CN101975204B - High-speed large-flow valve controlled hydraulic speed generator - Google Patents
High-speed large-flow valve controlled hydraulic speed generator Download PDFInfo
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- CN101975204B CN101975204B CN2010105439587A CN201010543958A CN101975204B CN 101975204 B CN101975204 B CN 101975204B CN 2010105439587 A CN2010105439587 A CN 2010105439587A CN 201010543958 A CN201010543958 A CN 201010543958A CN 101975204 B CN101975204 B CN 101975204B
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Abstract
The invention relates to a high-speed large-flow valve controlled hydraulic speed generator which comprises a pressure source, a high-speed large-flow control device and a hydraulic actuator, wherein the pressure source is connected with an inlet channel of the high-speed large-flow control device, the hydraulic actuator is connected with an outlet channel of the high-speed large-flow control device, and the connections are sealed to prevent leakage; and the high-speed large-flow control device can control the movement speed of a piston of the hydraulic actuator so as to adjust the test speed of impact collisions. The pressure difference between an upper cavity and a lower cavity of a piston valve plug is formed by means of the rapid release of pressure fluid, a large-size valve plug is quickly opened, and a larger flow is controlled by a smaller flow. The hydraulic energy of a power source is instantly converted into mechanical energy by means of the quick opening of a large-flow valve, so the difficulties of quick release of large energy and low reaction speed of the traditional large-flow valve in a project are overcome. A discharge circuit arranged in the hydraulic actuator realizes quick release of fluid pressure in a working cavity so as to avoid the oscillation of a piston assembly and the secondary collision of a test piece. The high-speed large-flow valve controlled hydraulic speed generator is applicable to high-speed heavy-load strong collision impact tests of electromechanical equipment, electronic products and various mechanical and construction structures.
Description
Technical field
The present invention relates to a kind of hydraulic pressure of realizing and to be converted into the hydraulic pressure rate generator of mechanical energy, particularly a kind of hydraulic pressure rate generator that can be converted into mechanical energy at short stroke moment realization hydraulic pressure.
Background technique
Improve electromechanical equipment, electronic product and various machinery and building structure opposing foreign impacts such as blast, earthquake, collide and take off and the requirement of the impact loads property that causes of landing has driven impact test apparatus and develops to heavily loaded high speed direction.But because tradition is fallen, the volumes that its means of energy storage of formal cause limit and self is huge such as plumb-bob gravity potential energy or the acting of spring potential energy, it is very little to expand leeway, even can't satisfy the high-speed overload collision impact and test.And adopt burning or blast can't guarantee the control of safety and test progress.Advantages such as it is big that the liquid gas pressure transmission has specific power, and energy storage is convenient become the first-selected kind of drive that realizes novel shock test.The power of existing oil hydraulic motor is too little, can't satisfy the requirement of the instantaneous big flow of impact test apparatus.Pressurized gas have huge pressure potential, how to realize that the potential energy abrupt release of pressurized gas is that key technology to be solved is arranged at present to obtain bigger impact energy.The power transmission of Flow valve at present commonly used or servovalve control hydraulic pressure installation, big for high-power impact test apparatus requirement of moment hydraulic control valve flow, speed of response is fast.But traditional flow direction control valve, opening speed is slow, and the maximum control flow can't satisfy the test requirements document of high-speed overload impact.Traditional position control valve when needs are controlled big flow, often adopts multistage (3 grades even 4 grades) control mode, and the increase of control progression causes complex structure, and is bulky, and speed of response is slow.Though traditional electrohydraulic control speed of response is fast, cost an arm and a leg, requirement on machining accuracy is high, and is strict to the dustiness of fluid, and when the pressure loss was 10Mpa, the peak rate of flow of control was 5500L/min.Secondly; Gas has very strong compressibility; The off-load speed of gas transmission device is much smaller than the off-load speed of liquid, and for fear of the secondary impact of shock test, existing what adopt as the impact test equipment of power with pneumatic shuttle is the spacing by force measure of machinery; Noise is big, and automaticity is low.
Summary of the invention
The present invention is directed to the deficiency of existing technology; Provide a kind of high-speed large-flow valve that utilizes to open fast; Can supply with quantity of liquid hydraulic pressure can be converted into mechanical energy for hydraulic actuator moment, a kind of high-speed large-flow valve control hydraulic pressure rate generator of huge energy is provided for high velocity impact or shock test.
