil port a of the sequence valve block 311Flows into the rodless chamber of the latch cylinder 22 to push out the piston rod of the latch cylinder 22, and the oil flowing out of the rod chamber of the latch cylinder 22 passes through the second working port B of the sequence valve block 311And the oil return port T flows back to the oil tank, the oil flowing out of the rod cavity of the valve hydraulic cylinder 21 finally flows back to the oil tank through the oil return port T of the sequence valve block 31 after passing through the first sequence valve 311, so that the purposes of firstly extending the piston rod of the valve hydraulic cylinder 21 and then extending the piston rod of the latch hydraulic cylinder 22 are realized, and when the oil enters from the oil return port T of the sequence valve block 31 and flows out from the oil inlet P, the piston rod of the latch hydraulic cylinder 22 can be firstly retracted and the piston rod of the valve hydraulic cylinder 21 can be secondly retracted.
The working principle of the turnover type elevator hydraulic system based on the independent control of the load port in the embodiment of the invention is as follows:
the quantitative pump 7 is driven by the motor to suck hydraulic oil from the oil tank 8 and supply the hydraulic oil to the oil supply valve group 5, the hydraulic oil flowing out of the oil supply valve group 5 can be divided into two paths, the hydraulic oil of one branch flows through the hydraulic lock valve group 4 and the sequence valve group 3 to reach the valve hydraulic cylinder 21 and the latch hydraulic cylinder 22, the piston rods of the valve hydraulic cylinder 21 and the latch hydraulic cylinder 22 can extend or retract in sequence, the valve and the latch of the elevator can be opened or closed in sequence, the hydraulic oil of the other branch flows into the overturning hydraulic cylinder 23, the piston rod of the overturning hydraulic cylinder 23 can extend or retract, and the elevator can be overturned; because the operation site is complicated, electric wires can not appear around the elevator, and only hydraulic pipelines can be available, the lifting touch spring cylinder 24, the induction latch spring cylinder 25 and the top drive lowering spring cylinder 26 are respectively used as hydraulic induction sensors, when lifting touch, latch closing and top drive lowering are carried out, plunger rods of the lifting touch spring cylinder 24, the induction latch spring cylinder 25 and the top drive lowering spring cylinder 26 can be forced to contract inwards, the pressure in rodless cavities can be increased, the pressure in the rodless cavities can be transmitted to the oil supply valve group 5, the oil supply valve group 5 converts the pressure into electric signals, and the information is fed back to the controller.
The above examples are only for describing the preferred embodiments of the present invention, and are not intended to limit the scope of the present invention, and various modifications and improvements made to the technical solution of the present invention by those skilled in the art without departing from the spirit of the present invention should fall within the protection scope defined by the claims of the present invention.

Claims (7)

1. The utility model provides a convertible elevator hydraulic system based on load mouth independent control which characterized in that includes:
the oil tank (8) is used for storing hydraulic oil required by the hydraulic system;
a constant delivery pump (7) for providing a constant flow of hydraulic oil to the hydraulic system;
the first overflow valve (6) is used for constant-pressure overflow of the hydraulic system;
the oil supply valve group (5) is used for supplying oil to the hydraulic system and controlling the actuating mechanism to act;
the hydraulic lock valve group (4) is used for sealing an oil way;
the sequence valve group (3) is used for controlling the sequence of extension and retraction of the actuating mechanism;
the actuating mechanism (2) comprises a valve hydraulic cylinder (21), a lock bolt hydraulic cylinder (22), a turnover hydraulic cylinder (23), a lifting touch spring cylinder (24), an induction lock bolt spring cylinder (25) and a top drive lowering spring cylinder (26);
an oil suction port T of the constant delivery pump (7), an oil return port T of the first overflow valve (6), an oil return port T of the oil supply valve group (5) and the oil tank (8) are connected through a hydraulic pipeline, and an oil outlet P of the constant delivery pump (7), an oil inlet P of the oil supply valve group (5) and an oil return port T of the first overflow valve (6) are connected through a hydraulic pipelineThe oil inlets P are connected through a hydraulic pipeline, and a first working oil port A of the oil supply valve group (5)1Is connected with an oil inlet P of the hydraulic lock valve group (4) through a hydraulic pipeline, and a second working oil port B of the oil supply valve group (5)1Is connected with an oil return port T of the hydraulic lock valve group (4) through a hydraulic pipeline, and a third working