CN202991683U - Hydraulic multipoint synchronous control system - Google Patents
Hydraulic multipoint synchronous control system Download PDFInfo
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- CN202991683U CN202991683U CN 201220713186 CN201220713186U CN202991683U CN 202991683 U CN202991683 U CN 202991683U CN 201220713186 CN201220713186 CN 201220713186 CN 201220713186 U CN201220713186 U CN 201220713186U CN 202991683 U CN202991683 U CN 202991683U
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Abstract
The utility model provides a hydraulic multipoint synchronous control system. The hydraulic multipoint synchronous control system comprises hydraulic cylinders provided with pistons and piston rods, a hydraulic oil way connected with the hydraulic cylinders, a plunger pump used for supplying hydraulic oil to the hydraulic oil way, a forced oil inlet pump, and a synchronous controller. The forced oil inlet pump is arranged on an oil suction side of the plunger pump and used for forcibly supplying the hydraulic oil into the plunger pump. The synchronous controller is used for confirming strokes of the piston rods are approximately the same. By above technical scheme, multipoint synchronous control of a hydraulic jacking system can be realized. Furthermore, since the forced oil inlet pump is arranged on the oil suction side of the plunger pump, volume efficiency can be obviously improved. In addition, via controlling the plunger pump via analog signals and realizing communication with the synchronous controller via digital signals, signal interference can be obviously reduced.
Description
Technical field
The utility model relates to a kind of hydraulic control system, especially a kind of hydraulic pressure Multipoint synchronous control system.
Background technique
Existing Multipoint synchronous system is mainly used in offshore oil weighing platform, bridge formation etc., and the precision General Requirements is controlled in 10mm, and what adopt is that segmentation loads, the mode of single adjusting, and complex operation, inefficiency, and also precision is not high.
In addition, the traditional oils pumping plant is by the oil suction of plunger type spring negative pressure, and volumetric efficiency is lower.
The model utility content
Control for the Multipoint synchronous of realizing hydraulic jacking system, propose the utility model.
According to an aspect of the present utility model, a kind of hydraulic pressure Multipoint synchronous control system has been proposed, comprising: a plurality of deceleration loading devices, each deceleration loading device has oil hydraulic cylinder, piston and piston rod; Plunger pump; Hydraulic circuit, be connected to the oil hydraulic cylinder of described a plurality of deceleration loading devices, described plunger pump is used for supplying with hydraulic oil to hydraulic circuit, described hydraulic circuit comprises a plurality of hydraulic oil branch roads of drawing from described plunger delivery side of pump, the parallel layout of described a plurality of hydraulic oil branch roads, be provided with an electromagnetic switching valve on each hydraulic oil branch road, one way outlet of described electromagnetic switching valve is communicated with via the hydraulic fluid chamber of piston top in the first branch and oil hydraulic cylinder, and another way outlet of described electromagnetic switching valve is communicated with via the hydraulic fluid chamber below piston in the second branch and oil hydraulic cylinder; A plurality of displacement transducers are for detection of the stroke of the piston rod of the oil hydraulic cylinder of correspondence; An isochronous controller, described a plurality of displacement transducer is communicated by letter with described isochronous controller, and described isochronous controller is controlled at least one in described electromagnetic switching valve based on the piston rod stroke that is detected by displacement transducer, and is roughly the same with the stroke of guaranteeing all piston rods.
Favourable, described isochronous controller control the oil pressure of the hydraulic oil that enters oil hydraulic cylinder, the oil-feed direction that enters the hydraulic oil of oil hydraulic cylinder, hydraulic oil the oil-feed time, enter at least a stroke of regulating corresponding piston rod in the oil mass of hydraulic oil of oil hydraulic cylinder.
Further, the degree of regulation of the stroke of piston rod is not more than 0.5mm.
Favourable, described hydraulic pressure Multipoint synchronous control system also comprises a plurality of pressure transducers, detects respectively a plurality of piston rods suffered pressure in lifting process, and described a plurality of pressure transducers are communicated by letter with described isochronous controller; Described isochronous controller is further regulated the stroke of corresponding piston rod based on the pressure that is detected by described pressure transducer.
