CN201554009U - Piston-type double hanging point hydraulic headstock gear - Google Patents
Piston-type double hanging point hydraulic headstock gear Download PDFInfo
- Publication number
- CN201554009U CN201554009U CN2009202537114U CN200920253711U CN201554009U CN 201554009 U CN201554009 U CN 201554009U CN 2009202537114 U CN2009202537114 U CN 2009202537114U CN 200920253711 U CN200920253711 U CN 200920253711U CN 201554009 U CN201554009 U CN 201554009U
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- 239000000725 suspension Substances 0.000 claims description 8
- 239000012530 fluid Substances 0.000 claims description 6
- 239000002828 fuel tank Substances 0.000 claims description 3
- 230000008676 import Effects 0.000 claims description 3
- 230000003134 recirculating effect Effects 0.000 claims description 2
- 230000002194 synthesizing effect Effects 0.000 claims description 2
- 230000001360 synchronised effect Effects 0.000 abstract description 6
- 239000007788 liquid Substances 0.000 abstract 1
- 239000003921 oil Substances 0.000 description 35
- 238000006073 displacement reaction Methods 0.000 description 19
- 230000009471 action Effects 0.000 description 4
- 238000001514 detection method Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000004134 energy conservation Methods 0.000 description 2
- 239000010720 hydraulic oil Substances 0.000 description 2
- 230000008901 benefit Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000002262 irrigation Effects 0.000 description 1
- 238000003973 irrigation Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
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Abstract
The utility model relates to a piston-type double hanging point hydraulic headstock gear which is composed of two piston-type hydraulic cylinders, one set of hydraulic control system and one set of electric control system, wherein the hydraulic control system comprises a balance valve, a bypass oil leakage error correcting valve group consisting of a three-bit four-way electromagnetic change-over valve and two choke valves, a diverting flow collection valve, a three-bit four-way electric liquid proportion change-over valve, an external control order valve, an overflow valve, an electromagnetic overflow valve, an oil return oil filter, an oil pump motor set and the like. The balance valve is adopted for keeping pressure, the piston-type double hanging point hydraulic headstock gear is provided with functions of differentially closing a brake, controlling double pressure of opening and closing the brake, and the like. The electric control system is provided with a detecting and displaying device for brake openness, and a programmable controller PLC connected with the detecting and displaying device, adopts a closed ring synchronous control scheme for coarsely tuning the diverting flow collection valve, and finely tuning the bypass error correcting valve group, and has high synchronous precision. The system has simple structure, convenient operation and excellent reliability.
Description
Technical field
The utility model is established and is related to the hydraulic hoist technical field, the two suspension centre hydraulic hoists of specifically a kind of piston type list.
Background technology
No matter be to administer rivers, urban flood defence, prevention waterlogging, or catchwork irrigation, Hydraulic and Hydro-Power Engineerings such as diversion and power all be unable to do without gate, and the opening and closing of gate must realize with special mechanical device, and headstock gear is exactly to be specifically designed to the special purpose crane tool that opens and closes gate.The quality of headstock gear start-stop performance is directly connected to the reliability that gate opens and closes, and plays critical effect for the safe operation of engineering, and the headstock gear that uses mainly contains winch hoist and hydraulic gate hoist two big classes at present.
The operating principle of hydraulic gate hoist is the hydraulic oil with oil pump output high pressure, and by the road, hydraulic valve bank control enters piston-type hydraulic cylinder, the driven plunger motion is driven gate opening or closed by piston.Hydraulic gate hoist both can produce pulling force upwards, can produce downward thrust again, have operate steadily, control conveniently, hoisting capacity is big, size is little, in light weight, the advantage that can simplify the hydraulic architecture structure.Along with the Hydraulic and Hydro-Power Engineering scale constantly to large-scale, super-huge development, many occasions, the hydraulic gate hoist scheme has become the irreplaceable unique selection of other machine, is the ideal equipment that regulating gate opens and closes.