oil port A of the oil supply valve group (5)2A rodless cavity oil port A of the turning hydraulic cylinder (23) is connected with a hydraulic pipeline, and a fourth working oil port B of the oil supply valve group (5)2A rod cavity oil port B of the turnover hydraulic cylinder (23) is connected through a hydraulic pipeline, and a fifth working oil port A of the oil supply valve group (5)3Is connected with the working oil port A of the lifting contact spring cylinder (24) through a hydraulic pipeline, and the sixth working oil port A of the oil supply valve group (5)4The hydraulic oil inlet is connected with a working oil port A of the induction lock latch spring cylinder (25) through a hydraulic pipeline, and a seventh working oil port A of the oil supply valve group (5)5The hydraulic oil inlet is connected with a working oil port A of the top drive lowering spring cylinder (26) through a hydraulic pipeline; the hydraulic control valve is characterized in that a first working oil port A of the hydraulic lock valve group (4) and an oil inlet P of the sequence valve group (3) are connected through a hydraulic pipeline, a second working oil port B of the hydraulic lock valve group (4) and an oil return port T of the sequence valve group (3) are connected through a hydraulic pipeline, and a first working oil port A of the sequence valve group (3)1A rodless cavity oil port A of the latch hydraulic cylinder (22) is connected with the hydraulic pipeline, and a second working oil port B of the sequence valve group (3)1A rod cavity oil port B of the latch hydraulic cylinder (22) is connected with the hydraulic pipeline, and a third working oil port B of the sequence valve group (3)2Is connected with a rodless cavity oil port A of the valve hydraulic cylinder (21) through a hydraulic pipeline, and a fourth working oil port A of the sequence valve group (3)2And the hydraulic cylinder is connected with a rod cavity oil port B of the valve hydraulic cylinder (21) through a hydraulic pipeline.
2. The turnover type elevator hydraulic system based on load port independent control is characterized in that the oil supply valve group (5) comprises an oil supply integrated valve block (51) which comprises a first load port independent control valve group (51a), a second load port independent control valve group (51b), a pressure sensor and a hydraulic control system of the turnover type elevator based on load port independent control(51c) The hydraulic control system comprises a first pressure reducing valve (51d), a second pressure reducing valve (51e), a first filter (51f), a second filter (51g), a first ball valve (51h), a second ball valve (51i), a first secondary overflow valve (51j), a second secondary overflow valve (51k), a third secondary overflow valve (51l), a first two-position two-way electromagnetic directional valve (51m), a second two-position two-way electromagnetic directional valve (51n), a third two-position two-way electromagnetic directional valve (51P), a first pressure relay (51q), a second pressure relay (51r) and a third pressure relay (51s), wherein an oil inlet P, an oil return port T and a first working oil port A are drilled in an oil supply integrated valve block (51), and a first pressure relay (51q) and a second pressure relay (51r) are respectively drilled in the oil supply integrated valve block (51)1A second working oil port B1And a third working oil port A2And a fourth working oil port B2The fifth working oil port A3And a sixth working oil port A4And a seventh working oil port A5The first ball valve (51h) is installed on the oil supply integrated valve block (51), an oil inlet P of the first ball valve (51h) is connected with an oil inlet P of the oil supply integrated valve block (51) through an internal flow channel of the oil supply integrated valve block (51), the first filter (51f) is installed on the oil supply integrated valve block (51), an oil inlet P of the first filter (51f) is connected with an oil return port T of the first ball valve (51h) through an internal flow channel of the oil supply integrated valve block (51), an oil return port T of the first filter (51f) is connected with an oil inlet P of the first reducing valve (51d) through an internal flow channel of the oil supply integrated valve block (51), an oil return port T of the first reducing valve (51d), an oil inlet P of the pressure sensor (51c), and an oil inlet P, P and P of an oil inlet of the second load port independent control valve group (51b), An oil inlet P of the first load port independent control valve group (51a) and an oil inlet P of the second reducing valve (51e) are connected through an internal flow passage of the oil supply integrated valve block (51), and a first working oil port A of the second load port independent control valve group (51b) is connected with a first working oil port A of the oil supply integrated valve block (51) through an internal flow passage of the oil supply integrated valve block (51)1The second working oil port B of the second load port independent control valve group (51B) passes through the internal flow passage of the oil supply integrated