According on the other hand of the present utility model, a kind of hydraulic pressure Multipoint synchronous control system has been proposed, comprising: a plurality of deceleration loading devices, each deceleration loading device has oil hydraulic cylinder, piston and piston rod; Plunger pump; Hydraulic circuit, be connected to the oil hydraulic cylinder of described a plurality of deceleration loading devices, described plunger pump is used for supplying with hydraulic oil to hydraulic circuit, described hydraulic circuit comprises a plurality of hydraulic oil branch roads of drawing from described plunger delivery side of pump, the parallel layout of described a plurality of hydraulic oil branch roads, be provided with an electromagnetic switching valve on each hydraulic oil branch road, one way outlet of described electromagnetic switching valve is communicated with via the hydraulic fluid chamber of piston top in the first branch and oil hydraulic cylinder, and another way outlet of described electromagnetic switching valve is communicated with via the hydraulic fluid chamber below piston in the second branch and oil hydraulic cylinder; A plurality of pressure transducers detect respectively a plurality of piston rods suffered pressure in lifting process; An isochronous controller, described a plurality of pressure transducer is communicated by letter with described isochronous controller, and described isochronous controller is based on the pressure that is detected by described pressure transducer, control at least one in described electromagnetic switching valve, roughly the same to guarantee each piston rod suffered pressure in lifting process with the stroke of regulating corresponding piston rod.
Favourable, described isochronous controller control the oil pressure of the hydraulic oil that enters oil hydraulic cylinder, the oil-feed direction that enters the hydraulic oil of oil hydraulic cylinder, hydraulic oil the oil-feed time, enter at least a in the oil mass of hydraulic oil of oil hydraulic cylinder and regulate corresponding piston rod suffered pressure in lifting process.
Favourable, described hydraulic pressure Multipoint synchronous control system also comprises a plurality of displacement transducers, for detection of the stroke of the piston rod of the oil hydraulic cylinder of correspondence; Described a plurality of displacement transducer is communicated by letter with described isochronous controller, and the described isochronous controller stroke of further regulating corresponding piston rod based on the piston rod stroke that is detected by displacement transducer is roughly the same to guarantee each piston rod suffered pressure in lifting process.
In above-mentioned hydraulic pressure Multipoint synchronous control system, optional, described hydraulic pressure Multipoint synchronous control system also comprises the pressure oil-feed pump, and described pressure oil-feed pump is arranged on the intake side of described plunger pump, is used for the hydraulic oil coercively fed to described plunger pump.Favourable, described outlet of plunger pump pressure is at least 70MPa, and flow is between 0.3L/min-1.2L/min.
Favourable, described plunger pump provides flow with the rotating speed linear change by the rotating speed that utilizes frequency variator to change its drive motor.
Optionally, described frequency variator utilizes analogue signal to control.
Further, utilize digital signal to realize with communicating by letter of described isochronous controller.
Utilize the technical solution of the utility model, can realize the Multipoint synchronous of hydraulic jacking system is controlled.Further, in the situation that force oil-feed pump to be arranged on the intake side of described plunger pump, can significantly improve volumetric efficiency.And, utilize digital signal to realize and the communicating by letter of isochronous controller in the situation that utilize analogue signal to control plunger pump, can significantly reduce the signal interference.
Description of drawings
Fig. 1 is the schematic block diagram according to an embodiment's of the present utility model hydraulic pressure Multipoint synchronous control system.
Fig. 2 is the schematic block diagram according to another embodiment's of the present utility model hydraulic pressure Multipoint synchronous control system.
Fig. 3 is the schematic block diagram according to another embodiment's of the present utility model hydraulic pressure Multipoint synchronous control system.
Fig. 4 is the structural representation according to the pressure oil-feed of an embodiment's of the utility model hydraulic pressure Multipoint synchronous control system.