The present invention realizes that the technological scheme of above-mentioned purpose is: comprise pressure source, high-speed large-flow control gear and hydraulic actuator; Pressure source connects with high-speed large-flow control gear inlet channel; Hydraulic actuator connects with high-speed large-flow control gear outlet passage; Pressure source is that hydraulic actuator provides pressure fluid, high-speed large-flow control gear control hydraulic actuator operating rate.Pressure source can be hydraulic accumulator or oil hydraulic pump, and can guarantee provides enough pressure fluids to hydraulic actuator.When pressure source is hydraulic accumulator, comprise accumulator, gas charging valve and liquid-filling valve, gas charging valve is connected with accumulator respectively with liquid-filling valve.Actuator can be oil hydraulic cylinder or oil hydraulic motor; When actuator is when having the oil hydraulic cylinder of quick relief and buffering reset function; Comprise piston rod assembly, cylinder body, throttle valve and off-load servovalve, piston rod assembly is made up of piston, piston rod and percussive hammer, and can in hydraulic cylinder cavity, slide.The high-speed large-flow control gear comprises valve body, piston valve core, adjustable restrictive valve, switch valve, pressure unloading valve, displacement transducer, liquid-filling valve and first buffer; Piston valve core and adjustable restrictive valve band handle spool can move in valve cavity, and displacement transducer is installed in adjustable spool afterbody.Annular groove in the valve body communicates with inlet channel, and inlet channel links to each other with hydraulic accumulator.Between oil pocket and outlet passage, be provided with adjustable restrictive valve, the throttle valve piston of adjustable restrictive valve can slide in bore hole, and band handle spool nose shape and its valve seat are adaptive.The relative position of band handle spool head and outlet passage is controlled by the quantity of adjustable valve piston both sides fluid, reaches the purpose of flow control with this, thus the speed of control percussive hammer.Be provided with a buffer in the control chamber bottom piston valve core is cushioned, control chamber links to each other with liquid-filling valve with the pressure unloading valve through passage.
The quick open theory of high-speed large-flow control gear: when piston valve core control chamber discharge channel is closed; The power that pressure source inlet channel inner fluid acts on the piston valve core ring-shaped step is very little; Can not overcome the control chamber fluid and act on the resistance on the spool, valve is in closed condition.In case the control chamber unloading channel is opened; Fluid in the control chamber is discharged rapidly; Piston valve core slides along valve body thorax hole under the effect of pressure at two ends difference; The valve port that forms between spool and the annular shoulder will open rapidly that (1 ~ 2ms), fluid flows into the hydraulic actuator active chamber rapidly through the adjustable valve port in the pressure source.The adjustable restrictive valve band handle spool that is arranged between inlet channel and the piston valve core epicoele can be regulated the hydraulic actuator operating rate.
The present invention relies on quick unlatching moment of high-speed large-flow control gear to hydraulic actuator the motion of quantity of liquid driven plunger to be provided, and realizes that hydraulic pressure can be to the conversion of the moment of mechanical energy, thereby test for impact enough large impact energy is provided.Related high-speed large-flow control gear relies on the pilot pressure fluid to discharge rapidly, forms spool upper and lower cavity pressure difference, thereby with the bigger flow of less flow control, realizes the quick unlatching of big latus rectum spool.Especially in control flow rate during, and can change spool upper and lower cavity pressure area arbitrarily according to process conditions and designing requirement and change the spool opening speed, realize big flow control greater than the pressure fluid of 10000L/min.Adjustable restrictive valve can be regulated flow to control the actuator operating rate, and the relief circuit of hydraulic actuator setting realizes that the active chamber fluid pressure discharges rapidly to avoid the secondary collision of piston assembly vibration and test specimen.
Description of drawings
Fig. 1 is an embodiment of the invention structural representation.
Fig. 2 is the structural representation of piston valve core of the present invention.
Fig. 3 is a piston valve core structure A-A sectional view.
Among the figure: 1. test specimen, 2. percussive hammer, 3. piston rod, 4. backhaul chamber, 5. cylinder body, 6. piston, 7. active chamber; 8. basis, 9. servovalve, 10. pressure unloading valve, 11. valves that reset, 12. first buffers, 13. valve bodies; 14. control chamber, 15. annular grooves, 16. inlet channeles, 17. annular shoulders, 18. piston valve cores, 19. outlet passages; 20. the oil hydraulic cylinder inlet channel, 21. band handle spools, 22. oil pockets, 23. switch valves, 24. adjustable restrictive valves, 25. displacement transducers; 26. second buffer, 27. liquid-filling valves, 28. gas charging valves, 30. accumulators, 31. throttling passages, 32. throttle valve; 33. ring-shaped step, 34. bore holes, 35. throttle valve pistons, 36. unloading channels, 37. oil hydraulic cylinders, 38. high-speed large-flow control gear.
Embodiment
As shown in Figure 1; The present invention includes pressure source, high-speed large-flow control gear 38 and oil hydraulic cylinder 37; Accumulator 30 connects with high-speed large-flow control gear inlet channel 16, and oil hydraulic cylinder 37 connects with high-speed large-flow control gear outlet passage 19, and junction seals with anti-leak.Pressure source is that oil hydraulic cylinder 37 provides pressure fluid, high-speed large-flow control gear 38 control oil hydraulic cylinders 37 piston assembly movement velocitys.