The most important indispensable basic function of two suspension centre hydraulic hoists is pressurize, synchronous, speed governing, and is high to the operational reliability requirement of equipment.Present hydraulic hoist adopts the hydraulic control one-way valve pressurize, because gate is very heavy, opens the controlled pressure of one way valve and has relatively high expectations, and the stuck or fault such as creep owing to the undesired gate that causes of fluid-control one-way opening of valves often occurs.In order to reduce the required controlled pressure of open check valve, need to adopt the formula hydraulic control one-way valve that leaks, every piston-type hydraulic cylinder has into, returns, controls, leaks four oil pipes, and pipeline is complicated.The gate speed governing is divided into two groups with four flow speed control valves, finish the speed that the opens and closes speed governing of two piston-type hydraulic cylinders respectively separately, make the speed of two piston-type hydraulic cylinders equal substantially, thus reach preliminary synchronously, be aided with again the bypass draining rectify a deviation realize more synchronous.This control mode has been continued to use for many years, and the speed adjusting confuses with adjusted in concert to be carried out, in case need the change gate open and close speed, just must readjust synchronously, even and this also is the thing that bothers very much for skilled professional.If the adjusted in concert process is made a fault, just may cause gate stuck because of deflection, cause a serious accident.These problems have restricted the lifting of headstock gear performance and reliability, can not satisfy the requirement that improves day by day for gate control function.
Summary of the invention
The purpose of this utility model provides the two suspension centre hydraulic hoists of a kind of piston type, can control the synchronous operation of two piston-type hydraulic cylinders of headstock gear automatically, guarantees that gate steadily opens and closes; With equalizing valve pressurize locking, prevent that gate from gliding because of deadweight when stopping.
The technical solution of the utility model is: the two suspension centre hydraulic hoists of piston type list are by 2 piston-type hydraulic cylinders, hydraulic control system and electrical control system are formed, and hydraulic control system comprises equalizing valve, bypass draining correction valve group, flow divider-combiner, unidirectional flow speed control valve, 3-position 4-way electro-hydraulic reversing valve, external control sequence valve, overflow valve, electromagnetic relief valve, oil return oil filter, Oil pump electrical machinery group etc.2 oil pump outlets are by synthesizing total pressure hydraulic fluid port behind the one way valve, respectively with the 3-position 4-way electro-hydraulic reversing valve, electromagnetic relief valve, the external control sequence valve connects, an outlet of 3-position 4-way electro-hydraulic reversing valve is connected with the flow divider-combiner import with two unidirectional flow speed control valve series connection backs, two outlets of flow divider-combiner are connected separately and are connected with the rod chamber of 2 piston-type hydraulic cylinders respectively behind the equalizing valve again, 2 piston-type hydraulic cylinder rodless cavity outlets unite two into one, another outlet with the 3-position 4-way electro-hydraulic reversing valve, the external control sequence valve, overflow valve connects, the external control sequence valve, the outlet parallel connection of overflow valve and electromagnetic relief valve becomes total oil return opening, is connected with fuel tank through the oil return oil filter.Bypass draining correction valve group is made up of 3-position 4-way solenoid operated directional valve and 2 choke valves, 2 outlets of 3-position 4-way solenoid operated directional valve respectively are in series with 1 choke valve, the other end of choke valve is in parallel with 2 outlets of flow divider-combiner respectively, the oil recirculating port connecting tank of 3-position 4-way solenoid operated directional valve.
Electrical control system has detection, the display unit of gatage and is attached thereto the programmable controller PLC that connects, the gatage checkout gear has 2 displacement transducers, be separately positioned on 2 piston-type hydraulic cylinders, displacement transducer detects the piston-type hydraulic cylinder actual displacement and is defeated by programmable controller PLC, programmable controller PLC compares 2 piston-type hydraulic cylinder actual displacements and setting displacement, the action of control 3-position 4-way electro-hydraulic reversing valve realizes that the commutation of piston-type hydraulic cylinder and location stop control.Relatively 2 piston-type hydraulic cylinder actual displacements of programmable controller PLC simultaneously, according to the action of actual displacement Deviation Control bypass draining correction valve group, realize automatic deviation correction, and with the actual displacement of piston-type hydraulic cylinder, set actual aperture that displacement and offset deviation be scaled gate, set aperture and deflection, show through display in good time.
