CN1032053A - High-frenquency hydraulic vibration pile driver - Google Patents
High-frenquency hydraulic vibration pile driver Download PDFInfo
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- CN1032053A CN1032053A CN 88105462 CN88105462A CN1032053A CN 1032053 A CN1032053 A CN 1032053A CN 88105462 CN88105462 CN 88105462 CN 88105462 A CN88105462 A CN 88105462A CN 1032053 A CN1032053 A CN 1032053A
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- Placing Or Removing Of Piles Or Sheet Piles, Or Accessories Thereof (AREA)
Abstract
High-frenquency hydraulic vibration pile driver belongs to construction machinery vibration piling.This pile driver is connected with cylinder body master body by outer control valve assembly and forms.Cylinder body inner carrier upper and lower cavity, about 2: 1 of the ratio of compression area in its chamber, and be provided with surge chamber, the inertia force that reciprocating motion of the pistons is produced obtains buffering at stop, reduces and impacts and noise.In the counterweight casing, be provided with high pressure accumulator,, absorb the buffer-braking energy, reduce the pumping source consumption, a low pressure accumulator also is set, in order to average low pressure oil return flow in order to the flow of average pump.The present invention has simple in structure, and technological requirement is low, and hydraulic braking is impacted for a short time, and noise is little, the characteristics that efficient is high.
Description
The invention belongs to construction machinery vibration piling.
Diesel hammer is because the exhaust emission environment, noise, the shortcoming that vibration is big, and use is restricted, and various countries greatly develop vibropiling.Present widely used vibro driver is that the Motor Drive eccentric block forms vibration, and for well, but owing to the restriction that is subjected to the antivibration ability of motor and power transmission bearing, its frequency can only reach 600～1000 times/minute (10～17Hz) to its performance than diesel hammer.Occurred the imagination and the research of high-frequency hydraulic hammer in recent years, its frequency can reach 20～60Hz, and this has improved the piling performance greatly, is subject to people's attention, and the form of high-frequency hydraulic hammer has multiple, wherein is preferably Russian Patent SU1142597A.It is to utilize small plunger control internal spool valve, thereby control oil cylinder and piston produce relative motion, form dither, owing to do not have power transmission bearing and motor antivibration problem, thereby frequency can improve, but there is following problem in this patent, and its application is restricted.
1, owing to use the control of valve piston internal valve, cause complex structure, the technological requirement height, difficult in maintenance.
2, oil cylinder piston and internal valve use the spacing braking of mechanical block, and this rigidity braking is impacted big, and noise is big, and the life-span is short.
3, do not have accumulator, thereby pumping source power is big, efficient is low, and heating is big, and the oil return resistance is big, and it is big that Great Wall Software's bore is wanted.
4, because internal valve is controlled, and the centre has stock to pass through, the internal valve diameter is bigger, makes valve motion flow also big, causes power dissipation.
The objective of the invention is to design that a kind of outer valve control type, frequency height, noise are little, little to foundation vibration, consuming little energy, simple in structure, cost is low, frequency modulation high-frequency hydraulic hammer easily.
