CN201908899U - Oil cylinder for static pressure vibration exciter - Google Patents
Oil cylinder for static pressure vibration exciter Download PDFInfo
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- CN201908899U CN201908899U CN2011200065582U CN201120006558U CN201908899U CN 201908899 U CN201908899 U CN 201908899U CN 2011200065582 U CN2011200065582 U CN 2011200065582U CN 201120006558 U CN201120006558 U CN 201120006558U CN 201908899 U CN201908899 U CN 201908899U
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- 230000003068 static effect Effects 0.000 title claims abstract description 28
- 230000002706 hydrostatic effect Effects 0.000 claims abstract description 80
- 238000007789 sealing Methods 0.000 claims description 22
- 230000007704 transition Effects 0.000 claims description 3
- 230000000694 effects Effects 0.000 description 8
- 239000012530 fluid Substances 0.000 description 8
- 239000007788 liquid Substances 0.000 description 8
- 230000008859 change Effects 0.000 description 5
- 230000001105 regulatory effect Effects 0.000 description 4
- 230000009471 action Effects 0.000 description 3
- 239000000314 lubricant Substances 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- VEMKTZHHVJILDY-UHFFFAOYSA-N resmethrin Chemical compound CC1(C)C(C=C(C)C)C1C(=O)OCC1=COC(CC=2C=CC=CC=2)=C1 VEMKTZHHVJILDY-UHFFFAOYSA-N 0.000 description 3
- 238000013016 damping Methods 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 230000002411 adverse Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 239000002828 fuel tank Substances 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000005272 metallurgy Methods 0.000 description 1
- 229920000642 polymer Polymers 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
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Abstract
本实用新型公开一种静压激振器油缸，其活塞两端各固定连接一个活塞杆，各活塞杆伸出缸筒的内腔；静压轴承横截面呈圆环形，静压轴承外壁沿轴向间隔设有环形外油槽，静压轴承内壁沿轴向设有环形内油槽，各环形外油槽对应地与一个环形内油槽通过第一通孔连通；端盖沿轴向设有第二通孔；活塞杆各自对应地贯穿一个静压轴承，静压轴承各自与一个端盖固定连接，缸筒两端分别置于对应端盖的第二通孔的大孔内，两端盖间通过锁紧螺栓固定连接；各端盖壳体上设有进油孔和对应出油孔，相邻两个环形外油槽中的一个环形外油槽与对应的所述进油孔连通，另一个环形外油槽与对应的所述出油孔连通。本实用新型可抵抗较大侧向力，且减少活塞与静压轴承之间的摩擦。
The utility model discloses a static pressure vibration exciter oil cylinder, the two ends of the piston are fixedly connected with a piston rod, and each piston rod protrudes from the inner chamber of the cylinder barrel; the cross section of the static pressure bearing is circular, and the outer wall of the static pressure bearing is along the There are annular outer oil grooves at intervals in the axial direction, and the inner wall of the static pressure bearing is provided with annular inner oil grooves in the axial direction. Each annular outer oil groove communicates with an annular inner oil groove through the first through hole; holes; the piston rods respectively pass through a hydrostatic bearing, and the hydrostatic bearings are respectively fixedly connected with an end cover. The bolts are fixedly connected; each end cover housing is provided with an oil inlet hole and a corresponding oil outlet hole, one of the two adjacent annular outer oil grooves is connected to the corresponding oil inlet hole, and the other annular outer oil groove communicate with the corresponding oil outlet hole. The utility model can resist relatively large lateral force and reduce the friction between the piston and the static pressure bearing.
Description
Technical field
The utility model relates to a kind of static pressure vibration exciter oil cylinder, can be widely used in single-degree-of-freedom and multi-freedom degree hydraulic vibration gen field, and at some Aerospace Products and metallurgy industry relevant application is arranged also simultaneously.
