CN204226308U - A kind of ultrahigh-pressure hydraulic pressurization system - Google Patents
A kind of ultrahigh-pressure hydraulic pressurization system Download PDFInfo
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- CN204226308U CN204226308U CN201420561972.3U CN201420561972U CN204226308U CN 204226308 U CN204226308 U CN 204226308U CN 201420561972 U CN201420561972 U CN 201420561972U CN 204226308 U CN204226308 U CN 204226308U
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Abstract
The utility model relates to a kind of ultrahigh-pressure hydraulic pressurization system, comprise one-level pressurization system, Two Stage Turbocharging System and control system, described one-level pressurization system is gas liquid pressurization system, comprise liquid case, air compressor and Pneumatic hydraulic booster pump, described Two Stage Turbocharging System is that liquid drives liquid pressurization system, comprise hydraulic pressure booster cylinder, some Pneumatic valves and one-way valve, described pressurized cylinder high-pressure outlet end both sides are configured with the identical one-way valve in direction respectively, pressurized cylinder low voltage terminal both sides are configured with Pneumatic valve respectively, described one-level pressurization system outlet end is connected with low voltage terminal respectively by the high-pressure outlet end of described one-way valve with Pneumatic valve and described pressurized cylinder, and the one-way valve both sides above described pressurized cylinder high-pressure outlet end are configured with Pneumatic valve, described control system controls the operation of described one-level pressurization system and Two Stage Turbocharging System.The utility model adopts two-step supercharging system to carry out supercharging, and hydraulic pressure can be made greatly to increase, and avoids and uses powerful device to reach the object of high pressure.
Description
Technical field
The utility model relates to a kind of pressurization system, particularly a kind of ultrahigh-pressure hydraulic pressurization system.
Background technique
A certain local in hydraulic system, the pressure needed usually exceeds the delivery pressure of power source, but is inconvenient to again use powerful power equipment to meet this high pressure, can waste resource like this, also can increase the volume of machinery, therefore expedite the emergence of the pressurization system of hydraulic pressure.Current hydraulic booster technology can be divided three classes roughly, and one is gas drive liquid high pressure technique, and it adopts low-pressure compressed air to drive suction booster to carry out fluid pressurization, and the highest hydraulic pressure can reach 500MPa at present.Two is that liquid drives liquid high pressure technique, and it adopts hydraulic system to drive fluid pressurization to carry out fluid pressurization, and current maximum pressure can reach 400MPa.Three is electric hydaulic technology, and it adopts motor-drive pump to produce the current maximum pressure of high-pressure and hydraulics can reach 100PMa.Visible existing high-pressure and hydraulic technology is all adopt one-level supercharging technology to carry out supercharging, so supercharging amplitude is little, most high output pressure also cannot reach the high pressure of more than 1000MPa, and this situation is urgently to be resolved hurrily.
Model utility content
In order to overcome above-mentioned technical problem, the utility model provides a kind of ultrahigh-pressure hydraulic pressurization system, and this system can produce higher hydraulic pressure, meets the needs of real work.
The technological scheme that the utility model adopts is:
A kind of ultrahigh-pressure hydraulic pressurization system, comprise one-level pressurization system, Two Stage Turbocharging System and control system, described one-level pressurization system is gas liquid pressurization system, comprise liquid case, air compressor and Pneumatic hydraulic booster pump, described Two Stage Turbocharging System is that liquid drives liquid pressurization system, comprise hydraulic pressure booster cylinder, some Pneumatic valves and one-way valve, described pressurized cylinder high-pressure outlet end both sides are configured with the identical one-way valve in direction respectively, pressurized cylinder low voltage terminal both sides are configured with Pneumatic valve respectively, described one-level pressurization system outlet end is connected with low voltage terminal respectively by the high-pressure outlet end of described one-way valve with Pneumatic valve and described pressurized cylinder, and the one-way valve both sides above described pressurized cylinder high-pressure outlet end are configured with Pneumatic valve, described Two Stage Turbocharging System continues supercharging on the basis of one-level pressurization system supercharging, described control system controls the operation of described one-level pressurization system and Two Stage Turbocharging System, it comprises computer, PCL and electric elements.
