CN105179362A - Unbalance load-resisting servo oil cylinder - Google Patents
Unbalance load-resisting servo oil cylinder Download PDFInfo
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- CN105179362A CN105179362A CN201510552817.4A CN201510552817A CN105179362A CN 105179362 A CN105179362 A CN 105179362A CN 201510552817 A CN201510552817 A CN 201510552817A CN 105179362 A CN105179362 A CN 105179362A
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- cylinder
- hydrostatic bearing
- piston rod
- bearing body
- oil
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Abstract
The invention relates to an unbalance load-resisting servo oil cylinder, which comprises a cylinder barrel, a piston and a piston rod, and is characterized in that the piston is an inner hydrostatic bearing body which is fixedly arranged at the inner end part of the piston rod; an outer hydrostatic bearing body is fixedly arranged on the opening end of the cylinder barrel; the inner hydrostatic bearing body and an inner hole of the cylinder barrel form an inner hydrostatic bearing; and the outer hydrostatic bearing body and the external surface of the piston rod form an outer hydrostatic bearing. The unbalance load-resisting servo oil cylinder has the advantages that the response frequency is high; the walking precision is high; and meanwhile, a certain radial load can be borne, so that no metal friction occurs between the piston rod and the inner hole of the cylinder barrel.
Description
Technical field
The present invention relates to servo-cylinder, particularly can bear certain radial load and can ensure that the anti-bias load servo-cylinder of metal friction does not occur for piston rod and cylinder sleeve bore.
Background technique
Servo hydraulic cylinder, as a complete automatic controller, requires that it has higher response frequency, higher walking precision, longer working life etc. characteristic.Open type or Closed Hydraulic servo-control system is formed with Hydrauservo System (having servovalve or Proportional valve), displacement transducer, control software design etc.And the servo hydraulic cylinder important hydraulic element that are one of them.
The composition of Normal hydraulic cylinder is made up of cylinder barrel and cylinder sleeve, piston and piston rod, seal arrangement, damping device and venting gas appliance five part substantially.
Servo hydraulic cylinder is compared with Normal hydraulic cylinder, and fundamental composition is the same, but because the position of servo hydraulic cylinder, speed are by servo-hydraulic control, servo hydraulic cylinder does not generally need damping device.
For ensureing that servo hydraulic cylinder has higher response frequency, walking precision high, working life is longer again, and the machining accuracy of its part is higher, and dimensional accuracy, the behavior required precision of such as inner hole of cylinder are all high, generally all requires to reach body IT7-IT6.Normal hydraulic cylinder also cannot bear radial load simultaneously, and radial load is inevitable concerning servo hydraulic cylinder.Reason is that part processing necessarily exists error, servo hydraulic cylinder constantly changes speed in the process of walking simultaneously, acceleration is larger, at a lot of occasion transient acceleration more than 3g, once the self-aligning bearing of piston rod upper pin has little time adjustment position will produce unbalance loading, one has unbalance loading to produce radial load.
Summary of the invention
The object of this invention is to provide and a kind ofly can bear certain radial load and the anti-bias load servo-cylinder that metal friction does not occur for piston rod and cylinder sleeve bore, piston and inner hole of cylinder can be ensured.
Technical solution of the present invention is that anti-bias load servo-cylinder comprises cylinder barrel, piston, piston rod, described piston is interior hydrostatic bearing body, this interior hydrostatic bearing body is fixedly arranged in the inner end of piston rod, outer hydrostatic bearing body has been installed with at the opening end of cylinder barrel, interior hydrostatic bearing body and inner hole of cylinder form interior hydrostatic bearing, and outer hydrostatic bearing body and piston rod outer surface form outer hydrostatic bearing.
Above-described interior static pressure axis body and outer hydrostatic bearing body are respectively equipped with flow controller, and described flow controller is fixed restriction device or feedback throttle device.
The above fixed restriction device can be orifice restriction device, capillary restrictor or gap flow controller.
The above feedback throttle device can be guiding valve feedback throttle device or the membrane feedbacks the flow controller.
The opening end of cylinder barrel of the present invention has been installed with cylindrical shape cylinder sleeve, and the outer hydrostatic bearing body of ladder barrel shape to be located between cylinder sleeve and piston rod and to be installed with on cylinder sleeve.
Advantage of the present invention is that the existing higher response frequency of anti-bias load servo-cylinder has again higher walking precision, can bear certain radial load again simultaneously, ensures that piston rod and cylinder sleeve bore metal friction do not occur.Anti-bias load servo hydraulic cylinder can also improve the working life of rubber-plastic sealing ring.