The present invention is by two most of compositions.Main body of being made up of cylinder body, cylinder sleeve, piston, cylinder cap and the outer control valve assembly of being made up of main valve stem, main valve housing, pilot stem, guide valve bushing, valve body, both are integral with screw attachment.Main valve stem is connected with connecting rod with piston moves back and forth both synchronously.Piston, cylinder sleeve, cylinder part; Cylinder sleeve inlays in cylinder body, and piston is reciprocating in cylinder sleeve.The cylinder sleeve upper and lower is provided with piston upper chamber and piston cavity of resorption, about 2: 1 of the ratio of its chamber inner carrier compression area.On the lower end casing wall of the upper end of piston upper chamber casing wall and piston cavity of resorption, be provided with surge chamber, the inertia force that reciprocating motion of the pistons is produced obtains buffering at stop, reduces and impacts and noise.The junction plate on cylinder body top and ballast box body and function screw connect with cylinder body.The counterweight casing is matched according to the size of pile driver tonnage.For the flow of average pump, absorb the buffer-braking energy, be provided with high pressure accumulator, by oil duct respectively with piston upper chamber and piston cavity of resorption UNICOM.For same purpose, also be provided with a low pressure accumulator, in order to average low pressure oil return flow.Be provided with sealing device in the cylinder sleeve top and bottom, sealed, prevent piston upper chamber and piston cavity of resorption hydraulic oil seepage with O shape circle and sliding sleeve.The piston lower end is threaded one and connects dish, connects dish and connects with anchor clamps.The valve body part; Main valve stem, main valve housing and pilot stem, guide valve bushing are embedded in respectively in the valve body, and main valve stem and pilot stem are reciprocating in valve pocket respectively, and the valve gap of both upper and lower sides tightens up with screw and valve body.The two ends of pilot stem respectively are provided with a surge chamber, make pilot stem and whole the reciprocating motion play cushioning effect.Whole valve body connects in aggregates with screw with cylinder body.Adopt this structure design, have the following advantages:
1, owing to adopt outer valve control, make simple in structurely, technological requirement is low, and cost is low, and maintaining is convenient, and Great Wall Software's pipe needs only 2;
2, adopt hydraulic braking, impact for a short time, noise is little, thereby long service life;
3, be provided with the high-low pressure accumulator, make the pumping source energy consumption little, the efficient height, it is little to generate heat, and the oil return resistance is little;
4, (20～60Hz), frequency modulation is convenient for the frequency height.
Description of drawings:
Fig. 1 is the principal section view.
Fig. 1-1 is the cross section view of bowing.
Fig. 1-2 is a left side view.
Fig. 2 is connecting rod ASSY figure, is tightened up with screw-nut 30b and packing ring 30d by connecting rod cap 30a and connecting rod shank 30c, constitutes connecting rod ASSY 30.
Fig. 3 constitutes sealing device for O shape circle and sliding sleeve assembling schematic diagram respectively by O shape circle 6,15,23 and sliding sleeve 7,16,24.O shape snare is in the sliding sleeve outside, and sliding sleeve is enclosed within on the axle, and both are embedded in the seal groove.
Fig. 4 is a fundamental diagram.
Hydraulic oil enters oil inlet P, always communicates with pilot valve annular groove 60,59,56, main valve annular groove 66 and piston cavity of resorption 46 by the pipeline oil circuit.Oil return opening O communicates with pilot valve annular groove 57,54, chamber 62,51, main valve annular groove 63 respectively.Oil inlet P links to each other with the high-low pressure of pumping source respectively with two Great Wall Software's pipes with oil return opening O, to form high-low circuit.Shown position at Fig. 4, piston upper chamber 45 and pilot valve annular groove 55,58 communicate, and annular groove 55,58 is communicated with to get up with pilot valve annular groove 54,57, then be communicated with oil return opening O, piston upper chamber 45 is a low pressure in this case, and piston cavity of resorption 46 is high pressure, cylinder body 22 relative piston 20 under the hydraulic oil effect moves downward, by oil column and piston 20 effects, stake is formed one upwards make a concerted effort, stake is moved upward.Because main valve stem 4 is connected with piston 20, the also relative valve body 32 of main valve stem 4 is moved downward, in case main valve stem 