Background technique
Common servo vibration exciting device oil cylinder extensive use in hydraulic vibration gen, for ultra-high frequency high thrust hydraulic vibration gen, the piston of vibration exciter oil cylinder and piston rod are done the high speed to-and-fro motion together, also to bear bigger lateral force simultaneously, make the friction of piston, piston rod and oil cylinder casing wall and sealing aggravate, the hydraulic system leakage quantity that leaks increases, and therefore tests poor repeatability.Chinese patent CN11877140A discloses a kind of hydraulic cylinder with static pressure support guide, it is that inwall with hydrostatic bearing has four rectangle oil pockets, and have 4 oil-return grooves vertically, therefore after fluid enters oil pocket, oil sealing surface and radially oil sealing surface oil return simultaneously vertically, form the oil film of certain rigidity, this design can reduce friction to a certain extent, but because there is radially oil return in this design, when the to-and-fro motion of piston rod high frequency, there is the phenomenon of scurrying oil between each oil pocket, the phenomenon of turbulent flow appears in fluid motion, so the piston rod lateral force resistance reduces greatly, " seize " phenomenon also might occur, thereby the damage oil cylinder can not satisfy the requirement of high frequency high thrust multi-freedom degree hydraulic vibration gen.Development along with high frequency high thrust multi-freedom degree hydraulic vibration gen, the vibration system control accuracy requires more and more higher, requirement to servo vibration exciting device oil cylinder lateral force resistance is more and more higher, and the utility model can satisfy the requirement that realizes minimum friction of oil cylinder and big lateral force resistance.So far, domestic yet there are no adopted this hydrostatic bearing Structures under Hydrostatic Pressure vibration exciter oil cylinder.
The model utility content
Technical problem to be solved in the utility model provides a kind of larger side of resisting to power and reduce the static pressure vibration exciter oil cylinder of the frictional force between hydrostatic bearing and the piston significantly.
The technical scheme in the invention for solving the technical problem is: this static pressure vibration exciter oil cylinder comprises cylinder barrel and places the piston of the inner chamber of cylinder barrel, the two ends of described piston respectively are fixedly connected with a piston rod, described each piston rod stretches out the inner chamber of described cylinder barrel, in addition, also comprise lock bolt, a pair of hydrostatic bearing and a pair of end cap, the cross section of described hydrostatic bearing is ring, the outside of the wall of described hydrostatic bearing is interval with annular outer oil sump more than two vertically, the inboard of the wall of described hydrostatic bearing is interval with annular inner oil sump more than two vertically accordingly, and each annular outer oil sump is communicated with by first through hole on the wall that is arranged at described hydrostatic bearing with an annular inner oil sump accordingly; Described end cap is provided with second through hole vertically, and described second through hole cross section vertically is stepped; Described piston rod runs through a described hydrostatic bearing separately accordingly and forms Spielpassung mutually, described hydrostatic bearing is fixedlyed connected with a described end cap separately, described hydrostatic bearing places in the aperture of second through hole of corresponding end cap separately and forms transition fit mutually, the two ends of described cylinder barrel place in the macropore of second through hole of corresponding end cap respectively and form sealing mutually and support, and the formation cavity forms Spielpassung mutually so that described piston can be moved to by the inner chamber of cylinder barrel in this cavity and with this cavity between the mesopore of described piston rod and second through hole of corresponding end cap; Fixedly connected between two described end caps by lock bolt; The housing of described each end cap is provided with oil inlet hole and corresponding oil outlet, annular outer oil sump in every adjacent two annular outer oil sumps and corresponding described oil inlet hole connection, another annular outer oil sump and corresponding described oil outlet connection.
Further, first through hole that is used to be communicated with each annular outer oil sump and corresponding annular inner oil sump described in the utility model has two, and these two first through holes become 90 ° of angles along the circumferencial direction of described hydrostatic bearing.
Further, oil inlet hole described in the utility model is a capillary restrictor.
