CN201962652U - Hydraulic system of diagonal tension door type hoist trolley driving mechanism - Google Patents
Hydraulic system of diagonal tension door type hoist trolley driving mechanism Download PDFInfo
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- CN201962652U CN201962652U CN2011200298506U CN201120029850U CN201962652U CN 201962652 U CN201962652 U CN 201962652U CN 2011200298506 U CN2011200298506 U CN 2011200298506U CN 201120029850 U CN201120029850 U CN 201120029850U CN 201962652 U CN201962652 U CN 201962652U
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Abstract
The utility model discloses a hydraulic system of a diagonal tension door type hoist trolley driving mechanism, which comprises two hydraulic cylinders, a hydraulic control unit which controls the hydraulic cylinders respectively, a hydraulic power unit, an oil box and a sensor; the hydraulic control unit mainly consists of two sets of hydraulic circuits which are respectively used for controlling the two hydraulic cylinders to run; each hydraulic circuit comprises a throttling and speed-adjusting circuit, a bypass correcting circuit, a differential circuit and a cylinder side locking circuit; the hydraulic power unit mainly consists of two duplex-blade pump electric machine sets and two multilevel pressure-adjusting control valve sets; the rod cavity and the rod-free cavity of each hydraulic cylinder are respectively communicated with the output end of the hydraulic power unit by the cylinder side locking circuit, the differential circuit, the bypass correcting circuit and the throttling and speed-adjusting circuit in the hydraulic control unit; and the hydraulic oil is absorbed by the duplex-blade pump electric machine sets from the oil box to adjust the pressure of the system by the multilevel pressure-adjusting control valve sets, is input into the hydraulic control unit, and flowed into the hydraulic cylinders to drive a trolley to walk.
Description
Technical field
The utility model relates to gate-type and the platform hoist dolly driving mechanism hydraulic system in the Hydraulic and Hydro-Power Engineering building, especially relates to the hydraulic system of oblique sliding door type headstock gear dolly driving mechanism.
Background technology
Hydraulic and Hydro-Power Engineering partial building gate slot is arranged and is had gradient, when adopting gate-type to move headstock gear keying gate, lifting mechanism wire rope on the main carriage becomes fixed angle with the vertical ground direction, and remain unchanged and to guarantee that gate normally opens and closes along gate slot, and the horizontal component that is produced in opening process traction door machine main carriage moves along track cross level, causes gate normally to open and close.Adopt oblique sliding door machine, by the Driven by Hydraulic Cylinder dolly along the track cross level displacement, and utilize the dynamic balance of holding of hydraulic cylinder to open the horizontal component that is produced in the process, keep dolly and be in and tiltedly draw the position, to guarantee that gate is along the normal a kind of solution well of can yet be regarded as that opens and closes of gate slot.But take two Driven by Hydraulic Cylinder owing to dolly moves along track cross level, and travel distance is generally more than five meters; Therefore, the synchronization accuracy during two hydraulic cylinder works is the prerequisite that guarantees the dolly operate as normal.It is more to influence two hydraulic cylinder synchronous factors, such as hydraulic-driven such as hydraulic system, hydraulic cylinder self because internal causes such as manufacturing, installation cause the twin-tub synchronization discrepancy, and for example the fluid pressure line from the pumping plant to the hydraulic cylinder is owing to may there are differences when laying the linear loss of two lateral lines is differed, also cause the frictional resistance of twin-tub to differ or the like, occur synchronism deviation in the time of all will causing two hydraulic cylinder works as difference owing to two hydraulic cylinders processing and assembling.How to address the above problem, be the problem that those skilled in the art study always, but yet there are no the report of all relevant this respects.
Summary of the invention
The utility model purpose is to provide a kind of hydraulic system of oblique sliding door type headstock gear dolly driving mechanism, not only realize opening dolly in the process and be in all the time and tiltedly draw position, dolly parking antiskid, satisfy dolly in horizontal handling with open speed and the pressure requirement that door tiltedly draws hydraulic cylinder rod chamber and rodless cavity under the operating mode, and also can control two synchronization accuracies that drive hydraulic cylinders.