Preferably, stop valve and filter is provided with between the liquid case of described one-level pressurization system and Pneumatic hydraulic booster pump, described Pneumatic hydraulic booster pump outlet end is provided with pressure gauge and pressure transducer, is provided with filter, electrical equipment Proportional valve, pressure gauge and solenoid valve between described air compressor and Pneumatic hydraulic booster pump.
Preferably, described Pneumatic valve is all connected with solenoid valve, and described solenoid valve is connected with described control system and controls by it.
Preferably, described Pneumatic hydraulic booster pump is provided with silencing apparatus.
Preferably, described pressurized cylinder high-pressure outlet end is provided with pressure transducer.
Preferably, described one-level pressurization system supercharging ratio is 195:1, and described Two Stage Turbocharging System supercharging ratio is 1:10.
The beneficial effects of the utility model are:
1, the utility model adopts two-step supercharging system to carry out supercharging, and hydraulic pressure can be made greatly to increase, and avoids and uses powerful device to reach the object of high pressure, save resource, also can not increase the volume of machinery.
2, the utility model is provided with computer controlled system, can the size of hydraulic control, direction and switch, safety easy to use.
3, the utility model is as detection facility, for the pressure test of ultrahigh pressure component, comprises static pressure test and explosion is tested.
4, the utility model is as ultrahigh pressure self intensification manufacturing mechanism, may be used for the Self-enhancement treatment of all kinds of ultrahigh pressure pipe fitting, steel pipe, container.
Accompanying drawing explanation
Below in conjunction with drawings and embodiments, the utility model is further illustrated.
Fig. 1 is structure flow chart of the present utility model;
Fig. 2 is the flow chart of simplification one-level pressurization system of the present utility model.
Embodiment
As shown in Figure 1 to Figure 2, a kind of ultrahigh-pressure hydraulic pressurization system of the present embodiment, comprise one-level pressurization system, Two Stage Turbocharging System and control system, described one-level pressurization system is gas liquid pressurization system, comprise liquid case, air compressor and Pneumatic hydraulic booster pump, stop valve and filter is provided with between the liquid case of described one-level pressurization system and Pneumatic hydraulic booster pump, described Pneumatic hydraulic booster pump outlet end is provided with pressure gauge and pressure transducer, filter is provided with between described air compressor and Pneumatic hydraulic booster pump, electrical equipment Proportional valve, pressure gauge and solenoid valve.In addition, described Pneumatic hydraulic booster pump is provided with silencing apparatus.
Described Two Stage Turbocharging System is that liquid drives liquid pressurization system, comprise hydraulic pressure booster cylinder, some Pneumatic valves and one-way valve, described pressurized cylinder high-pressure outlet end both sides are configured with the identical one-way valve in direction respectively, pressurized cylinder low voltage terminal both sides are configured with Pneumatic valve respectively, described Pneumatic valve is all connected with solenoid valve, described solenoid valve is connected with described control system, and described solenoid valve drives air to control it after filtering pressure reducing valve.Described pressurized cylinder high-pressure outlet end is provided with pressure transducer.Described one-level pressurization system outlet end is connected with described pressurized cylinder low voltage terminal by described Pneumatic valve, and be connected with low voltage terminal respectively by the high-pressure outlet end of described one-way valve with Pneumatic valve and described pressurized cylinder, and the one-way valve both sides above described pressurized cylinder high-pressure outlet end are configured with Pneumatic valve, described Two Stage Turbocharging System continues supercharging on the basis of one-level pressurization system supercharging, described control system controls the operation of described one-level pressurization system and Two Stage Turbocharging System, and it comprises computer, PCL and electric elements.In addition, arranging described one-level pressurization system supercharging ratio is 195:1, and described Two Stage Turbocharging System supercharging ratio is 1:10.