Compared with prior art, the beneficial effects of the utility model are: (1) the utility model is because the inboard of the wall of hydrostatic bearing is provided with annular inner oil sump more than two vertically, between two adjacent annular inner oil sumps, form axial oil sealing surface structure thus, avoid forming radially oil sealing surface, thereby prevent to cause the phenomenon of turbulent flow because of the fluid crossfire of each annular inner oil sump.In addition; axially the formed high pressure oil of oil sealing surface structure makes each the utility model static pressure vibration exciter oil cylinder on the hydraulic vibration gen can resist the lateral force that influences each other and produced each other; the system that has protected each static pressure vibration exciter oil cylinder and hydraulic vibration gen to be constituted, and improve the stability of this system greatly.Simultaneously, because hydrostatic bearing of the present utility model can be provided with a plurality of annular inner oil sumps vertically, therefore can increase the group number of inner oil sump easily vertically, thereby improve lateral force resistance to the static pressure oil cylinder, realize the Flexible Production and the processing of the utility model static pressure vibration exciter oil cylinder, and the utility model static pressure vibration exciter cylinder structure compactness, exquisiteness.When axially the formed high pressure oil of oil sealing surface structure makes the oil cylinder proper functioning, the lubricant oil that is pumped between hydrostatic bearing and the piston separates certain interval, so the friction between hydrostatic bearing and the piston belongs to the neat liquid friction, surface friction drag is minimum, power consumpiton is little, vibration efficiency is high, the Waveshape reproduction effect of hydraulic vibration gen, precision stability is good and the oil cylinder life-span is long.(2) hydrostatic bearing adopts " second throttle " (promptly earlier through the oil inlet hole throttling in the utility model, pass through the annular outer oil sump of hydrostatic bearing again) structure, reduced the particularly size of end cap part of vibration exciter oil cylinder greatly, simultaneously since piston float that the pressure that is to rely on external oil realizes, therefore, under various vibration frequencies, all have advantages of high bearing capacity, frequency change is little to the oil film rigidity influence.Axially the structrural build up high pressure oil of oil sealing surface has the good resistance to shock and the effect of compensating error, can reduce the adverse effect that piston and hydrostatic bearing bring because of self foozle.(3) the axial oil sealing surface structure of hydrostatic bearing of the present utility model can make hydrostatic bearing satisfy the requirement of underloading to heavily loaded various machinery at aspects such as bearing capacity, oil film rigidity, temperature rises.
Description of drawings
The utility model is described in further detail below in conjunction with accompanying drawing.
Fig. 1 is the structure cross-sectional schematic of the utility model static pressure vibration exciter oil cylinder.
Fig. 2 is the profile schematic representation of the utility model static pressure vibration exciter oil cylinder.
Fig. 3 is the structural representation of end cap in the utility model.
Fig. 4 is the structure cross-sectional schematic of end cap in the utility model.
Fig. 5 is the profile schematic representation of hydrostatic bearing in the utility model.
Fig. 6 is the structure cross-sectional schematic of hydrostatic bearing in the utility model.
Fig. 7 is the A-A sectional view of Fig. 1.
Embodiment
Below in conjunction with accompanying drawing the utility model is done detailed elaboration.