Pressure source comprises accumulator 30, gas charging valve 28 and liquid-filling valve 27, and gas charging valve 28 is connected with accumulator 30 respectively with liquid-filling valve 27.
High-speed large-flow control gear 38 comprises valve body 13, piston valve core 18, adjustable restrictive valve 24, switch valve 23, pressure unloading valve 10, displacement transducer 25, the reset valve 11 and first buffer 12, and displacement transducer 25 is installed in adjustable restrictive valve 24 afterbodys.Piston valve core 18 can slide in valve body control chamber 14.When piston valve core 18 rests in 17 last times of annular shoulder, high-speed large-flow control gear 38 valves are in closed condition.Annular groove 15 in the valve body 13 communicates with inlet channel 16, and inlet channel 16 links to each other with accumulator 30.Between oil pocket 22 and outlet passage 19, be provided with an adjustable restrictive valve 24, control the flow of fluid through the position of adjustment band handle spool 21, thereby control the speed of percussive hammer 2.The throttle valve piston 35 of adjustable restrictive valve 24 can slide in bore hole 34, and band handle spool 21 nose shapes and its valve seat are adaptive.The relative position of band handle spool 21 heads and outlet passage 19 is controlled by the quantity of 35 liang of side liquids of throttle valve piston, reaches the purpose of flow control with this.Be provided with 12 pairs of piston valve cores 18 of a buffer in control chamber 14 bottoms and cushion, control chamber 14 links to each other with the valve 11 that resets with pressure unloading valve 10 through unloading channel 36.
Oil hydraulic cylinder 37 is made up of piston rod assembly, cylinder body 5, throttling passage 31, throttle valve 32, throttle valve 32 and unloading channel and servovalve 9, and piston 6 has been divided into active chamber 7 and backhaul chamber 4 with cylinder body 5 inner chambers, and the unloading channel of active chamber 7 connects with servovalve 9.Piston assembly can move reciprocatingly in cylinder body.Piston assembly is made up of piston 6, piston rod 3 and percussive hammer 2 mechanical coupling.Whole actuator cylinder body is installed on the basis 8.The throttle circuit of throttling passage 31 and throttle valve 32 compositions runs to end of travel to piston and plays buffer function, and the quick relief of unloading channel and servovalve 9 prevents the vibration of piston, and can adjust the initial position of piston 6.
Workflow of the present invention is:
(1) through being full of fluid in the 11 pairs of control chambers 14 of valve that reset piston valve core 18 is pressed in cut-out accumulator 30 and oil hydraulic cylinder 37 passages on the valve seat;
(2) carry out the initial position of topping up through 9 pairs of accelerating cavities of servovalve with adjustment piston 6;
(3) set band handle spool 21 initial positions through switch valve 23 and displacement transducer 25, with the top speed of control percussive hammer 2;
(4) through pressure and the fluid total volume of liquid-filling valve 27 with gas charging valve 28 adjustment accumulators 30;
(5) close the off-load servovalve 9 that links to each other with the active chamber 7 of oil hydraulic cylinder 37;
(6) open actuator backhaul chamber throttle valve 32;
(7) the breakout pressure unloading valve 10; Fluid in the control chamber 14 is discharged through unloading channel 36; Fluid in the accumulator 30 acts on through inlet channel 16 and ring-shaped step 33 on the surface of contact of spool 18 and annular shoulder 17, piston valve core 18 under the effect of upper and lower end pressure difference to lower slider up to bumping against buffer 12.The micro gap in case piston valve core 18 and annular shoulder 17 surface of contact split; Fluid flows into oil pocket 22 through the crack in the accumulator 30; Its pressure will act on the top of spool 18 and promote it and move downward rapidly, and the valve port that forms between piston valve core 18 and the annular shoulder 17 is meanwhile opened.Valve port is very short from being closed to the time of opening fully, approximately has only 1～2ms.
(8) after valve port was opened, the fluid in the accumulator 30 was entered in the active chamber 7 of oil hydraulic cylinder 37 by oil pocket 22, outlet passage 19 and inlet channel 20 under the effect of pressurized gas, promoted upwards accelerated motion bump test specimen 1 of piston 6 with given flow.Fluid in the backhaul chamber 4 is discharged by throttling passage 31.
(9) in the time of percussive hammer 2 bump test specimen 1, servovalve 9 is opened, and active chamber 7 inner fluids is drained, to prevent piston 6 repeated oscillation in cylinder body.
(10) close servovalve 9 and throttle valve 32 after piston 6 resets.