Embodiment
The below describes the embodiment of exemplary of the present utility model in detail, and embodiment's example is shown in the drawings, and wherein same or analogous label represents same or analogous element.The embodiment who describes below with reference to accompanying drawing is exemplary, is intended to explain the utility model, and can not be interpreted as restriction of the present utility model.
as shown in fig. 1, the hydraulic pressure Multipoint synchronous control system according to an exemplary embodiment of the present utility model comprises: a plurality of deceleration loading devices 10, each deceleration loading device have oil hydraulic cylinder 11, piston 12 and piston rod 13, plunger pump 20, hydraulic circuit, be connected to the oil hydraulic cylinder 11 of described a plurality of deceleration loading device 10, described plunger pump 20 is used for supplying with hydraulic oil to hydraulic circuit, described hydraulic circuit comprises a plurality of hydraulic oil branch roads 21 of drawing from the outlet of described plunger pump 20, the parallel layout of described a plurality of hydraulic oil branch roads 21, be provided with an electromagnetic switching valve 22 on each hydraulic oil branch road, one way outlet of described electromagnetic switching valve is communicated with via the hydraulic fluid chamber of piston top in the first branch 221 and oil hydraulic cylinder, another way outlet of described electromagnetic switching valve is communicated with via the hydraulic fluid chamber of piston below in the second branch 222 and oil hydraulic cylinder, a plurality of displacement transducers 40 are for detection of the stroke of the piston rod 13 of the oil hydraulic cylinder 11 of correspondence, an isochronous controller 50, described a plurality of displacement transducer 40 is communicated by letter with described isochronous controller 50, and described isochronous controller is based on the piston rod stroke that is detected by displacement transducer 40, control at least one in described electromagnetic switching valve 22, roughly the same with the stroke of guaranteeing all piston rods 13.
Stroke difference between piston rod 13 (its can by the calculator in isochronous controller 50 calculate) is in the situation that the progressive error threshold value within (its can be stored in the storage of isochronous controller 50 in) scope, isochronous controller 50 is all deceleration loading devices 10 of synchronization control directly, for example, simultaneously supply with hydraulic oil to the oil pocket of piston 12 belows of the oil hydraulic cylinder 11 of deceleration loading device 10.In the situation that progressive error surpasses the progressive error threshold value, isochronous controller 50 can be controlled separately respectively the piston rod 13 of each deceleration loading device 10, to regulate the stroke of each piston rod 13, also can regulate separately several deceleration loading devices 10 wherein, keep simultaneously the current operation of other deceleration loading devices 10.By regulating one by one or local modulation, can realize the roughly equilibrium between the piston rod stroke between a plurality of deceleration loading devices 10.
The feedback signal of utilizing displacement transducer 40 to provide can realize stroke roughly balanced of the piston rod 13 of a plurality of deceleration loading devices 10.
Favourable, described isochronous controller 50 control the oil pressure of the hydraulic oil that enters oil hydraulic cylinder 11, the oil-feed direction that enters the hydraulic oil of oil hydraulic cylinder 11, hydraulic oil the oil-feed time, enter at least a stroke of regulating corresponding piston rod 13 in the oil mass of hydraulic oil of oil hydraulic cylinder.Degree of regulation to the stroke of piston rod 13 preferably is not more than 0.5mm.
As shown in Figure 3, hydraulic pressure Multipoint synchronous control system in Fig. 1 also can comprise a plurality of pressure transducers 60, detect respectively a plurality of piston rods 13 suffered pressure in lifting process (or jacking process), described a plurality of pressure transducers 60 are communicated by letter with described isochronous controller 50; Described isochronous controller 50 is further regulated the stroke of corresponding piston rod 13 based on the pressure that is detected by described pressure transducer 60.
In the situation that piston rod 13 jackings, the pressure that piston rod 13 is subject to also can reflect the stroke of piston rod 13.For example, in the situation that by four deceleration loading devices 10 in Fig. 3 simultaneously rectangle plate of horizontal jacking and this four deceleration loading devices 10 be placed in respectively four bights of rectangle plate, can think that pressure that piston rod 13 is subject to is proportional to the stroke of piston rod 13.The signal that utilizes pressure transducer 60 to obtain can further be finely tuned the stroke of the piston rod 13 of different deceleration loading device 10, in the stroke difference of guaranteeing piston rod 13 in the situation that in prespecified range, make each piston rod 13 bear roughly the same pressure.
Below the exemplary operation that illustrates hydraulic pressure Multipoint synchronous control system.