For achieving the above object, the utility model can be taked following technical proposals:
The hydraulic control system that oblique sliding door type headstock gear dolly described in the utility model drives, it comprises two hydraulic cylinders, controls hydraulic control unit, hydraulic power unit, fuel tank and the sensor of hydraulic cylinder respectively; Described hydraulic control unit mainly is made up of two groups of hydraulic circuits of controlling two hydraulic cylinder actions respectively; Described hydraulic circuit comprises throttling speed control circuit, bypass correction loop, differential circuit, the other locking of cylinder loop; Described hydraulic power unit mainly is made up of two pair vane pump group of motors and two multi-stage pressure regulating control valve groups; Described sensor comprises pressure sensor, flow transmitter, temperature pick up, liquid level sensor; The rod chamber of each hydraulic cylinder, the rodless cavity other locking of the cylinder in hydraulic control unit loop, differential circuit, bypass correction loop, throttling speed control circuit respectively are connected with the output of hydraulic power unit; Described pair vane pump group of motors sucks hydraulic oil from fuel tank and sets up system pressure through multi-stage pressure regulating control valve group, and the input hydraulic pressure control module enters hydraulic cylinder then, the driving trolley walking.
The other locking of the cylinder of described every hydraulic cylinder loop is formed by the overflow valve of two hydraulic control one-way valves that are connected with hydraulic cylinder rod chamber, rodless cavity respectively and protection cylinder pressure;
Described differential circuit comprises one-way throttle valve and electro-hydraulic reversing valve and the solenoid operated directional valve composition that is connected with hydraulic cylinder rod chamber oil circuit; An outlet of described electro-hydraulic reversing valve is connected with hydraulic cylinder rodless cavity oil circuit, another outlet is connected with described one-way throttle valve, the commutation function of described solenoid operated directional valve control electro-hydraulic reversing valve, import of electro-hydraulic reversing valve links to each other with the oil return oil filter on the fuel tank, and another import is connected with the outlet of one group of flow control valve group of described throttling speed control circuit;
Throttling speed control circuit comprises an electro-hydraulic reversing valve, one group of flow control valve piece; Described flow control valve piece is made up of two different flow control valves of large and small latus rectum that are in parallel; Described big latus rectum flow-control valve inlet communicates with an outlet of described electro-hydraulic reversing valve, and little latus rectum flow-control valve inlet and electro-hydraulic reversing valve inlet communicate with the outlet of multi-stage pressure regulating control valve group jointly; Electro-hydraulic reversing valve is controlled the big latus rectum flow control valve of two hydraulic cylinders simultaneously;
Described multi-stage pressure regulating control valve group comprises electromagnetic relief valve, 3-position 4-way solenoid operated directional valve, superposing type overflow valve, control cover plate and overflow cartridge valve; Described electromagnetic relief valve communicates with the mass flow blade pump discharge; The two-stage pressure-regulating valve group that described 3-position 4-way solenoid operated directional valve, superposing type overflow valve, control cover plate and overflow cartridge valve are formed communicates with the outlet of low discharge vane pump;
Described pair vane pump group of motors is made up of duplex pump and drive motors that two different single-stage blade pump groups of large and small flow constitute;
Described bypass correction loop comprises one-way throttle valve and solenoid operated directional valve.
The utility model advantage is to be connected on the solenoid operated directional valve in the described bypass correction loop from the other respectively oil circuit of drawing of throttling speed control circuit, and its oil return line is to fuel tank.Detect the operation of two hydraulic cylinders when deviation occurring when being arranged on two stroke measuring devices on the hydraulic cylinder, feed back to PLC and send instruction, according to deviation signal electromagnetic switch valve events, make hydraulic cylinder bypass draining oil sump tank in advance, reach the purpose of adjusting two cylinder displacement synchronous.When the offset deviation of two hydraulic cylinders reached setting allowed band value, the solenoid operated directional valve dead electricity resetted, and stops draining.PLC is by comparing in real time two hydraulic cylinder travel measurement mechanisms → feedback signal → send instruction, solenoid operated directional valve continuous, dead electricity, reach the purpose of adjusting two hydraulic cylinder synchronous.Simultaneously, the utility model is open loop control, compare with the closed-loop control system of employing ratio, the control of servo-hydraulic element more economical, simple, lower to the class of pollution requirement of fluid, be convenient to the later stage maintenance, and satisfy the requirement of trolley travelling synchronization accuracy.