The utility model adopts the equalizing valve pressurize, prevents that gate from gliding because of deadweight, and oil circuit is simple, and control is reliable.Only advance after the pressurize of employing equalizing valve, return two oil pipes, compare with four oil pipes of one way valve pressurize, oil circuit is greatly simplified, and has both reduced cost, has reduced again because the equipment fault risk that pipe breakage may cause.It is synchronously thick to adopt flow divider-combiner to realize, is aided with bypass draining correction valve group and realizes accurately synchronously the synchronization accuracy height.Owing to realize automatically by flow divider-combiner synchronously that slightly do not need manual intervention, Synchronization Control and speed governing are separate, do not disturb mutually, and be convenient and reliable.Two kinds of operating modes of gate opening/closing adopt double pressure-controlled system, adopt the external control sequence valve to form differential circuit during closing gate, and available less oil pump flow realizes Rapid door closer, can effectively reduce power of motor, energy conservation.Compare with headstock gear in the past, system is simple, easy and simple to handle, good reliability.
Description of drawings
Fig. 1 is the two suspension centre hydraulic system of hydraulic headstock gear schematic diagrams of piston type of the present utility model.
Among the figure: 1. (1.1 and 1.2) displacement transducer, 2. (2.1 and 2.2) piston-type hydraulic cylinder, 3. (3.1 and 3.2) equalizing valve, 4. (4.1 and 4.2) choke valve, 5. 3-position 4-way solenoid operated directional valve, 6. flow divider-combiner, 7. (7.1 and 7.2) unidirectional flow speed control valve, 8. 3-position 4-way electro-hydraulic reversing valve, 9. external control sequence valve, 10. overflow valve, 11. electromagnetic relief valves, 12. the oil return oil filter, 13. (13.1 and 13.2) Oil pump electrical machinery group.
The specific embodiment
The two suspension centre hydraulic hoists of a kind of piston type of the present utility model as shown in Figure 1 are by 2 piston-type hydraulic cylinders, 1 cover hydraulic control system and 1 cover electrical control system are formed, and hydraulic control system comprises equalizing valve 3, forms bypass draining correction valve group, flow divider-combiner 6, unidirectional flow speed control valve 7,3-position 4-way electro-hydraulic reversing valve 8, external control sequence valve 9, overflow valve 10, electromagnetic relief valve 11, oil return oil filter 12, Oil pump electrical machinery group 13 etc. by 3-position 4-way solenoid operated directional valve 5 and 2 choke valves 4.2 oil pumps 13.1,13.2 outlet synthesize total pressure hydraulic fluid port after by one way valve, respectively with 3-position 4-way electro-hydraulic reversing valve 8, electromagnetic relief valve 11, external control sequence valve 9 connects, an outlet of 3-position 4-way electro-hydraulic reversing valve 8 is connected with flow divider-combiner 6 imports with two unidirectional flow speed control valve 7 series connection backs, two outlets of flow divider-combiner 6 are connected separately and are connected with the rod chamber of 2 piston-type hydraulic cylinders respectively behind the equalizing valve 3 again, 2 piston-type hydraulic cylinder rodless cavity outlets unite two into one, another outlet with 3-position 4-way electro-hydraulic reversing valve 8, external control sequence valve 9, overflow valve 10 connects, external control sequence valve 9, overflow valve 10 is in parallel with the outlet of electromagnetic relief valve 11 to become total oil return opening, is connected with fuel tank through oil return oil filter 12.Bypass draining correction valve group is made up of 3-position 4-way solenoid operated directional valve 5 and 2 choke valves 4.1,4.2,2 outlets of 3-position 4-way solenoid operated directional valve 5 respectively are in series with 1 choke valve 4, the other end of choke valve 4 is in parallel with 2 outlets of flow divider-combiner 3 respectively, the hydraulic fluid port connected tank of 3-position 4-way solenoid operated directional valve 5.
The effect of Oil pump electrical machinery group 13 is for system provides hydraulic oil stream, work of two Oil pump electrical machinery groups, and another is as standby.When the electromagnet 3YA of programmable controller PLC control 3-position 4-way electro-hydraulic reversing valve 8 switches on, the position work of valve 8 left side, pressure oil is through position, valve 8 left side, by unidirectional flow speed control valve 7.1,7.2, enter the rod chamber of piston-type hydraulic cylinder 2.1,2.2 after being divided into two by flow divider-combiner 6 respectively through equalizing valve 3.1,3.2, piston rises, and drives gate opening.Opening the maximum working pressure (MWP) of door is set up by electromagnetic relief valve 11.Because the operating pressure during gate opening is greater than the opening pressure of sequence valve 9, valve 9 is opened, and the fluid of piston-type hydraulic cylinder epicoele is crossed oil return oil filter 12 oil sump tanks behind valve 9.