To shown in Figure 7, the utility model static pressure vibration exciter oil cylinder comprises cylinder barrel 5 and places the piston 2 of the inner chamber of cylinder barrel as Fig. 1.Adopt two seals between cylinder bucket 5 and the piston 2, can significantly improve sealing effect.The two ends of piston 2 respectively are fixedly connected with a piston rod 11 and piston rod 12, and piston rod 11 is fixedlyed connected with piston 2 respectively threadably with piston rod 12, and piston rod 11, piston rod 12 stretch out the inner chamber of cylinder barrel 5 separately.Hydrostatic bearing 31 is fixedlyed connected with end cap 41 with bolt 182 by bolt 181; Hydrostatic bearing 32 is fixedlyed connected with end cap 42 with bolt 184 by bolt 183.As shown in Figure 5, the cross section of hydrostatic bearing 31, hydrostatic bearing 32 is ring, the outside of the wall of hydrostatic bearing 31 and hydrostatic bearing 32 is provided with four annular outer oil sumps 121,122,123,124 vertically, wherein annular outer oil sump 121,123 is an oil-feed tank, also have the effect of flow controller simultaneously, thereby reduced the particularly size of end cap 41,42 of vibration exciter oil cylinder greatly; Annular outer oil sump 122,124 is an oil-return groove, and annular outer oil sump 122,124 is communicated with oil outlet 171,172,175,176 on the end cap 41, and wherein, each oil outlet is as the passage of oil return.The inboard of the wall of hydrostatic bearing 31 and hydrostatic bearing 32 is provided with four annular inner oil sumps 151,152,153,154 vertically accordingly, between two adjacent annular inner oil sumps, form axial oil sealing surface structure 131,132,133,134 thus, avoid forming radially oil sealing surface, thereby prevent to cause the phenomenon of turbulent flow because of the fluid crossfire of each annular inner oil sump.Enter into Inner oil groove 152,154 and form the high pressure oil films from the lubricant oil of oil inlet hole 71,72,75,76 annular outer oil sump 122,124, make piston rod 11 float by oil sealing surface structure 131,132,133,134 by hydrostatic bearing 31; Enter into Inner oil groove 152,154 and form the high pressure oil films from the lubricant oil of oil inlet hole 73,74,77,78 annular outer oil sump 122,124, make that piston rod 12 floats by axial oil sealing surface structure 131,132,133,134 by hydrostatic bearing 32.Therefore, hydrostatic bearing 41,42 belongs to the neat liquid friction with friction between the corresponding piston rod 11,12, surface friction drag is minimum.In addition, as shown in Figure 5 and Figure 6, annular outer oil sump 121 and annular inner oil sump 154 are by first through hole 114 on the wall that is arranged at hydrostatic bearing, 118 are communicated with, annular outer oil sump 122 and annular inner oil sump 153 are by first through hole 113 on the wall that is arranged at hydrostatic bearing, 117 are communicated with, annular outer oil sump 123 and annular inner oil sump 152 are by first through hole 112 on the wall that is arranged at hydrostatic bearing, 116 are communicated with, annular outer oil sump 124 and annular inner oil sump 151 are by first through hole 111 on the wall that is arranged at hydrostatic bearing, 115 are communicated with, wherein, first through hole 112,114,116,118 are used for oil-feed, first through hole 111,113,115,117 are used for oil return.Need to prove, be used to be communicated with each annular outer oil sump and can have only one with first through hole of corresponding annular inner oil sump.
Shown in Fig. 1,3,4, it is stepped that end cap 41,42 all is provided with second through hole, 10, the second through hole 10 cross sections vertically vertically, makes second through hole 10 be presented the structure of macropore 83, mesopore 81, aperture 85 successively by end to end.Piston rod 11 and 12 is corresponding respectively to be run through hydrostatic bearing 31,32 and forms Spielpassung mutually with corresponding hydrostatic bearing, the oil clearance 16 that this gap just forms during static pressure vibration exciter oil cylinder proper functioning.Hydrostatic bearing 31 is fixedlyed connected by bolt 181,182 with end cap 41, and hydrostatic bearing 32 is fixedlyed connected by bolt 183,184 with end cap 42.Hydrostatic bearing 31 places in the inwall of aperture 85 of second through hole 10 of end cap 41, and the inwall of the outer wall of hydrostatic bearing 31 and aperture 85 forms transition fit.The two ends of cylinder barrel 5 place respectively in the macropore 83 of second through hole 10 of end cap 41,42 and form sealing with the inwall of macropore 83 and support.In addition, between the mesopore 81 of second through hole 10 of piston rod 11 and end cap 41, form cavity so that piston 2 can be moved to by the inner chamber of cylinder barrel 5 cavity 81 in and with the cavity 81 mutual Spielpassung that form.End cap 41 is fixedlyed connected by lock bolt 612,634 with end cap 42, thereby compact structure, stressed even.