Description of drawings
Fig. 1 is a hydraulic control system theory diagram described in the utility model.
Fig. 2 is a hydraulic control system schematic diagram described in the utility model.
The specific embodiment
As shown in Figure 1, 2, the hydraulic control system that oblique sliding door type headstock gear dolly described in the utility model drives, it comprises two hydraulic cylinders 1,2, controls hydraulic control unit, hydraulic power unit, fuel tank 9 and the sensor of hydraulic cylinder 1,2 respectively; Described hydraulic control unit is made up of two groups of hydraulic circuits of controlling hydraulic cylinder 1,2 actions respectively; Described hydraulic control unit comprises throttling speed control circuit 5, bypass correction loop 7, differential circuit 6, the other locking of cylinder loop 8; Described hydraulic power unit is made up of two pair vane pump group of motors 3 and two two-stage pressure-regulating control valve groups 4; Described sensor comprises pressure sensor, flow transmitter, temperature pick up, liquid level sensor; The rod chamber of each hydraulic cylinder, the rodless cavity other locking of the cylinder in hydraulic control unit loop 8, differential circuit 6, bypass correction loop 7, throttling speed control circuit 5 respectively are connected with the output of hydraulic power unit; Described pair vane pump group of motors 3 sucks hydraulic oil from fuel tank 9 and sets up system pressure through multi-stage pressure regulating control valve group 4, and the input hydraulic pressure control module enters hydraulic cylinder then, the driving trolley walking.
The other locking of the cylinder of described every hydraulic cylinder 1,2 loop 8 is formed by the overflow valve 11 of two hydraulic control one-way valves 10 that are connected with hydraulic cylinder 1,2 rod chambers, rodless cavity respectively and protection hydraulic cylinder 1,2 pressure.Realize tiltedly drawing and open an operating mode hydraulic cylinder and hold dolly and keep tiltedly drawing position functions, realize when dolly stops simultaneously anchoring, lock function preventing slippage.
Described differential circuit 6 is made up of the one-way throttle valve 12 that is connected with hydraulic cylinder 1,2 rod chamber oil circuits and electro-hydraulic reversing valve 13 and solenoid operated directional valve; An outlet of described electro-hydraulic reversing valve 13 is connected with hydraulic cylinder 1,2 rodless cavity oil circuits, another outlet is connected with described one-way throttle valve 12, the commutation function of described solenoid operated directional valve control electro-hydraulic reversing valve 13, import of electro-hydraulic reversing valve 13 links to each other with the oil return oil filter 14 on the fuel tank 9, and another import is connected with the outlet of one group of flow control valve group of described throttling speed control circuit 5.Solve hydraulic cylinder 1,2 rod chambers, rodless cavity because area difference causes hydraulic cylinder piston rod to stretch out with retraction speed and differs bigger problem, make that dolly advances, astern speed is approaching.
Described throttling speed control circuit 5 comprises an electro-hydraulic reversing valve 15, one group of flow control valve piece 16; Described flow control valve piece 16 is made up of two different flow control valves of large and small latus rectum that are in parallel; Described big latus rectum flow-control valve inlet communicates with an outlet of described electro-hydraulic reversing valve 15, and little latus rectum flow-control valve inlet and electro-hydraulic reversing valve 15 inlets communicate with the outlet of multi-stage pressure regulating control valve group 4 jointly; Electro-hydraulic reversing valve 15 is controlled the big latus rectum flow control valve of two hydraulic cylinders 1,2 simultaneously.With pair vane pump group of motors 3 compound actions, solve oblique sliding door machine multiple rate request under various operating modes, hydraulic system realizes 5-10 speed-regulating function on a large scale doubly.
Described two-stage pressure-regulating control valve group 4 comprises electromagnetic relief valve 16,3-position 4-way solenoid operated directional valve 17, superposing type overflow valve 18, control cover plate and overflow cartridge valve 19; Described electromagnetic relief valve 16 communicates with the mass flow blade pump discharge, sets up its pressure by designing requirement; The two-stage pressure-regulating valve group that described 3-position 4-way solenoid operated directional valve 17, superposing type overflow valve 18, control cover plate and overflow cartridge valve 19 are formed communicates with the outlet of low discharge vane pump, sets up its pressure by designing requirement.Realize the setting requirement of a plurality of force value of hydraulic cylinder 1,2 rod chambers, rodless cavity under the various operating modes.