4 moves to main valve annular groove 66 and 65 is linked up, when annular groove 64 and 63 was closed, pilot valve annular groove 53 promptly communicated with high pressure.About 2: 1 of the ratio of the compression area of pilot stem 34 in the pilot valve annular groove 53 and 60.Like this,, make pilot valve annular groove 53 high-low pressures alternately, order about pilot stem 34 and move back and forth commutation by the reciprocating motion of main valve stem 4.Therefore, pilot stem 34 is under the high pressure effect of pilot valve annular groove 53, and commutation moves upward.Pilot valve annular groove 54,55,57,58 is closed gradually, and pilot valve annular groove 55 and 56,58 and 59 open gradually, when the face of cylinder, pilot stem 34 upper end enters pilot valve chamber 62, chamber 62 forms oil closed cavity, make pilot stem 34 top pressurizeds be closed the fluid braking gradually up to stop, commutation finishes, and plays non-rigid buffer-braking effect.At this moment, piston upper chamber 45 changes into high pressure by low pressure, and piston 20 upper end cylinder endless belt 44 enter the surge chamber 43 on the cylinder body 22 simultaneously, forms oil closed cavity, and makes cylinder body 22 be subjected to oil pressure effect buffer-braking up to stop, and cylinder body 22 upward strokes finish.Because piston upper and lower cavity 45 and 46 all is high pressure at this moment, but the piston compression area differs one times, because the ratio of piston upper chamber compression area and piston cavity of resorption compression area is about 2: 1, pressure differs one times, thereby cylinder body 22 relative piston 20 under piston upper chamber 45 oil pressure effects moves upward, effect by oil column and piston 20 produces downward making a concerted effort to stake, and stake is moved downward.When 20 times cylinder endless belt 47 of piston enter cylinder body 22 surge chambers 48, form oil closed cavity, cylinder body 22 is promptly braked up to stop by oleo cushion, and cylinder body 22 upward strokes finish.At this moment, the also relative valve body 32 of main valve stem 4 moves downward, and main valve annular groove 65 and 66 is closed again, and making main valve annular groove 64 and 63 reopen (position as shown in Figure 2), pilot stem 34 restarts commutation, cylinder body 22 relative pistons 20 move upward, and repeat to begin second stroke again.Under the high low oil pressure effect of oil inlet P and oil return opening O, cylinder body 22 relative pistons 20 will be not reciprocating not left alone without helply, thereby produce high frequency piling power, and stake is sunk, and finishes piling work.Because the oil sources supply is a steady state value, and the motion process of cylinder body 22 be quicken-at the uniform velocity-slow down, like this, require flow just non-constant, for this reason, be provided with accumulator 36,37,38, store by high pressure accumulator 37,38, with balanced energy, accumulator 36 is oil-return accumulator, to absorb oil return flow pulsation, reduce the diameter of low pressure oil return Great Wall Software pipe.
Fig. 1,1-1,1-2 are a structure enforcement figure of the present invention.
Form cylinder body master body by cylinder body 22, cylinder sleeve 19, piston 20, cylinder cover 17, cylinder body lower cover 21.Cylinder sleeve 19 is embedded in the cylinder body 22, studs with cushion collar 18 between cylinder sleeve 19 and cylinder body 22, and piston 20 is reciprocating in cylinder sleeve 19, and the cylinder sleeve upper and lower is provided with piston upper chamber 45 and piston cavity of resorption 46, about 2: 1 of the ratio of its chamber inner carrier compression area.At the cylinder sleeve 19 of piston upper chamber 45, the drainback passage that cylinder body 22 places have oil return opening O, same at the cylinder sleeve 19 of piston cavity of resorption 46, the oil inlet passage that cylinder body 22 places have oil inlet P.On the lower end casing wall of the upper end of piston upper chamber 45 casing wall and piston cavity of resorption 46, be provided with surge chamber 43,48, the inertia force that reciprocating motion of the pistons is produced obtains buffer-braking at stop, reduces and impacts and noise.Cylinder cover 17 usefulness screws and cylinder body 22 tighten up, and are provided with drain pan 42 and seal groove 41 in the cylinder cover 17, and O shape circle 16 and sliding sleeve 17 are embedded in the seal groove, constitute sealing device, and compress with gland 14, put dust ring 13.Also be provided with drain pan 49 and seal groove 50 in the cylinder body lower cover 21, O shape circle 23 and sliding sleeve 24 are embedded in the seal groove, constitute sealing device, be set in the cylinder body