Have oil inlet hole 71,72,75,76 and oil outlet 171,172,175,176 on the housing of end cap 41; Having oil inlet hole 73,74,77,78 and oil outlet on the housing of end cap 42 is 173,174,177,178.As shown in Figure 4, oil inlet hole 72 on the end cap 41, oil outlet 175, oil inlet hole 71, oil outlet 176 axially distribute successively along end cap 41, equally, oil inlet hole 75, oil outlet 171, oil inlet hole 76, oil outlet 172 axially distribute successively along end cap 41, form the structure that oil inlet hole and oil outlet are interspersed thus.As shown in Figure 2, form the structure that is interspersed too between the oil inlet hole on the end cap 42 77,78,73,74 and the corresponding oil outlet 177,178,173,174.
Wherein, as shown in Figure 6, oil inlet hole 72,76 is communicated with the annular outer oil sump 121 of hydrostatic bearing, and oil inlet hole 71,75 is communicated with the annular outer oil sump 123 of hydrostatic bearing 31; Oil outlet 172,176 is communicated with annular outer oil sump 122, and oil outlet 171,175 is communicated with annular outer oil sump 124.Annular outer oil sump 121, annular outer oil sump 122, annular outer oil sump 123, annular outer oil sump 124 are adjacent successively.In addition, as shown in Figure 5, be used to be communicated with the annular outer oil sump 121 of hydrostatic bearing and first through hole of annular inner oil sump 154 has two, be respectively first through hole 114, first through hole 118, and first through hole, 114,118 circumferencial directions along hydrostatic bearing become 90 ° of angles.Each oil inlet hole of end cap 41 and end cap 42 plays the effect of capillary restrictor, and certainly, each oil inlet hole also can directly use capillary restrictor to substitute.Flow controller is the important devices in the hydrodynamic journal liquid polymers system, it is the same just as the resistive element in the circuitry, because it has certain liquid flow damping, thereby feasible pressure oil from oil pump produces pressure and falls, play the regulating action of pressure oil, for level pressure oil feeding type hydrostatic bearing, bearing arrangement must have compensating element, and the oil liquid pressure in the bearing oil pocket can be regulated along with the variation of extraneous load.
Shown in Fig. 1 to 6, working procedure of the present utility model is as follows: from the oil of the certain pressure of oil pump through oil inlet hole 71,72,75,76 flow into the annular outer oil sump 121 of hydrostatic bearing 31,123, and by first through hole 121,123,114,112 enter annular Inner oil groove 154,152, and by axial oil sealing surface structure 131,132,133,134 float piston rod 11, then by annular Inner oil groove 151,153 by first through hole 115,117,111,113 flow out to outer oil sump 122,124, at last by the oil outlet 171 on the end cap 41,172,175,176 flow back to fuel tank, and this moment, pressure was zero.Do not have radially oil sealing surface owing to hydrostatic bearing only adopts axial oil sealing surface structure 131,132,133,134, can prevent fluid crossfire radially, avoid causing the phenomenon of turbulent flow, make static pressure vibration exciter oil cylinder have advantages of excellent stability.The utility model static pressure vibration exciter oil cylinder goes out rod type for two, therefore is furnished with hydrostatic bearing 41,42 at the oil cylinder two ends respectively, has strengthened the ability of oil cylinder lateral force resistance greatly.