Described pair vane pump group of motors 3 is made up of duplex pump and drive motors that two different single-stage blade pump groups of large and small flow constitute, in order to obtain multiple flow, adapts to the requirement of hydraulic cylinder friction speed.
Described bypass correction loop 7 comprises one-way throttle valve and solenoid operated directional valve, and when two hydraulic cylinders, 1,2 displacement difference exceed setting value, PLC sends instruction, electromagnetic switch valve events, the fireballing hydraulic cylinder oil sump tank 9 of draining the oil.
Oblique sliding door machine trolley travelling operating mode is divided into tiltedly draws operating mode and handling operating mode, is summarized as follows:
Tiltedly draw operating mode: a door machine dolly drives to and opens oblique pull-up beginning of a door position, and the main hoisting mechanism on the dolly starts hook down, and pull bar tangles the gate suspender, and dolly retreats, and with putting of the main hoisting drum maintenance synchronizing speed of restricting.Open door when tiltedly drawing the position when arrival, hydraulic cylinder displacement transducer output signal is uploaded PLC, and PLC sends control instruction, and dolly stops, hydraulic cylinder self locking.The dolly driving mechanism is finished and is tiltedly drawn operation condition in place.Main hoisting mechanism on the dolly starts, and the reel lay winding wire ropes reclaims, and at this moment hydraulic cylinder is held or spur dolly and remains on to open and tiltedly draw the position, and when gate is finished breakdown action, the dolly driving mechanism is promptly finished main carriage and tiltedly drawn and open an operating mode.
The handling operating mode: the handling operating mode of dolly driving mechanism be exactly main hoisting mechanism on the dolly hanging orbiting under weight or the empty hook-shaped attitude, must reach certain speed of service, to enhance productivity.Since tiltedly the sliding door machine have handling walking operating mode, tiltedly draw walking operating mode in place, tiltedly draw and open an operating mode.The handling of must walking at a high speed of corresponding dolly; Must be consistent with the rope speed of putting of main hoisting drum on the dolly again, steadily put rope; Also have when opening hydraulic cylinder to hold dolly and keep tiltedly drawing the position, so that gate is opened along oblique door groove.Therefore hydraulic system need have 5～10 times of speed-regulating functions on a large scale.Simultaneously, under every kind of operating mode hydraulic cylinder advance, the pressure difference of corresponding hydraulic cylinder rod chamber, rodless cavity when retreating.In hydraulic system, take the control mode of setting pressure respectively, promptly multi-stage pressure regulating adapts to corresponding working condition requirement.For preventing that track grade, wind load or other external force from causing a machine dolly slippage, hydraulic system must have anchoring, lock function.
Claims (2)
1. the hydraulic system of an oblique sliding door type headstock gear dolly driving mechanism, it comprises two hydraulic cylinders (1,2), controls hydraulic control unit, hydraulic power unit, fuel tank (9) and the sensor of hydraulic cylinder (1,2) respectively; It is characterized in that: described hydraulic control unit mainly is made up of two groups of hydraulic circuits of controlling hydraulic cylinder (1,2) action respectively; Described hydraulic circuit comprises throttling speed control circuit (5), bypass correction loop (7), differential circuit (6), the other locking of cylinder loop (8); Described hydraulic power unit mainly is made up of two pair vane pump group of motors (3) and two multi-stage pressure regulating control valve groups (4); Described sensor comprises pressure sensor, flow transmitter, temperature pick up, liquid level sensor; The rod chamber of each hydraulic cylinder (1,2), the rodless cavity other locking of the cylinder in hydraulic control unit loop (8), differential circuit (6), bypass correction loop (7), throttling speed control circuit (5) respectively are connected with the output of hydraulic power unit; Described pair vane pump group of motors (3) sucks hydraulic oil from fuel tank (9) and sets up system pressure through multi-stage pressure regulating control valve group (4), and the input hydraulic pressure control module enters hydraulic cylinder then, the driving trolley walking.