Accompanying drawing explanation
Fig. 1 is organigram of the present invention;
Fig. 2 is outer hydrostatic bearing organigram of the present invention;
Fig. 3 is along C-C sectional view in Fig. 1;
Fig. 4 is one of the stressed principle schematic of piston rod of the present invention;
Fig. 5 is the two stressed principle schematic of piston rod of the present invention.
Embodiment
As shown in Figure 1, Figure 2, Figure 3 shows, anti-bias load servo-cylinder comprises cylinder barrel 1, piston, piston rod 3, described piston is interior hydrostatic bearing body 2, this interior hydrostatic bearing body 2 is fixedly mounted on the inner end of piston rod 3 with nut 16, outer hydrostatic bearing body 4 is installed with at the opening end of cylinder barrel 1, hydrostatic bearing in interior hydrostatic bearing body 2 forms with cylinder barrel 1 endoporus, outer hydrostatic bearing body 4 forms outer hydrostatic bearing with piston rod 3 outer surface.
Hydrostatic bearing body 4 is circumferentially processed with four oil pockets outside, interior hydrostatic bearing body 2 is circumferentially processed with two rows totally eight oil pockets.Be provided with a flow controller 5 in oil inlet hole on the bearing support that each oil pocket is corresponding, flow controller 5 is fixed restriction devices, also can use feedback throttle device.
The present invention's fixed restriction device 5 used is orifice restriction devices, also can use capillary restrictor or gap flow controller.
Flow controller 5 of the present invention also can use guiding valve feedback throttle device or the membrane feedbacks the flow controller.
The opening end of cylinder barrel 1 of the present invention is installed with cylindrical shape cylinder sleeve 6, and the outer hydrostatic bearing body 4 of ladder barrel shape is arranged between cylinder sleeve 6 and piston rod 3 and is also fixedly mounted on cylinder sleeve 6 with bolt 14.
In the body of rod of piston rod 3, be axially processed with oil transportation hole 7 and spill port 8 along it, one end of described oil transportation hole 7 and spill port 8 is connected with the oil inlet hole of interior hydrostatic bearing body 2 and spill port respectively.Described oil transportation hole 7 is connected with the fuel inlet fitting 9 on piston rod 3 outer end and back leakage connection 10 respectively with the other end of spill port 8.
The outer end of hydrostatic bearing body 4 is processed with oil inlet hole outside, is processed with spill port within it.The outer end of hydrostatic bearing body 4 is installed with fittings body 15 outside.Oil inlet hole on outer hydrostatic bearing body 4 is connected with the fuel inlet fitting 11 be fixedly mounted on fittings body 15, and described spill port is connected with the back leakage connection 12 on cylinder sleeve 6.
Cylinder sleeve 6 is separately installed with the closed end of cylinder barrel 1 the hydraulic oil joint 13 be connected with cylinder barrel 1 endoporus.
Self-aligning bearing 17 is separately installed with at the two end part of cylinder barrel 1.Fuel inlet fitting 9 is connected with reduction valve respectively with the filler opening of fuel inlet fitting 11.
From the oil supply system of oil cylinder through reduction valve, reduction valve outlet pressure is adjusted to Ps, 4 oil pocket symmetric designs, flow controller 5 is identical, adopt fixed restriction (such as orifice restriction device, capillary restrictor, gap flow controller etc.), also can adopt feedback throttle device (guiding valve feedback throttle device, the membrane feedbacks the flow controller etc.).Pressure oil produces Pressure Drop Δ P through flow controller 5, enters oil pocket, forms oil pocket pressure P r at oil pocket, flows into drainback passage, hydraulic return fuel tank through the gap of the sealing oil edge of oil pocket.Therefore following formula is set up:
Viscosity hydraulic oil flows through flow controller 5 can produce Pressure Drop Δ P, and the size of Δ P is relevant with the flow flowing through flow controller, and the flow in general flowing through flow controller 5 is larger, and Δ P is larger; The flow flowing through flow controller 5 is less, and Δ P is less.
3 powers of flow and gap that viscosity hydraulic oil flows through parallel flat gap are directly proportional.The gap of the sealing oil edge of oil pocket just can be considered as parallel flat gap.
As shown in Figure 2, Radial Loads is subject to when oil cylinder affects by unbalance loading, piston rod 3 offsets downward, the gap of the sealing oil edge of oil pocket 1 is changed Δ h, reduce to ho-Δ h by ho, the flow flowing to drainback passage from oil pocket 1 will reduce, and the flow flowing through flow controller 5 also just reduces, therefore Δ h1 also just reduces, and Pr1 just raises.Same analysis Pr3 just reduces, and the effective bearing area that (Pr1-Pr3) is multiplied by oil pocket just forms radial forces.Piston rod 3 is made still to be among oil film encirclement and not produce metal friction.