As shown in Figure 5 and Figure 6, as preferred implementation of the present utility model, first through hole, 114,118 circumferencial directions along hydrostatic bearing become 90 ° of angles, and first through hole 114,118 is as oil-feed herein; And first through hole, 113,117 circumferencial directions along hydrostatic bearing become 90 ° of angles, and first through hole 113,117 is as fuel-displaced herein.First through hole 114,118 circumferencial directions along hydrostatic bearing become the 90 ° of angles and first through hole 113,117 circumferencial directions along hydrostatic bearing become 90 ° purpose to be: improve hydrostatic bearing 31 oil films and set up speed, simultaneously by rotation hydrostatic bearing 31, changed the annular outer oil sump 121 of throttling action, 123 arc length, thereby change the resistance of oil-feed liquid, improved the stability of vibration exciter oil cylinder, simultaneously, in order to improve static pressure vibration exciter oil cylinder lateral force resistance, can be at hydrostatic bearing 31,32 outer walls and inwall increase the outer oil sump number in couples, inner oil sump number, and corresponding with it oil inlet hole and fuel-displaced hole count on the end cap.The main purpose that the outer wall of hydrostatic bearing is provided with annular outer oil sump 121,123 is that the fluid that flows into oil pocket is played throttling, both can fit into the effect that oilhole 71,72,75,76 plays pressure regulation, play throttling action owing to annular outer oil sump 121,123 simultaneously, thereby can reduce the size of vibration exciter cylinder cover greatly.According to the difference (for example being step load or pulsating cyclic load) of the disaster-stricken situation of oil cylinder piston, can increase the quantity of annular inner oil sump at the inwall of hydrostatic bearing 31,32, the quantity of annular inner oil sump can be odd number or even number.For the multi-freedom degree hydraulic vibration gen, the utility model static pressure vibration exciter oil cylinder adopts two hydrostatic bearings 31,32 to support, and can satisfy the needs of the stability of a system and control accuracy, can make simple in structurely again, and process industrial art performance is good.
As Fig. 1, Fig. 2, shown in Figure 7, under the situation of ignoring the piston rod deadweight, when bearing level plus load W left, piston rod 11 does the time spent, piston rod 11 just moves the distance of e along the direction of load W, if there is gap 16 in piston 11 with hydrostatic bearing 31 when zero load, then behind the plus load W, the gap 16 on the oil pocket left side reduces and gap 16 increases on the right.The place that gap 16 reduces, the fluid flow just reduces, and resistance increases, and oil pressure increases; The place that gap 16 increases, the fluid flow just increases, and resistance reduces, and oil pressure just descends.Suppose that the oil inlet hole 71,72,75,76 that leads to each oil pocket is all identical, be that the liquid flow damping is identical, input pressure is also identical, then owing to bearing the gap variation that external load takes place, the pressure of the left side oil pocket of annular inner oil sump 154,152 is increased, the pressure of annular inner oil sump 154,152 right side oil pockets is reduced.Produce on so axial oil sealing surface 131,132,133,134 left to the right the active force of pressure difference on loaded area just in time with external load W balance, so piston 11 is fixed up on a new position.According to the job requirement of piston 11, often wish the pressure difference that oil pressure produced on the axial oil sealing surface structure 131,132,133,134, the external load of must balance bearing can keep piston to be unlikely to produce bigger displacement again.But in actual conditions, constant external load is actually rare, and particularly in vibration exciter, external load changes mostly within the specific limits.In order to satisfy above-mentioned hope, this can change with the variation of external load with regard to the oil pressure that requires each annular inner oil sump 152,154, thereby the oil pressure that guarantees each oil pocket can change with the variation of external load, and annular outer oil sump 121,123 of the present utility model has been exactly this effect.Simultaneously, can regulate the relative position of the annular outer oil sump 121,123 of the inlet of oil inlet hole 71,72,75,76 and hydrostatic bearing 31 by rotation hydrostatic bearing 31, so that regulated the arc length length of the annular outer oil sump of throttling action, thereby change total liquid resistance of oil-feed, can improve the dynamic characteristic (for example stability, accuracy, rapidity) of oil film according to the convenient pressure of regulating oil film of the stand under load situation of static pressure vibration exciter oil cylinder.The utility model static pressure vibration exciter oil cylinder lateral force resistance ability is strong, and the frictional force between piston 11,12 and the hydrostatic bearing 31,32 is minimum, is convenient to the multi-freedom degree hydraulic vibration gen is accurately controlled.Simultaneously, this static pressure vibration exciter cylinder structure is simple, has reduced the difficulty of machining, and compact structure can satisfy the demand of various hydraulic vibration gen.