valve block (51) and the second working oil port B of the oil supply integrated valve block (51)1The first working oil port A of the first load port independent control valve group (51a) passes through the internal flow passage of the oil supply integrated valve block (51) and the oil supply setA third working oil port A of the valve forming block (51)2The second working oil port B of the first load port independent control valve group (51a) passes through the internal flow passage of the oil supply integrated valve block (51) and the fourth working oil port B of the oil supply integrated valve block (51)2Link to each other, first two lead to solenoid operated valve (51m), second two lead to solenoid operated valve (51n) and third two lead to solenoid operated valve (51P) and install supply oil integration valve piece (51), just oil inlet P of third two lead to solenoid operated valve (51P) passes through the inside runner of supply oil integration valve piece (51) with oil return opening T of second relief pressure valve (51e) links to each other, oil return opening T of third two lead to solenoid operated valve (51P), oil inlet P of first secondary overflow valves (51j), oil inlet P of third pressure relay (51s), oil inlet P of second two lead to solenoid operated valve (51n) and the fifth work hydraulic fluid port A of supply oil integration valve piece (51)3The internal flow passage of the oil supply integrated valve block (51) is connected, the oil return port T of the second two-position two-way electromagnetic directional valve (51n), the oil inlet P of the second secondary overflow valve group (51k), the oil inlet P of the second pressure relay (51r), the oil inlet P of the first two-position two-way electromagnetic directional valve (51m) and the sixth working oil port A of the oil supply integrated valve block (51)4The oil return port T of the first two-position two-way electromagnetic directional valve (51m), the oil inlet P of the third secondary overflow valve group (51l), the oil inlet P of the first pressure relay (51q) and the seventh working oil port A of the oil supply integrated valve block (51) are connected through the internal flow passage of the oil supply integrated valve block (51)5The internal flow passage through the oil supply integration valve block (51) is connected, the second ball valve (51i) is installed on the oil supply integration valve block (51), the oil return opening T of the second ball valve (51i) is connected with the oil return opening T of the oil supply integration valve block (51) through the internal flow passage of the oil supply integration valve block (51), the second filter (51g) is installed on the oil supply integration valve block (51), the oil return opening T of the second filter (51g) is connected with the oil inlet P of the second ball valve (51i) through the internal flow passage of the oil supply integration valve block (51), the oil inlet P of the second filter (51g), the oil return opening T of the second load opening independent control valve group (51b), the oil return opening T of the first load opening independent control valve group (51a), the oil return opening T of the first secondary overflow valve group (51j), and the second secondary overflow valve groupAnd an oil return port T of the valve group (51k) and an oil return port T of the third secondary overflow valve group (51l) are connected through an internal flow passage of the oil supply integrated valve block (51).
3. The turnover type elevator hydraulic system based on load port independent control as claimed in claim 1, wherein the hydraulic lock valve set (4) comprises a hydraulic lock valve block (41) which comprises a first hydraulic control one-way valve (411) and a second hydraulic control one-way valve (412), an oil inlet P, an oil return port T, a first working oil port A and a second working oil port B are drilled on the hydraulic lock valve block (41), the first hydraulic control one-way valve (411) and the second hydraulic control one-way valve (412) are both installed on the hydraulic lock valve block (41), and the oil inlet P of the second hydraulic control one-way valve (412) is1A control oil port X of the first hydraulic control one-way valve (411)2Is connected with an oil inlet P of the hydraulic lock valve block (41) through an internal flow passage of the hydraulic lock valve block (41), and a working oil port A of the second hydraulic control one-way valve (412)1A first working oil port A of the hydraulic lock valve block (41) is connected with an internal flow passage of the hydraulic lock valve block (41), and an oil inlet P of the first hydraulic control one-way valve (411)2And a control oil port X of a second hydraulic control one-way valve (412)1The oil return port T of the hydraulic lock valve block (41) is connected with the internal flow passage of the hydraulic lock valve block (41), and the working oil port A of the first hydraulic control one-way valve (411)2And the second working oil port B of the hydraulic lock valve block (41) is connected with the internal flow passage of the hydraulic lock valve block (41).