Walk because piston rod 3, piston are all in during oil film surrounds, and oil film can offset the machining error of a part of part, therefore the walking precision of piston rod 3, piston is improved.
The theory calculate of anti-bias load servo hydraulic cylinder
1, anti-bias load servo hydraulic cylinder is walked leftmost state, as shown in Figure 4
Our assumed condition is as follows:
The maximum load W=200000N of 1.1 oil hydraulic cylinders
1.2 maximum eccentricity L=0.5mm
1.3L1=1212mmL2=175mm
The moment M that the piston rod 3 caused due to unbalance loading must bear
1can be provided by following formula:
The stressing conditions of piston rod 3 as shown in Figure 5
At this radial force F
3effect lower piston rod 3 to while mobile, be easy to cause Sealing to damage.Even there is metal friction in piston rod 3 and outer hydrostatic bearing body 4 endoporus.
If the oil film of servo hydraulic cylinder of the present invention can bear this radial force, then piston rod 3 would not to mobile.Calculate oil film rigidity below:
Piston rod 3 diameter DD=80mm radius R=40mm=4cm
Width B B=D/1.5=60mm=6cm
Axial sealing oil edge C
1c
1=10mm=1cm
Circumference sealing oil edge b
1b
1=5.48mm=0.548cm
Oil pocket cornerite 2 θ
12 θ
1=70 ° of θ
1=35 °
Oil pocket axial length L L=60-2 × 10mm=4cm
Oil pocket degree of depth tt=3mm=0.3cm
Oil return groove width × dark=3mm × 3mm=0.3cm × 0.3cm
Radius clearance h
0h
0=0.05mm=0.005cm belongs to predetermined
Best Throttling ratio β β=1.71 of orifice restriction
Employing viscosity is the hydraulic oil of 40 centistokes(cst)s:
η
50℃=20×10
-8kg*s/cm
2ρ
50℃=8.36×10
-7kg*s
2/cm
4
Reduction valve outlet pressure PsPs=2.5MPa
From the flow Q that the sealing oil edge of oil pocket flows out
r
Flow through the flow Q of throttling pore
f
From the flow Q that the sealing oil edge of oil pocket flows out
rwith the flow Q flowing through throttling pore
fequal
I.e. Q
f=Q
r
5: ask hole diameter d
0h
0=0.005cm
Calculate oil film rigidity
The effective bearing area A of oil pocket
e
A
e=2R(L+C
1)sin(θ
1+θ
2)/2
θ in formula
1the half of oil pocket cornerite
θ
2oil pocket center line is to the angle on the limit of circumferential oil-return groove
This calculating θ
2=42.85 °
（θ
1+θ
2）/2=（35°+42.85°）/2=38.925°
Oil pocket axial length L=60-10 × 2=40=4cm
A
e=2×4×(4+1)×sin38.925°=25.132cm
2
(2) oil film rigidity J
The oil film rigidity J of mechanism design as shown in Figure 2 can be provided by following formula:
J=212N/μm
If charge oil pressure brings up to 5MPa, oil film rigidity J=424N/ μm
As long as the therefore mobile 2 μm of radial loads just enough born because unbalance loading causes of piston rod 3.Piston rod 3 is run at the approximate centerline of inner hole of cylinder all the time, and maximum deviation can not more than 2 μm.
The rubber-plastic sealing ring that oil hydraulic cylinder uses has a very common failure phenomenon, exactly when the gap of piston or piston rod 3 exceedes after certain value is called and extrudes gap, under the pressure effect of hydraulic oil, rubber-plastic sealing ring can be pressed against in gap and go, and causes rubber-plastic sealing ring to damage and loses efficacy.Piston rod 3 or piston all ensure that when manufacturing and designing gap can not exceed and extrude gap, but the effect of the radial force caused by unbalance loading, piston rod 3 or piston can be moved into, and make the gap of another side become large, can easily exceed and extrude gap.The working life of Sealing reduces greatly.Anti-bias load servo hydraulic cylinder can ensure that piston rod 3 or piston operate in approximate centerline, can improve the working life of rubber-plastic sealing ring, and the working life of oil hydraulic cylinder also improves greatly.
Claims (5)
1. anti-bias load servo-cylinder, comprise cylinder barrel, piston, piston rod, it is characterized in that described piston is interior hydrostatic bearing body, this interior hydrostatic bearing body is fixedly arranged in the inner end of piston rod, outer hydrostatic bearing body has been installed with at the opening end of cylinder barrel, interior hydrostatic bearing body and inner hole of cylinder form interior hydrostatic bearing, and outer hydrostatic bearing body and piston rod outer surface form outer hydrostatic bearing.