When the electromagnet 2YA of programmable controller PLC control 3-position 4-way electro-hydraulic reversing valve 8 gets when electric, valve 8 right position work, pressure oil enters piston-type hydraulic cylinder 2.1,2.2 epicoeles piston is descended through valve 8 right position, drive closing gate, close the maximum working pressure (MWP) of door and set up by overflow valve 10.Because the operating pressure during closing gate is less than the opening pressure of sequence valve 9, valve 9 cuts out, the fluid of two piston-type hydraulic cylinder cavity of resorptions is united two into one by valve 6 by valve 3.1,3.2 backs, by valve 7.1,7.2, oil sump tank not behind the right position of 3-position 4-way electro-hydraulic reversing valve 8, but enter piston-type hydraulic cylinder 2.1,2.2 epicoeles, form differential circuit.This connected mode can realize Rapid door closer with the flow of less oil pump, can effectively reduce power of motor, energy conservation.
Unidirectional flow speed control valve 7 has flow control function, and flow speed control valve 7.1 control oil return flows form the meter out speed governing, regulate a speed of closing.Flow speed control valve 7.2 control oil-feed flows form the in-line throttle grverning, regulate a speed that opens.The flow of piston-type hydraulic cylinder rate request is satisfied in the output of unidirectional flow speed control valve, enters flow divider-combiner 6 backs and is divided into two-way in 1: 1 ratio, enters two piston-type hydraulic cylinders 2 respectively, realizes the synchronously thick of two piston-type hydraulic cylinders.Slightly realize automatically by flow divider-combiner 6 synchronously, irrelevant with speed governing, do not need manual intervention.Because flow divider-combiner has the load compensation function, even also can keep good synchronization performance under the unfavorable operating mode of unbalance loading, this has just alleviated the pressure to back bypass draining correction valve group.Finally can reach the higher synchronous precision.
Electrical control system has detection, the display unit of gatage and is attached thereto the programmable controller PLC that connects, the gatage checkout gear has 2 displacement transducers 1, be separately positioned on 2 piston-type hydraulic cylinders 2, programmable controller PLC is defeated by in the actual displacement that displacement transducer 2 detects piston-type hydraulic cylinder 2, programmable controller PLC compares 2 piston-type hydraulic cylinder actual displacements and setting displacement, 8 actions of control 3-position 4-way electro-hydraulic reversing valve realize that the commutation of piston-type hydraulic cylinder and location stop control.Relatively 2 piston-type hydraulic cylinder actual displacements of programmable controller PLC simultaneously, according to the action of actual displacement Deviation Control bypass draining correction valve group, realize automatic deviation correction, and with the actual displacement of piston-type hydraulic cylinder, set actual aperture that displacement and offset deviation be scaled gate, set aperture and deflection, show through display in good time.