Suppose in Fig. 3 deceleration loading device 10 from left to right its piston rod stroke be respectively 10mm, 10.5mm, 10.5mm, 11.5mm, and the threshold value of the stroke difference of isochronous controller 50 inner piston rods 13 is 1mm.As seen, the stroke difference of the stroke of the piston rod 13 of the leftmost side and the piston rod 13 of the rightmost side is 1.5mm, greater than the threshold value 1mm that sets.at this moment, isochronous controller 50 can be controlled the electromagnetic switching valve 22 of the rightmost side, supply with hydraulic oil a period of time via the first branch road 221 in the hydraulic fluid chamber of piston 12 tops of the oil hydraulic cylinder 11 of the deceleration loading device 10 of the rightmost side, and keep the operation of other deceleration loading devices 10 constant, monitor simultaneously the stroke of all piston rods, until the stroke difference of the piston rod 13 of the stroke of the piston rod 13 of the leftmost side and the rightmost side at 1mm with interior for example 0.5mm, at this moment, deceleration loading device 10 in Fig. 3 from left to right its piston rod stroke is respectively for example 10.3mm, 10.8mm, 10.8mm, 11.1mm.Then, the electromagnetic switching valve 22 that isochronous controller 50 can be controlled the rightmost side is supplied with hydraulic oil via the second branch road 222 in the hydraulic fluid chamber of piston 12 belows of the oil hydraulic cylinder 11 of the deceleration loading device 10 of the rightmost side, and the stroke of all piston rods is monitored in the operation that keeps other deceleration loading devices 10 simultaneously.Certainly, the electromagnetic switching valve 22 of deceleration loading device 10 correspondences that also can close the rightmost side to interrupt to 10 fuel feeding a period of times of deceleration loading device of this rightmost side until the stroke difference of the piston rod 13 of the current minimum stroke of piston rod 13 and the rightmost side in 1mm.Can also keep the operation of electromagnetic switching valve 22 of deceleration loading device 10 correspondences of the leftmost side constant, and close three other electromagnetic switching valves 22 and not to oil hydraulic cylinder 11 fuel feeding of correspondence, can increase the stroke of the piston rod 13 of the leftmost side.To the situation of single oil hydraulic cylinder fuel feeding, rotating speed that can pilot plunger pump 20 is to regulate the oil pressure supplied with, oil mass etc. for only.
If the detection based on pressure transducer 60, find through above-mentioned adjustment (progressive error between piston rod is in threshold range) afterwards the deceleration loading device 10 in Fig. 3 from left to right the pressure that is subject to of its piston rod 13 for example be respectively 100 tons, 102 tons, 103 tons, 105 tons, and the threshold pressure differential of isochronous controller 50 interior settings is 4 tons, can similarly further reduce the stroke of rightmost side piston rod 13 or further increase the stroke of leftmost side piston rod 13, until pressure reduction is in threshold pressure differential.
Certainly, the adjustment of the stroke difference that records based on displacement transducer can be synchronizeed with the adjustment of the pressure difference value that records based on pressure transducer and carried out, restriction mutually.
For the electromagnetic switching valve 22 of opening, isochronous controller 50 can also be controlled fuel feeding direction (being that electromagnetic switching valve 22 is fuel-displaced via the first branch road 221 or the second branch road 222).
The above operation that also can be applicable to similarly following hydraulic pressure Multipoint synchronous control system according to another embodiment of the present utility model to the exemplary description according to the operation of an embodiment's of the present utility model hydraulic pressure Multipoint synchronous control system.
as shown in Figure 2, the hydraulic pressure Multipoint synchronous control system according to another exemplary embodiment of the present utility model comprises: a plurality of deceleration loading devices 10, each deceleration loading device have oil hydraulic cylinder 11, piston 12 and piston rod 13, plunger pump 20, hydraulic circuit, be connected to the oil hydraulic cylinder 11 of described a plurality of deceleration loading devices, described plunger pump 20 is used for supplying with hydraulic oil to hydraulic circuit, described hydraulic circuit comprises a plurality of hydraulic oil branch roads 21 of drawing from described plunger delivery side of pump, the parallel layout of described a plurality of hydraulic oil branch roads 21, be provided with an electromagnetic switching valve 22 on each hydraulic oil branch road, one way outlet of described electromagnetic switching valve 22 is communicated with via the hydraulic fluid chamber of piston top in the first branch 221 and oil hydraulic cylinder, another way outlet of described electromagnetic switching valve is communicated with via the hydraulic fluid chamber of piston below in the second branch 222 and oil hydraulic cylinder, a plurality of pressure transducers 60 detect respectively a plurality of piston rods 13 suffered pressure in (or jacking) process of lifting, an isochronous controller 50, described a plurality of pressure transducer 60 is communicated by letter with described isochronous controller 50, and described isochronous controller is based on the pressure that is detected by described pressure transducer 60, control at least one in described electromagnetic switching valve 22, roughly the same to guarantee each piston rod 13 suffered pressure in lifting process with the stroke of regulating corresponding piston rod 13.