Wherein, Pneumatic valve B in Fig. 1 and Pneumatic valve C is used for controlling the commutation of pressurized cylinder in Two Stage Turbocharging System, open Pneumatic valve C and close Pneumatic valve B, the descent of piston of pressurized cylinder, pressurized cylinder is in imbibition process, open Pneumatic valve B and close Pneumatic valve C, then pressurized cylinder piston is up, is in secondary booster process.Pneumatic valve A is pressure-relief valve, and Pneumatic valve D is stop valve.One-way valve prevents ultrahigh pressure adverse current when being used for pressurized cylinder commutation.Electrical equipment Proportional valve is used for automatically regulating driving air pressure, thus controls the delivery pressure of one-level pressurization system, and pressure gauge and pressure transducer are used for gathering the delivery pressure of one-level or Two Stage Turbocharging System.
The whole workflow of the present embodiment is: air compressor produces pressurized air through filter, Pneumatic hydraulic booster pump is entered after electromagnetic proportional valve and solenoid valve, Pneumatic hydraulic booster pump is started working, export after liquid medium in liquid case is sucked Pneumatic hydraulic booster pump entry end by stop valve and filter, export high-pressure outlet on the one hand, export Two Stage Turbocharging System on the other hand, when opening Pneumatic valve B and closing Pneumatic valve C, hydraulic pressure enters pressurized cylinder bottom low voltage terminal through Pneumatic valve B, promotion pressurized cylinder piston is up, when opening Pneumatic valve C and closing Pneumatic valve B, hydraulic pressure enters the high-pressure outlet end on pressurized cylinder top, pressurized cylinder piston is descending.Liquid medium, after the supercharging of one-level pressurization system, enters Two Stage Turbocharging System, by pressurized cylinder, liquid medium is carried out secondary booster, exported by Pneumatic valve D afterwards, until after reaching required high-pressure, pressurized cylinder quits work, at this moment close Pneumatic valve D, enter pressure maintenance phase.When needs release, open Pneumatic valve A and D successively, liquid medium lets out liquid-return box through Pneumatic valve D and Pneumatic valve A.
The above be the utility model preferred embodiment, it does not form the restriction to the utility model protection domain.
Claims (6)
1. a ultrahigh-pressure hydraulic pressurization system, comprise one-level pressurization system, Two Stage Turbocharging System and control system, it is characterized in that, described one-level pressurization system is gas liquid pressurization system, comprise liquid case, air compressor and Pneumatic hydraulic booster pump, described Two Stage Turbocharging System is that liquid drives liquid pressurization system, comprise hydraulic pressure booster cylinder, some Pneumatic valves and one-way valve, described pressurized cylinder high-pressure outlet end both sides are configured with the identical one-way valve in direction respectively, pressurized cylinder low voltage terminal both sides are configured with Pneumatic valve respectively, described one-level pressurization system outlet end is connected with low voltage terminal respectively by the high-pressure outlet end of described one-way valve with Pneumatic valve and described pressurized cylinder, and the one-way valve both sides above described pressurized cylinder high-pressure outlet end are configured with Pneumatic valve, described Two Stage Turbocharging System continues supercharging on the basis of one-level pressurization system supercharging, described control system controls the operation of described one-level pressurization system and Two Stage Turbocharging System, it comprises computer, PCL and electric elements.
2. hydraulic pressure boosting system according to claim 1, it is characterized in that, stop valve and filter is provided with between the liquid case of described one-level pressurization system and Pneumatic hydraulic booster pump, described Pneumatic hydraulic booster pump outlet end is provided with pressure gauge and pressure transducer, is provided with filter, electrical equipment Proportional valve, pressure gauge and solenoid valve between described air compressor and Pneumatic hydraulic booster pump.
3. hydraulic pressure boosting system according to claim 1, is characterized in that, described Pneumatic valve is all connected with solenoid valve, and described solenoid valve is connected with described control system and controls by it.
4. hydraulic pressure boosting system according to claim 1, is characterized in that, described Pneumatic hydraulic booster pump is provided with silencing apparatus.
5. hydraulic pressure boosting system according to claim 1, is characterized in that, described pressurized cylinder high-pressure outlet end is provided with pressure transducer.