2. according to the hydraulic system of the described oblique sliding door type headstock gear dolly driving mechanism of claim 1, it is characterized in that: the cylinder of described every hydraulic cylinder (1,2) other locking loop (8) is formed by the overflow valve (11) of two hydraulic control one-way valves (10) that are connected with hydraulic cylinder (1,2) rod chamber, rodless cavity respectively and protection hydraulic cylinder (1,2) pressure;
Described differential circuit (6) comprises one-way throttle valve (12) and electro-hydraulic reversing valve (13) and the solenoid operated directional valve composition that is connected with hydraulic cylinder (1,2) rod chamber oil circuit; An outlet of described electro-hydraulic reversing valve (13) is connected with hydraulic cylinder (1,2) rodless cavity oil circuit, another outlet is connected with described one-way throttle valve (12), the commutation function of described solenoid operated directional valve control electro-hydraulic reversing valve (13), import of electro-hydraulic reversing valve (13) links to each other with the oil return oil filter (14) on the fuel tank (9), and another import is connected with the outlet of one group of flow control valve group of described throttling speed control circuit (5);
Throttling speed control circuit (5) comprises an electro-hydraulic reversing valve (15), one group of flow control valve piece (16); Described flow control valve piece (16) is made up of two different flow control valves of large and small latus rectum that are in parallel; Described big latus rectum flow-control valve inlet communicates with an outlet of described electro-hydraulic reversing valve (15), and little latus rectum flow-control valve inlet and electro-hydraulic reversing valve (15) inlet communicate with the outlet of multi-stage pressure regulating control valve group (4) jointly; Electro-hydraulic reversing valve (15) is controlled the big latus rectum flow control valve of two hydraulic cylinders (1,2) simultaneously;
Described multi-stage pressure regulating control valve group (4) comprises electromagnetic relief valve (16), 3-position 4-way solenoid operated directional valve (17), superposing type overflow valve (18), control cover plate and overflow cartridge valve (19); Described electromagnetic relief valve (16) communicates with the mass flow blade pump discharge; The two-stage pressure-regulating valve group that described 3-position 4-way solenoid operated directional valve (17), superposing type overflow valve (18), control cover plate and overflow cartridge valve (19) are formed communicates with the outlet of low discharge vane pump;
Described pair vane pump group of motors (3) is made up of duplex pump and drive motors that two different single-stage blade pump groups of large and small flow constitute;
Described bypass correction loop (7) comprises one-way throttle valve and solenoid operated directional valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011200298506U CN201962652U (en) | 2011-01-28 | 2011-01-28 | Hydraulic system of diagonal tension door type hoist trolley driving mechanism |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011200298506U CN201962652U (en) | 2011-01-28 | 2011-01-28 | Hydraulic system of diagonal tension door type hoist trolley driving mechanism |
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| CN201962652U true CN201962652U (en) | 2011-09-07 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011200298506U Expired - Lifetime CN201962652U (en) | 2011-01-28 | 2011-01-28 | Hydraulic system of diagonal tension door type hoist trolley driving mechanism |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102155007A (en) * | 2011-01-28 | 2011-08-17 | 黄河勘测规划设计有限公司 | Hydraulic system for trolley driving mechanism of inclined sliding door hoist |
| CN102913498A (en) * | 2012-10-18 | 2013-02-06 | 温州市森泰环保设备有限公司 | Energy-saving device for hydraulic plunger pump of pressure filter |
-
2011
- 2011-01-28 CN CN2011200298506U patent/CN201962652U/en not_active Expired - Lifetime
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102155007A (en) * | 2011-01-28 | 2011-08-17 | 黄河勘测规划设计有限公司 | Hydraulic system for trolley driving mechanism of inclined sliding door hoist |
| CN102155007B (en) * | 2011-01-28 | 2012-08-15 | 黄河勘测规划设计有限公司 | Hydraulic system for trolley driving mechanism of inclined sliding door hoist |
| CN102913498A (en) * | 2012-10-18 | 2013-02-06 | 温州市森泰环保设备有限公司 | Energy-saving device for hydraulic plunger pump of pressure filter |
| CN102913498B (en) * | 2012-10-18 | 2017-07-07 | 温州市森泰环保设备有限公司 | A kind of energy saver of filter press hydraulic planger pump |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20110907 Effective date of abandoning: 20120815 |