The feedback signal of utilizing pressure transducer 60 to provide can realize the roughly balanced of pressure that the piston rod of a plurality of deceleration loading devices 10 is subject to.
Similarly, described isochronous controller 50 can control the oil pressure of the hydraulic oil that enters oil hydraulic cylinder 11, the oil-feed direction that enters the hydraulic oil of oil hydraulic cylinder 11, hydraulic oil the oil-feed time, enter at least a in the oil mass of hydraulic oil of oil hydraulic cylinder 11 and regulate corresponding piston rod 13 suffered pressure in lifting process.
Equally as shown in Figure 3, the hydraulic pressure Multipoint synchronous control system in Fig. 2 also can comprise a plurality of displacement transducers, for detection of the stroke of the piston rod 13 of the oil hydraulic cylinder 11 of correspondence.Described a plurality of displacement transducer 40 is communicated by letter with described isochronous controller 50, and described isochronous controller 50 stroke of further regulating corresponding piston rod 13 based on piston rod 13 strokes that detected by displacement transducer 40 is roughly the same to guarantee each piston rod 13 suffered pressure in lifting process.
In the situation that piston rod 13 jackings, the stroke of piston rod 13 also can reflect the pressure that piston rod 13 is subject to.For example, in the situation that by four deceleration loading devices 10 in Fig. 3 simultaneously rectangle plate of horizontal jacking and this four deceleration loading devices 10 be placed in respectively four bights of rectangle plate, can think that the stroke of piston rod 13 is proportional to the pressure that piston rod 13 is subject to.The signal that utilizes displacement transducer 40 to obtain; can further finely tune the pressure that the piston rod 13 of different deceleration loading device 10 is subject to; guaranteeing the pressure difference value that piston rod 13 is subject in the situation that in prespecified range, make each piston rod 13 keep roughly the same stroke.
As shown in Fig. 1-3, described hydraulic pressure Multipoint synchronous control system also comprises forces oil-feed pump 70, and described pressure oil-feed pump 70 is arranged on the intake side of described plunger pump 20, is used for the hydraulic oil coercively fed to described plunger pump 20.Show in detail in Fig. 4 and force being connected between oil-feed pump 70 and plunger pump 20.In the situation that force oil-feed pump 70 to be arranged on the intake side of described plunger pump, especially for the running of hydraulic power oil of small flow, can significantly improve volumetric efficiency.
Favourable, described plunger pump 20 outlet pressures are at least 70MPa, and flow is between 0.3L/min-1.2L/min.
Described plunger pump 20 can provide by the rotating speed that utilizes frequency variator to change its drive motor the flow with rotating speed (for example 300r/min-2000r/min) linear change.Described frequency variator can utilize analogue signal to control.Favourable, utilize digital signal to realize with the communicating by letter of described isochronous controller 50 (comprising communicating by letter of pressure transducer and/or displacement transducer and isochronous controller 50), so, can significantly reduce signal and disturb.
Although illustrated and described embodiment of the present utility model, for the ordinary skill in the art, be appreciated that in the situation that do not break away from principle of the present utility model and spirit can change these embodiments.Applicable scope of the present utility model is limited by claims and equivalent thereof.