2. anti-bias load servo-cylinder as claimed in claim 1, it is characterized in that being respectively equipped with flow controller on interior static pressure axis body and outer hydrostatic bearing body, described flow controller is fixed restriction device or feedback throttle device.
3. anti-bias load servo-cylinder as claimed in claim 2, is characterized in that described fixed restriction device is orifice restriction device, capillary restrictor, or gap flow controller.
4. anti-bias load servo-cylinder as claimed in claim 2, is characterized in that described feedback throttle device is guiding valve feedback throttle device or the membrane feedbacks the flow controller.
5. anti-bias load servo-cylinder as claimed in claim 1, is characterized in that being installed with cylindrical shape cylinder sleeve at the opening end of cylinder barrel, and the outer hydrostatic bearing body of ladder barrel shape to be located between cylinder sleeve and piston rod and to be installed with on cylinder sleeve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510552817.4A CN105179362A (en) | 2015-09-02 | 2015-09-02 | Unbalance load-resisting servo oil cylinder |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510552817.4A CN105179362A (en) | 2015-09-02 | 2015-09-02 | Unbalance load-resisting servo oil cylinder |
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| Publication Number | Publication Date |
|---|---|
| CN105179362A true CN105179362A (en) | 2015-12-23 |
Family
ID=54901691
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|---|---|---|---|
| CN201510552817.4A Pending CN105179362A (en) | 2015-09-02 | 2015-09-02 | Unbalance load-resisting servo oil cylinder |
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|---|---|
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107989107A (en) * | 2017-10-31 | 2018-05-04 | 山东天瑞重工有限公司 | Hydraulic shock quartering hammer with fluid pressure support piston function |
| CN109611411A (en) * | 2018-12-29 | 2019-04-12 | 厦门理工学院 | A kind of high-speed overload actuator |
| CN110296122A (en) * | 2019-06-25 | 2019-10-01 | 同济大学 | A kind of movable frame posture hydraulic cylinder of resistance to unbalance loading |
| CN110307206A (en) * | 2019-06-21 | 2019-10-08 | 同济大学 | A kind of low internal leakage anti-bias load cylinder device |
| CN111396384A (en) * | 2020-04-08 | 2020-07-10 | 重庆凯瑞汽车试验设备开发有限公司 | Plug-in throttle valve group for pull rod type static pressure oil cylinder |
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| DE2301443A1 (en) * | 1973-01-12 | 1974-07-25 | Schenck Gmbh Carl | HYDRAULIC CYLINDER FOR A TESTING MACHINE OR TESTING SYSTEM |
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| CN203098449U (en) * | 2013-01-28 | 2013-07-31 | 上海朝田实业有限公司 | Static pressure suspension servo oil cylinder applied to hydraulic pump station |
| CN104632755A (en) * | 2014-12-31 | 2015-05-20 | 太原科技大学 | Anti-unbalance-loading overloading servo hydraulic cylinder |
| CN205001281U (en) * | 2015-09-02 | 2016-01-27 | 张响芝 | Anti unbalance loading servo cylinder |
-
2015
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Patent Citations (7)
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Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107989107A (en) * | 2017-10-31 | 2018-05-04 | 山东天瑞重工有限公司 | Hydraulic shock quartering hammer with fluid pressure support piston function |
| CN107989107B (en) * | 2017-10-31 | 2024-01-26 | 山东天瑞重工有限公司 | Hydraulic impact breaking hammer with hydrostatic pressure supporting piston function |
| CN109611411A (en) * | 2018-12-29 | 2019-04-12 | 厦门理工学院 | A kind of high-speed overload actuator |
| CN109611411B (en) * | 2018-12-29 | 2024-04-12 | 厦门理工学院 | High-speed heavy-load actuator |
| CN110307206A (en) * | 2019-06-21 | 2019-10-08 | 同济大学 | A kind of low internal leakage anti-bias load cylinder device |
| CN110296122A (en) * | 2019-06-25 | 2019-10-01 | 同济大学 | A kind of movable frame posture hydraulic cylinder of resistance to unbalance loading |
| CN111396384A (en) * | 2020-04-08 | 2020-07-10 | 重庆凯瑞汽车试验设备开发有限公司 | Plug-in throttle valve group for pull rod type static pressure oil cylinder |
| CN111396384B (en) * | 2020-04-08 | 2022-05-13 | 重庆凯瑞汽车试验设备开发有限公司 | Plug-in throttle valve group for pull rod type static pressure oil cylinder |
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Application publication date: 20151223 |
|
| RJ01 | Rejection of invention patent application after publication |