Claims (3)
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| Application Number | Priority Date | Filing Date | Title |
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| CN2011200065582U CN201908899U (en) | 2011-01-11 | 2011-01-11 | Oil cylinder for static pressure vibration exciter |
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| Application Number | Priority Date | Filing Date | Title |
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| CN2011200065582U CN201908899U (en) | 2011-01-11 | 2011-01-11 | Oil cylinder for static pressure vibration exciter |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102042281A (en) * | 2011-01-11 | 2011-05-04 | 浙江大学 | Oil cylinder of static pressure vibration exciter |
| CN102287423A (en) * | 2011-08-11 | 2011-12-21 | 浙江大学 | Outflow-type micro-stoke double-acting exciting hydraulic cylinder |
| CN102305227A (en) * | 2011-08-11 | 2012-01-04 | 浙江大学 | Micro-stroke double-action vibration-exciting hydraulic cylinder |
| CN104035127A (en) * | 2014-06-04 | 2014-09-10 | 同济大学 | SDOF (single degree of freedom) vibrating table testing device |
| CN104747520A (en) * | 2015-03-20 | 2015-07-01 | 辽东学院 | Hydraulic shock excitation rotation reversing valve |
| CN109723701A (en) * | 2017-10-27 | 2019-05-07 | 北京精密机电控制设备研究所 | A small volume cavity oil source pressure pulsation excitation device |
-
2011
- 2011-01-11 CN CN2011200065582U patent/CN201908899U/en not_active Expired - Lifetime
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102042281A (en) * | 2011-01-11 | 2011-05-04 | 浙江大学 | Oil cylinder of static pressure vibration exciter |
| CN102042281B (en) * | 2011-01-11 | 2012-12-12 | 浙江大学 | Oil cylinder of static pressure vibration exciter |
| CN102287423A (en) * | 2011-08-11 | 2011-12-21 | 浙江大学 | Outflow-type micro-stoke double-acting exciting hydraulic cylinder |
| CN102305227A (en) * | 2011-08-11 | 2012-01-04 | 浙江大学 | Micro-stroke double-action vibration-exciting hydraulic cylinder |
| CN102287423B (en) * | 2011-08-11 | 2013-09-18 | 浙江大学 | Outflow-type micro-stoke double-acting exciting hydraulic cylinder |
| CN102305227B (en) * | 2011-08-11 | 2013-10-23 | 浙江大学 | A micro-stroke double-acting excitation hydraulic cylinder |
| CN104035127A (en) * | 2014-06-04 | 2014-09-10 | 同济大学 | SDOF (single degree of freedom) vibrating table testing device |
| CN104747520A (en) * | 2015-03-20 | 2015-07-01 | 辽东学院 | Hydraulic shock excitation rotation reversing valve |
| CN104747520B (en) * | 2015-03-20 | 2017-11-28 | 辽东学院 | Hydraulic exciting rotates reversal valve |
| CN109723701A (en) * | 2017-10-27 | 2019-05-07 | 北京精密机电控制设备研究所 | A small volume cavity oil source pressure pulsation excitation device |
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| C14 | Grant of patent or utility model | ||
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| AV01 | Patent right actively abandoned |
Granted publication date: 20110727 Effective date of abandoning: 20130306 |
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| RGAV | Abandon patent right to avoid regrant |