Claims (12)
1. hydraulic pressure Multipoint synchronous control system comprises:
A plurality of deceleration loading devices, each deceleration loading device has oil hydraulic cylinder, piston and piston rod;
Plunger pump;
Hydraulic circuit, be connected to the oil hydraulic cylinder of described a plurality of deceleration loading devices, described plunger pump is used for supplying with hydraulic oil to hydraulic circuit, described hydraulic circuit comprises a plurality of hydraulic oil branch roads of drawing from described plunger delivery side of pump, the parallel layout of described a plurality of hydraulic oil branch roads, be provided with an electromagnetic switching valve on each hydraulic oil branch road, one way outlet of described electromagnetic switching valve is communicated with via the hydraulic fluid chamber of piston top in the first branch and oil hydraulic cylinder, and another way outlet of described electromagnetic switching valve is communicated with via the hydraulic fluid chamber below piston in the second branch and oil hydraulic cylinder;
A plurality of displacement transducers are for detection of the stroke of the piston rod of the oil hydraulic cylinder of correspondence;
An isochronous controller, described a plurality of displacement transducer is communicated by letter with described isochronous controller, and described isochronous controller is controlled at least one in described electromagnetic switching valve based on the piston rod stroke that is detected by displacement transducer, and is roughly the same with the stroke of guaranteeing all piston rods.
2. hydraulic pressure Multipoint synchronous control system according to claim 1 is characterized in that:
Described isochronous controller control the oil pressure of the hydraulic oil that enters oil hydraulic cylinder, the oil-feed direction that enters the hydraulic oil of oil hydraulic cylinder, hydraulic oil the oil-feed time, enter at least a stroke of regulating corresponding piston rod in the oil mass of hydraulic oil of oil hydraulic cylinder.
3. hydraulic pressure Multipoint synchronous control system according to claim 2 is characterized in that:
Degree of regulation to the stroke of piston rod is not more than 0.5mm.
4. hydraulic pressure Multipoint synchronous control system according to claim 2 is characterized in that:
Described hydraulic pressure Multipoint synchronous control system also comprises a plurality of pressure transducers, detects respectively a plurality of piston rods suffered pressure in lifting process, and described a plurality of pressure transducers are communicated by letter with described isochronous controller;
Described isochronous controller is further regulated the stroke of corresponding piston rod based on the pressure that is detected by described pressure transducer.
5. hydraulic pressure Multipoint synchronous control system comprises:
A plurality of deceleration loading devices, each deceleration loading device has oil hydraulic cylinder, piston and piston rod;
Plunger pump;
Hydraulic circuit, be connected to the oil hydraulic cylinder of described a plurality of deceleration loading devices, described plunger pump is used for supplying with hydraulic oil to hydraulic circuit, described hydraulic circuit comprises a plurality of hydraulic oil branch roads of drawing from described plunger delivery side of pump, the parallel layout of described a plurality of hydraulic oil branch roads, be provided with an electromagnetic switching valve on each hydraulic oil branch road, one way outlet of described electromagnetic switching valve is communicated with via the hydraulic fluid chamber of piston top in the first branch and oil hydraulic cylinder, and another way outlet of described electromagnetic switching valve is communicated with via the hydraulic fluid chamber below piston in the second branch and oil hydraulic cylinder;
A plurality of pressure transducers detect respectively a plurality of piston rods suffered pressure in lifting process;
An isochronous controller, described a plurality of pressure transducer is communicated by letter with described isochronous controller, and described isochronous controller is based on the pressure that is detected by described pressure transducer, control at least one in described electromagnetic switching valve, roughly the same to guarantee each piston rod suffered pressure in lifting process with the stroke of regulating corresponding piston rod.
6. hydraulic pressure Multipoint synchronous control system according to claim 5 is characterized in that:
Described isochronous controller control the oil pressure of the hydraulic oil that enters oil hydraulic cylinder, the oil-feed direction that enters the hydraulic oil of oil hydraulic cylinder, hydraulic oil the oil-feed time, enter at least a in the oil mass of hydraulic oil of oil hydraulic cylinder and regulate corresponding piston rod suffered pressure in lifting process.
7. hydraulic pressure Multipoint synchronous control system according to claim 5 is characterized in that:
Described hydraulic pressure Multipoint synchronous control system also comprises a plurality of displacement transducers, for detection of the stroke of the piston rod of the oil hydraulic cylinder of correspondence;
Described a plurality of displacement transducer is communicated by letter with described isochronous controller, and the described isochronous controller stroke of further regulating corresponding piston rod based on the piston rod stroke that is detected by displacement transducer is roughly the same to guarantee each piston rod suffered pressure in lifting process.