4. The turnover type elevator hydraulic system based on load port independent control as claimed in claim 2, characterized in that the sequence valve set (3) comprises a sequence valve block (31), the sequence valve block (31) comprises a first sequence valve (311) and a second sequence valve (312), and an oil inlet P, an oil return port T and a first working oil port A are drilled on the sequence valve block (31) respectively1A second working oil port B1And a third working oil port B2And a fourth working oil port A2The second sequence valve (312) is arranged on the sequence valve block (31), and an oil inlet P of the second sequence valve (312)1Sequence valve block(31) Fourth working oil port B2The oil inlet P of the sequence valve block (31) is connected with the internal flow passage of the sequence valve block (31), and the working oil port A of the second sequence valve (312)1A first working oil port A connected with the sequence valve block (31)1The first sequence valve (311) is arranged on the sequence valve block (31) and is connected with the internal flow passage of the sequence valve block (31), and an oil inlet P of the first sequence valve (311)2And a second working oil port B of the sequence valve block (31)1Is connected with an oil return port T of the sequence valve block (31) through an internal flow passage of the sequence valve block (31), and a working oil port A of the first sequence valve (311)2A fourth working oil port A of the sequence valve block (31) through a hydraulic pipeline2Are connected.
5. The turnover type elevator hydraulic system based on load port independent control is characterized in that the first load port independent control valve group (51a) and the second load port independent control valve group (51B) are identical in composition and comprise load port independent control valve blocks (511), each load port independent control valve block (511) comprises a first two-position two-way normally open proportional valve (5111), a second two-position two-way normally open proportional valve (5112), a first two-position two-way normally closed proportional valve (5113) and a second two-position two-way normally closed proportional valve (5114), an oil inlet P, an oil return port T, a first working oil port A and a second working oil port B are drilled in each load port independent control valve block (511), and the first two-position two-way normally open proportional valve (5111), the second two-position two-way normally open proportional valve (5112), the first two-position two-way normally closed valve (5113) and the second normally closed proportional valve (5114) are installed in each load port independent control valve (5114) On the block (511), an oil inlet P of the second two-position two-way normally-closed proportional valve (5114)1An oil inlet P of a first two-position two-way normally closed proportional valve (5113)2An oil inlet P of the load port independent control valve block (511) is connected with an internal flow passage of the load port independent control valve block (511), and a working oil port A of a second two-position two-way normally-closed proportional valve (5114)1And a working oil port A of a second two-position two-way normally-open proportional valve (5112)3And a first working oil port A of a load port independent control valve block (511) passes through the load port independent control valve block(511) The internal flow passage of the second two-position two-way normally-closed proportional valve (5114) is connected, and a working oil port A of the second two-position two-way normally-closed proportional valve2And a working oil port A of a first two-position two-way normally open proportional valve (5111)4The second working oil port B of the load port independent control valve block (511) is connected with an internal flow passage of the load port independent control valve block (511), and an oil inlet P of a second two-position two-way normally-open proportional valve (5112)3An oil inlet P of a first two-position two-way normally open proportional valve (5111)4And an oil return port T of the load port independent control valve block (511) is connected through an internal flow passage of the load port independent control valve block (511).
6. The turnover type elevator hydraulic system based on load port independent control as claimed in claim 2, wherein the first secondary overflow valve group (51j), the second secondary overflow valve group (51k) and the third secondary overflow valve group (51l) are the same in composition and each comprise a secondary overflow valve block (512), the secondary overflow valve block (512) comprises a second overflow valve (5121) and a first check valve (5122), an oil inlet P and a working oil port a are drilled on the secondary overflow valve block (512), the first check valve (5122) is installed on the secondary overflow valve block (512), the second overflow valve (5121) is installed on the secondary overflow valve block (512), and the working oil port a of the check valve (5122) is installed on the second overflow valve block (512)1And a working oil port A of a second overflow valve (5121)1The working oil port A of the secondary overflow valve block (512) is connected with the inner flow passage on the secondary overflow valve block (512), and the oil inlet P of the check valve (5122)1And an oil inlet P of a second overflow valve (5121)1And an oil inlet P of the secondary overflow valve block (512) is connected with an internal flow passage on the secondary overflow valve block (512).
7. The turnover elevator hydraulic system based on load port independent control as claimed in claim 4, characterized in that the first sequence valve (311) and the second sequence valve (312) are identical in composition, and the first sequence valve (311) and the second sequence valve (312) are identical in composition with the first secondary overflow valve group (51j), the second secondary overflow valve group (51k) and the third secondary overflow valve group (51 l).
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