lower cover 21 with gland 25, put dust ring 26, cover compressing tablet 27, then cylinder body lower cover 21 and compressing tablet 27 usefulness screws and cylinder body 22 are tightened up.By valve body 32, valve pocket 2, main valve housing 3, main valve stem 4, main valve loam cake 1, main valve lower cover 5, guide valve bushing 33, pilot stem 34, pilot valve loam cake 35, pilot valve lower cover 31 constitute outer control valve assembly, and whole valve body connects to tighten up with cylinder body 22 with screw and is integral.Valve pocket 2, main valve housing 3 are embedded in the valve body 32, and valve pocket 2 upper ends are tightened up by main valve loam cake 1 usefulness screw and valve body 32.Main valve lower cover 5 is provided with seal groove, and O shape circle 6 and sliding sleeve 7 are embedded in wherein, and with gland 8, compressing tablet 9 compresses, and puts dust ring 10, then main valve lower cover 5 usefulness screws and valve body 32 is tightened up.Main valve stem 4 is reciprocating in valve pocket 2, main valve housing 3, main valve stem 4 lower ends are connected with connecting rod 30 with piston 20 lower ends, and the wrist-pin end of connecting rod recess is embedded in the main valve stem 4 lower end grooves, and connecting rod tip is inlaid in the groove of piston lower end, and rotatable, both move back and forth synchronously to make main valve stem 4 and piston 20.Main valve stem 4, main valve housing 3 have oil groove 63,64,65,66 and oil inlet and oil return road.Guide valve bushing 33 also is embedded in the valve body 32, and guide valve bushing 33 top and bottom are tightened up by pilot valve loam cake 35, pilot valve lower cover 31 usefulness screws and valve body 32.The two ends of pilot stem 34 respectively are provided with a surge chamber 61,52, make pilot stem and whole the reciprocating motion play cushioning effect.Pilot stem 34, guide valve bushing 33 have oil groove 53,54 equally, and 55,56,57,58,59,60 and the oil inlet and oil return road.Counterweight casing 11 is rinsed 1 and is matched according to the size of pile driver tonnage with the solid a large bamboo or straw hat with a concial crown, broard brim and handle wash with watercolours of screw is impossible by junction plate 12 and whole cylinder body top.For the flow of average pump, absorb the buffer-braking energy, be provided with two high pressure accumulators 37,338, use oil duct and piston upper chamber 45 and piston cavity of resorption 46 UNICOMs respectively.For same purpose, also be provided with a low pressure accumulator 36, in order to average low pressure oil return flow, and with low pressure oil duct UNICOM.Piston 20 lower ends are threaded one and connect dish 28, and with pressing plate 29 and screw lock, connect dish 28 usefulness bolts and connect pile driver of formation with anchor clamps.
Claims (5)
1, high-frenquency hydraulic vibration pile driver belongs to construction machinery vibration piling, comprises cylinder body, cylinder sleeve, cylinder cover, cylinder body lower cover, valve rod, valve pocket, connect dish, counterweight casing, junction plate, oil-in and oil return opening and oil duct, it is characterized in that: by valve body 32, valve pocket 2, main valve housing 3, main valve stem 4, main valve loam cake 1, main valve lower cover 5, guide valve bushing 33, pilot stem 34, pilot valve loam cake 35, pilot valve lower cover 31 constitute outer control valve assembly, and whole valve body is connected into one with screw and cylinder body 22; Stud with cushion collar 18 between cylinder sleeve 19 and the cylinder body 22, cylinder sleeve 19 upper and lowers are provided with piston upper chamber 45 and piston cavity of resorption 46, about 2: 1 of the ratio of its chamber inner carrier compression area; On the casing wall of the upper end of piston upper chamber 45, be provided with surge chamber 43, also be provided with surge chamber 48 on the lower end casing wall of piston cavity of resorption 46; Be provided with drain pan 42 and seal groove 41 in the cylinder cover 17, O shape circle 16 and sliding sleeve 17 are embedded in the seal groove 41, constitute sealing device, also are provided with drain pan 49 and seal groove 50 in the cylinder body lower cover 21, and O shape circle 23 and sliding sleeve 24 are embedded in the seal groove 50, constitute sealing device; Be provided with high pressure accumulator 37,38 and low pressure accumulator 36 in the counterweight casing on top, piston upper chamber 45 and piston cavity of resorption 46 are used oil duct and high pressure accumulator 37,38 UNICOMs respectively, low pressure accumulator 36 and low pressure oil duct UNICOM; Main valve stem 4 lower ends are connected with connecting rod 30 with piston 20 lower ends.