Claims (3)
1. high-speed large-flow valve control hydraulic pressure rate generator; It is characterized in that: comprise pressure source, high-speed large-flow control gear (38) and hydraulic actuator; Pressure source connects with high-speed large-flow control gear inlet channel (16); Hydraulic actuator connects with high-speed large-flow control gear outlet passage (19), and junction seals with anti-leak; Described high-speed large-flow control gear (38) comprises valve body (13), piston valve core (18), adjustable restrictive valve (24), switch valve (23), pressure unloading valve (10), displacement transducer (25), the valve that resets (11) and first buffer (12); Displacement transducer (25) is installed in adjustable restrictive valve (24) afterbody, and piston valve core (18) can slide in control chamber (14); Annular groove (15) in the valve body (13) communicates with inlet channel (16); Between oil pocket (22) and outlet passage (19), be provided with adjustable restrictive valve (24); The throttle valve piston (35) of adjustable restrictive valve (24) can slide in bore hole (34), and band handle spool (21) nose shape and its valve seat are adaptive; Be provided with first buffer (12) in control chamber (14) bottom piston valve core (18) is cushioned, control chamber (14) links to each other with the valve that resets (11) with pressure unloading valve (10) through unloading channel (36).
2. high-speed large-flow valve control hydraulic pressure rate generator according to claim 1; It is characterized in that: described pressure source comprises accumulator (30), gas charging valve (28) and liquid-filling valve (27), and gas charging valve (28) is connected with accumulator (30) respectively with liquid-filling valve (27).
3. high-speed large-flow valve control hydraulic pressure rate generator according to claim 1 and 2; It is characterized in that: described hydraulic actuator is oil hydraulic cylinder (37), comprises piston assembly, cylinder body (5), throttling passage (31), throttle valve (32) and unloading channel and servovalve (9); Piston (6) has been divided into active chamber (7) and backhaul chamber (4) with cylinder body (5) inner chamber, and the unloading channel of active chamber (7) connects with servovalve (9); Piston assembly can move reciprocatingly in cylinder body (5), and piston assembly is connected by piston (6), piston rod (3) and percussive hammer (2) and forms; Cylinder body (5) is installed on the basis (8); Throttling passage (31) and throttle valve (32) are formed throttle circuit.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010105439587A CN101975204B (en) | 2010-11-15 | 2010-11-15 | High-speed large-flow valve controlled hydraulic speed generator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010105439587A CN101975204B (en) | 2010-11-15 | 2010-11-15 | High-speed large-flow valve controlled hydraulic speed generator |
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| Publication Number | Publication Date |
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| CN101975204A CN101975204A (en) | 2011-02-16 |
| CN101975204B true CN101975204B (en) | 2012-11-07 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN2010105439587A Expired - Fee Related CN101975204B (en) | 2010-11-15 | 2010-11-15 | High-speed large-flow valve controlled hydraulic speed generator |
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Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103528826A (en) * | 2012-07-06 | 2014-01-22 | 重庆车辆检测研究院有限公司 | Detection device for commercial automobile protection |
| CN107478404A (en) * | 2017-09-18 | 2017-12-15 | 诏安县鹏达机械设计部 | A kind of high-speed overload hydraulic impact test device |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1065897A (en) * | 1992-05-09 | 1992-11-04 | 东北工学院 | Combined differential hydraulic pile hammer |
| DE19825726A1 (en) * | 1998-06-09 | 1999-12-30 | Schloemann Siemag Ag | Shock absorbing system works with reaction cylinder and reaction piston |
| CN101112719A (en) * | 2007-08-13 | 2008-01-30 | 淮阴工学院 | Hydraulic pressure type two station type sheller |
| DE102008016518A1 (en) * | 2008-03-31 | 2009-10-01 | Festo Ag & Co. Kg | Fluid actuated working cylinder |
| CN201858212U (en) * | 2010-11-15 | 2011-06-08 | 武汉理工大学 | High-speed large-flow valve controlled hydraulic speed generator |
-
2010
- 2010-11-15 CN CN2010105439587A patent/CN101975204B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1065897A (en) * | 1992-05-09 | 1992-11-04 | 东北工学院 | Combined differential hydraulic pile hammer |
| DE19825726A1 (en) * | 1998-06-09 | 1999-12-30 | Schloemann Siemag Ag | Shock absorbing system works with reaction cylinder and reaction piston |
| CN101112719A (en) * | 2007-08-13 | 2008-01-30 | 淮阴工学院 | Hydraulic pressure type two station type sheller |
| DE102008016518A1 (en) * | 2008-03-31 | 2009-10-01 | Festo Ag & Co. Kg | Fluid actuated working cylinder |
| CN201858212U (en) * | 2010-11-15 | 2011-06-08 | 武汉理工大学 | High-speed large-flow valve controlled hydraulic speed generator |
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| CN101975204A (en) | 2011-02-16 |
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