8. the described hydraulic pressure Multipoint synchronous of any one control system according to claim 1-7 is characterized in that:
Described hydraulic pressure Multipoint synchronous control system also comprises the pressure oil-feed pump, and described pressure oil-feed pump is arranged on the intake side of described plunger pump, is used for the hydraulic oil coercively fed to described plunger pump.
9. hydraulic pressure Multipoint synchronous control system according to claim 8 is characterized in that:
Described outlet of plunger pump pressure is at least 70MPa, and flow is between 0.3L/min-1.2L/min.
10. hydraulic pressure Multipoint synchronous control system according to claim 9 is characterized in that:
Described plunger pump provides flow with the rotating speed linear change by the rotating speed that utilizes frequency variator to change its drive motor.
11. hydraulic pressure Multipoint synchronous control system according to claim 10 is characterized in that:
Described frequency variator utilizes analogue signal to control.
12. hydraulic pressure Multipoint synchronous control system according to claim 11 is characterized in that:
Utilize digital signal to realize with communicating by letter of described isochronous controller.
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| CN 201220713186 CN202991683U (en) | 2012-12-20 | 2012-12-20 | Hydraulic multipoint synchronous control system |
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| CN 201220713186 CN202991683U (en) | 2012-12-20 | 2012-12-20 | Hydraulic multipoint synchronous control system |
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103334973A (en) * | 2013-06-13 | 2013-10-02 | 三一汽车起重机械有限公司 | Synchronizing system for multiple hydraulic cylinders and control method for synchronizing system for multiple hydraulic cylinders |
| CN103883574A (en) * | 2012-12-20 | 2014-06-25 | 国家核电技术有限公司 | Hydraulic multipoint synchronous control system |
| CN105570238A (en) * | 2016-01-07 | 2016-05-11 | 南通大学 | Valveless hydraulic servo synchronous system |
| CN105984022A (en) * | 2015-03-02 | 2016-10-05 | 任丘市永基建筑安装工程有限公司 | Combined die bottom hydraulic cylinder synchronization technology |
| CN106050773A (en) * | 2016-08-11 | 2016-10-26 | 上海华龙测试仪器股份有限公司 | Multi-cylinder loading tester with synchronous control system |
| CN106946144A (en) * | 2017-04-19 | 2017-07-14 | 中央军委后勤保障部建筑工程研究所 | Container handling system synchronous control system based on point-to-point communication |
| CN111577687A (en) * | 2020-05-06 | 2020-08-25 | 太原理工大学 | Load-sensitive double-hydraulic-cylinder synchronization system and control method thereof |
-
2012
- 2012-12-20 CN CN 201220713186 patent/CN202991683U/en not_active Expired - Lifetime
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103883574A (en) * | 2012-12-20 | 2014-06-25 | 国家核电技术有限公司 | Hydraulic multipoint synchronous control system |
| CN103334973A (en) * | 2013-06-13 | 2013-10-02 | 三一汽车起重机械有限公司 | Synchronizing system for multiple hydraulic cylinders and control method for synchronizing system for multiple hydraulic cylinders |
| CN105984022A (en) * | 2015-03-02 | 2016-10-05 | 任丘市永基建筑安装工程有限公司 | Combined die bottom hydraulic cylinder synchronization technology |
| CN105570238A (en) * | 2016-01-07 | 2016-05-11 | 南通大学 | Valveless hydraulic servo synchronous system |
| CN106050773A (en) * | 2016-08-11 | 2016-10-26 | 上海华龙测试仪器股份有限公司 | Multi-cylinder loading tester with synchronous control system |
| CN106946144A (en) * | 2017-04-19 | 2017-07-14 | 中央军委后勤保障部建筑工程研究所 | Container handling system synchronous control system based on point-to-point communication |
| CN111577687A (en) * | 2020-05-06 | 2020-08-25 | 太原理工大学 | Load-sensitive double-hydraulic-cylinder synchronization system and control method thereof |
| CN111577687B (en) * | 2020-05-06 | 2021-10-08 | 太原理工大学 | Load-sensitive double-hydraulic-cylinder synchronization system and control method thereof |
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