2, pile driver according to claim 1 is characterized in that: described connecting rod ASSY 30, by connecting rod cap 30a, connecting rod shank 30c, form with screw-nut 30b and packing ring 30d, wrist-pin end of connecting rod is the forked type structure.
3, pile driver according to claim 1, it is characterized in that: valve pocket 2, main valve housing 3 are embedded in the valve body 32, main valve stem 4 is embedded in valve pocket 2, the main valve housing 3, can move back and forth, main valve housing 3, main valve stem 4 have oil groove 63,64,65,66 and oil inlet and oil return road, valve pocket 2 upper ends are tightened up by main valve loam cake 1 usefulness screw and valve body 32, main valve lower cover 5 is provided with seal groove, O shape circle 6 and sliding sleeve 7 are embedded in wherein, and compress with gland 8, compressing tablet 9, put dust ring 10, then main valve lower cover 5 usefulness screws and valve body 32 are tightened up.
4, pile driver according to claim 3, it is characterized in that: guide valve bushing 33 and pilot stem 34 are embedded in the valve body 32, pilot stem 4 is embedded in the guide valve bushing 33, can move back and forth, guide valve bushing 33 and pilot stem 34 have oil groove 53,54,55,56,57,58,59,60 and oil inlet and oil return road, guide valve bushing 33 top and bottom are by pilot valve loam cake 35, and pilot valve lower cover 31 usefulness screws and valve body 32 tighten up.
5, pile driver according to claim 4 is characterized in that: respectively be provided with a surge chamber 61,52 between the two ends of pilot stem 34 and the guide valve bushing 33.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN88105462.3A CN1004088B (en) | 1988-01-21 | 1988-01-21 | High-frequency hydraulic vibration pile driver |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN88105462.3A CN1004088B (en) | 1988-01-21 | 1988-01-21 | High-frequency hydraulic vibration pile driver |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1032053A true CN1032053A (en) | 1989-03-29 |
| CN1004088B CN1004088B (en) | 1989-05-03 |
Family
ID=4833651
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN88105462.3A Expired CN1004088B (en) | 1988-01-21 | 1988-01-21 | High-frequency hydraulic vibration pile driver |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1004088B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102864778A (en) * | 2012-09-11 | 2013-01-09 | 同济大学 | Hydraulic system for hydraulic pile hammer |
| CN104289545A (en) * | 2014-09-23 | 2015-01-21 | 浙江工业大学 | Electric liquid type fluttering platform used for cold extruding vibration machining |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1049002C (en) * | 1995-11-14 | 2000-02-02 | 北京元朝飞翔科技贸易公司 | Multipurpose metal surface caring agent and preparing process thereof |
| CN1078240C (en) * | 1997-09-25 | 2002-01-23 | 中国科学院兰州化学物理研究所 | High-low-temp. extreme-pressure resisting special lubricant |
-
1988
- 1988-01-21 CN CN88105462.3A patent/CN1004088B/en not_active Expired
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102864778A (en) * | 2012-09-11 | 2013-01-09 | 同济大学 | Hydraulic system for hydraulic pile hammer |
| CN104289545A (en) * | 2014-09-23 | 2015-01-21 | 浙江工业大学 | Electric liquid type fluttering platform used for cold extruding vibration machining |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1004088B (en) | 1989-05-03 |
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