6. hydraulic pressure boosting system according to claim 1, is characterized in that, described one-level pressurization system supercharging ratio is 195:1, and described Two Stage Turbocharging System supercharging ratio is 1:10.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420561972.3U CN204226308U (en) | 2014-09-26 | 2014-09-26 | A kind of ultrahigh-pressure hydraulic pressurization system |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420561972.3U CN204226308U (en) | 2014-09-26 | 2014-09-26 | A kind of ultrahigh-pressure hydraulic pressurization system |
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| CN204226308U true CN204226308U (en) | 2015-03-25 |
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| CN201420561972.3U Expired - Fee Related CN204226308U (en) | 2014-09-26 | 2014-09-26 | A kind of ultrahigh-pressure hydraulic pressurization system |
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| CN (1) | CN204226308U (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106969887A (en) * | 2016-05-17 | 2017-07-21 | 上海石油天然气有限公司 | High pressure test device for air tightness |
| CN106969890A (en) * | 2016-07-15 | 2017-07-21 | 上海石油天然气有限公司 | High pressure watertight system safety testing device |
| CN106996403A (en) * | 2017-06-02 | 2017-08-01 | 中国科学院地球化学研究所 | A kind of fluid power plant and pressure method for accurately controlling pressure |
| CN107035739A (en) * | 2017-06-02 | 2017-08-11 | 中国科学院地球化学研究所 | A kind of aerodynamic device and pressure method for accurately controlling pressure |
| CN108425821A (en) * | 2018-05-18 | 2018-08-21 | 宁波真格液压科技有限公司 | A kind of hydraulic booster pump |
| CN108716464A (en) * | 2018-05-18 | 2018-10-30 | 宁波真格液压科技有限公司 | A kind of hydraulic booster pump |
| CN108730144A (en) * | 2018-05-18 | 2018-11-02 | 宁波真格液压科技有限公司 | A kind of hydraulic booster pump |
| CN109538552A (en) * | 2019-01-03 | 2019-03-29 | 杨斌堂 | Fluid passage driving device and composite structure |
| CN112362494A (en) * | 2020-10-15 | 2021-02-12 | 中国特种设备检测研究院 | Hydraulic bulging test system |
-
2014
- 2014-09-26 CN CN201420561972.3U patent/CN204226308U/en not_active Expired - Fee Related
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106969887A (en) * | 2016-05-17 | 2017-07-21 | 上海石油天然气有限公司 | High pressure test device for air tightness |
| CN106969890A (en) * | 2016-07-15 | 2017-07-21 | 上海石油天然气有限公司 | High pressure watertight system safety testing device |
| CN106996403A (en) * | 2017-06-02 | 2017-08-01 | 中国科学院地球化学研究所 | A kind of fluid power plant and pressure method for accurately controlling pressure |
| CN107035739A (en) * | 2017-06-02 | 2017-08-11 | 中国科学院地球化学研究所 | A kind of aerodynamic device and pressure method for accurately controlling pressure |
| CN108425821A (en) * | 2018-05-18 | 2018-08-21 | 宁波真格液压科技有限公司 | A kind of hydraulic booster pump |
| CN108716464A (en) * | 2018-05-18 | 2018-10-30 | 宁波真格液压科技有限公司 | A kind of hydraulic booster pump |
| CN108730144A (en) * | 2018-05-18 | 2018-11-02 | 宁波真格液压科技有限公司 | A kind of hydraulic booster pump |
| CN108716464B (en) * | 2018-05-18 | 2020-05-12 | 泗阳广鑫机电制造有限公司 | Hydraulic booster pump |
| CN108730144B (en) * | 2018-05-18 | 2020-08-28 | 台州市鑫屏机电有限公司 | Hydraulic booster pump |
| CN109538552A (en) * | 2019-01-03 | 2019-03-29 | 杨斌堂 | Fluid passage driving device and composite structure |
| CN112362494A (en) * | 2020-10-15 | 2021-02-12 | 中国特种设备检测研究院 | Hydraulic bulging test system |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20150325 Termination date: 20190926 |