Claims (1)
1. two suspension centre hydraulic hoists of a piston type, comprise 2 piston-type hydraulic cylinders, hydraulic control system and electrical control system is characterized in that: hydraulic control system comprises equalizing valve, bypass draining correction valve group, flow divider-combiner, unidirectional flow speed control valve, 3-position 4-way electro-hydraulic reversing valve, external control sequence valve, overflow valve, electromagnetic relief valve, oil return oil filter, Oil pump electrical machinery group; 2 oil pump outlets are by synthesizing total pressure hydraulic fluid port behind the one way valve, respectively with the 3-position 4-way electro-hydraulic reversing valve, electromagnetic relief valve, the external control sequence valve connects, an outlet of 3-position 4-way electro-hydraulic reversing valve is connected with the flow divider-combiner import with two unidirectional flow speed control valve series connection backs, two outlets of flow divider-combiner are connected separately and are connected with the rod chamber of 2 piston-type hydraulic cylinders respectively behind the equalizing valve again, 2 piston-type hydraulic cylinder rodless cavity outlets unite two into one, another outlet with the 3-position 4-way electro-hydraulic reversing valve, the external control sequence valve, overflow valve connects, the external control sequence valve, overflow valve is in parallel with the outlet of electromagnetic relief valve to become total oil return opening, is connected with fuel tank through the oil return oil filter; Bypass draining correction valve group is made up of 3-position 4-way solenoid operated directional valve and 2 choke valves, 2 outlets of 3-position 4-way solenoid operated directional valve respectively are in series with 1 choke valve, the other end of choke valve is in parallel with 2 outlets of flow divider-combiner respectively, the oil recirculating port connecting tank of 3-position 4-way solenoid operated directional valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009202537114U CN201554009U (en) | 2009-11-17 | 2009-11-17 | Piston-type double hanging point hydraulic headstock gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009202537114U CN201554009U (en) | 2009-11-17 | 2009-11-17 | Piston-type double hanging point hydraulic headstock gear |
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| Publication Number | Publication Date |
|---|---|
| CN201554009U true CN201554009U (en) | 2010-08-18 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009202537114U Expired - Fee Related CN201554009U (en) | 2009-11-17 | 2009-11-17 | Piston-type double hanging point hydraulic headstock gear |
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| CN (1) | CN201554009U (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102001039A (en) * | 2010-10-19 | 2011-04-06 | 昆山昆江数控机床有限公司 | Machine tool spindle reciprocating motion control system |
| 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 |
| CN102797719A (en) * | 2011-05-26 | 2012-11-28 | 邵阳维克液压股份有限公司 | Synchronous valve block of surface discharge outlet gate hydraulic hoist |
| CN105065353A (en) * | 2015-09-06 | 2015-11-18 | 常州液压成套设备厂有限公司 | Hydraulic hoist capable of emergently closing door |
| CN105604991A (en) * | 2016-01-21 | 2016-05-25 | 燕山大学 | Cabin door opening and closing hydraulic control system of underwater vehicle |
| CN106704281A (en) * | 2017-01-24 | 2017-05-24 | 长沙通石达机械制造有限公司 | Combined rope sawing machine |
| CN107366650A (en) * | 2017-08-30 | 2017-11-21 | 常州液压成套设备厂有限公司 | Spillway hydraulic hoist system with emergency function |
| CN111022434A (en) * | 2019-12-28 | 2020-04-17 | 武汉承天液压机电设备有限公司 | Mixed pressure hydraulic test platform |
| CN111577678A (en) * | 2020-05-26 | 2020-08-25 | 中国铁建重工集团股份有限公司 | Hydraulic system of heading machine and heading machine |
-
2009
- 2009-11-17 CN CN2009202537114U patent/CN201554009U/en not_active Expired - Fee Related
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102001039A (en) * | 2010-10-19 | 2011-04-06 | 昆山昆江数控机床有限公司 | Machine tool spindle reciprocating motion control system |
| 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 |
| CN102797719A (en) * | 2011-05-26 | 2012-11-28 | 邵阳维克液压股份有限公司 | Synchronous valve block of surface discharge outlet gate hydraulic hoist |
| CN105065353A (en) * | 2015-09-06 | 2015-11-18 | 常州液压成套设备厂有限公司 | Hydraulic hoist capable of emergently closing door |
| CN105604991A (en) * | 2016-01-21 | 2016-05-25 | 燕山大学 | Cabin door opening and closing hydraulic control system of underwater vehicle |
| CN106704281A (en) * | 2017-01-24 | 2017-05-24 | 长沙通石达机械制造有限公司 | Combined rope sawing machine |
| CN106704281B (en) * | 2017-01-24 | 2018-09-21 | 长沙通石达机械制造有限公司 | Combined rope saw |
| CN107366650A (en) * | 2017-08-30 | 2017-11-21 | 常州液压成套设备厂有限公司 | Spillway hydraulic hoist system with emergency function |
| CN111022434A (en) * | 2019-12-28 | 2020-04-17 | 武汉承天液压机电设备有限公司 | Mixed pressure hydraulic test platform |
| CN111577678A (en) * | 2020-05-26 | 2020-08-25 | 中国铁建重工集团股份有限公司 | Hydraulic system of heading machine and heading machine |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20100818 Termination date: 20121117 |