CN2537848Y - Double plunger hydraulic hammer - Google Patents
Double plunger hydraulic hammer Download PDFInfo
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- CN2537848Y CN2537848Y CN 02223944 CN02223944U CN2537848Y CN 2537848 Y CN2537848 Y CN 2537848Y CN 02223944 CN02223944 CN 02223944 CN 02223944 U CN02223944 U CN 02223944U CN 2537848 Y CN2537848 Y CN 2537848Y
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Abstract
The utility model belongs to drilling machinery and forging (punching) device technology field, which relates to the double-plunger hydraulic hammer. The double-plunger hydraulic hammer comprises a machine frame seat, an ascending double-plunger cylinder, and an undershot double-plunger cylinder, the oil path of the hydraulic oil path controlling device is respectively connected with the ascending double-plunger cylinder and the undershot double-plunger cylinder, the plunger area of the actuation of the hydraulic oil to the undershot double-plunger cylinder is larger that the plunger actuation area of the ascending double-plunger cylinder, and the lower parts of the ascending double-plunger cylinder, and the undershot double-plunger cylinder are connected with the hammer head through connecting bodies. The utility model can be used as the double-plunger hydraulic driving hammer or the double-plunger hydraulic forging hammer, which is used in the drilling machinery and forging (punching) devices, and the utility model can be applied in the technology and device of the compaction of the roads and dams through engineering machinery. The operation of the utility model is simple, the automatization degree is high, the working efficiency is high, the structure is simple, the manufacture cost and the maintenance cost can be reduced by about 70 percent compared with the similar products in foreign countries.
Description
Technical field
The utility model belongs to piling machinery and the equipment class technical field is pressed in forging (dashing), relates to a kind of double-plunger hydraulic hammer.
Background technique
Build in high-rise building, highway and the engineerings such as railroad bridge, port and pier, reservoir dam, heavy factory building, subsurface construction and oil development, all need solid foundation.The basis, support and enclose engineering construction such as dinner and all need piling machinery.Use the hydraulic hammer of hydraulic shock technology, be applicable to all kinds of soil layers and a stake type, can carry out operation, have the ability of beating straight stake and taper pile various reinforced concrete piles, steel sheet pile, shaped steel stake etc.; The no exhaust emission pollution of working endangers, and noise is all less with vibration.Because the weight ratio diesel hammer of hydraulic hammer is heavy, thereby make a face obtain bigger pile penetration, piling efficient height (generally high by 40～50% than steam hammer and diesel hammer work efficiency) is according to the hammering energy and the frequency of intensity regulated at will (control) pile monkey of soil property situation and pile material, the precision height of piling; Can also in the piling process, obtain the pile monkey impact force with the variation that adapts to the stratum with obtain the penetration resistance index.The performance that can guarantee impact energy does not damage pile body again, also can determine whether stake gets to predetermined soil layer by penetration resistance.
Abroad, as the existing hydraulic pile hammer product of minority developed countries such as Holland, Finland, Germany, Japan, hydraulic hammer all adopts the stepped piston principle.Its working portion is an airtight impact cylinder body.Top in cylinder body is full of hydraulic oil, and the centre is full of inert gas (nitrogen); There is a floating piston that oil and nitrogen are separated between oil and the nitrogen.Inferior part of the cylinder block is equipped with a piston, and its tailpiece of the piston rod fixed impacts head.This structure is very complicated, and seal request is very high between oil, gas, and manufacturing technology requires height, costs an arm and a leg.Modern hydraulic shock technology is towards high pressure, and small flow develops; Under the certain operating mode of the gross mass of hammer, impact stroke size decision impact energy size.It is little and impact stroke is long to impact cylinder diameter, and it is just big more that its cylinder diameter is carried out super accurately machined manufacturing technology difficulty, and the sealing problem between oil, gas is just bigger, and this is the main cause that product is hammered in China's aneroid piling still at present into shape.
Traditional forging equipment has the almost of steaming hammer and pneumatics hammer all to belong to the product that is eliminated.20th century, late nineteen eighties replaced by the hydraulic forging hammer of little tonnage level the sixth of the twelve Earthly Branches, its product structure complexity, and manufacturing technology requires high, costs an arm and a leg, and develops and applies slowly.Middle nineteen nineties.First 8MN of China (800 tons) rapid forge machine is heard generation, but the complicated manufacturing technology difficulty of its device structure is big, and (700～8,000,000 yuan/the platform cover) cost an arm and a leg.This patent " the double-plunger hydraulic forging hammer " simple in structurely tightly to play, manufacturing technology is easy to solve, and hammer rating is changeable, and cost is low, is widely used, and is easy to promote.
Summary of the invention
Technical problem to be solved in the utility model is to adopt the differential principle of double-plunger area difference, providing a kind of simple in structurely tightly plays, inner wall of cylinder is not processed, and only plunger outer diameter is carried out superfinish, thereby solves the double-plunger hydraulic hammer of the big problem of manufacturing technology difficulty.Because no piston, axially (back and forth linear velocity 5～8 meter per seconds) sealing.China's Wellendichtring has become series product, and back and forth linear velocity reaches 5～15 meter per seconds, can satisfy seal request fully.
The technological scheme that solution the utility model technical problem is adopted is that this double-plunger hydraulic hammer comprises frame seat, rising twin columns plug cylinder, following to the twin columns plug cylinder, the oil circuit of hydraulic circuit control device is respectively with rising twin columns plug cylinder, be connected towards the twin columns plug cylinder down, towards the plunger active area of the twin columns plug cylinder plunger active area greater than rising twin columns plug cylinder, rising twin columns plug cylinder, the bottom towards the twin columns plug cylinder connects tup by connecting body to hydraulic oil pressure down to down.
The utility model double-plunger hydraulic hammer belongs to double action and impacts liquid hammer; After hammer rose to assigned altitute by hydraulic pressure installation, under the differential action of pressure oil, hammer was with greater than a g (g=9.8 meter per second
2) acceleration impact downwards, the kinetic energy of impact is very big.What external modern liquid hammer adopted is stepped piston (oil cylinder) principle, and the utility model employing is differential and double plunger (oil cylinder) principle.Since hydraulic hammer work in the impact process be greater than a g acceleration movement, piston or plunger to-and-fro motion linear velocity are up to 4～8 meter per seconds, and be more much higher than general hydraulic equipment.High like this active line speed is high especially to the manufacturing technology and the seal request of oil hydraulic cylinder.External liquid hammer adopts piston and floating piston, must carry out super precision processing to inner wall of cylinder (deep and long hole), even adopt modern high-precision, sharp deep hole processing equipment, and the also difficult requirement of guaranteeing the precision and the surface roughness of its endoporus; For adopting the floating piston technology, also must adopt floating piston and inner wall of cylinder pairing abrasive process during manufacturing, can guarantee the strict seal request of isolating of oil and nitrogen; The fretting wear that piston and the relative movement of inner wall of cylinder high speed produce reduces the sealability aggravation.So manufacture cost and maintenance cost height.The utility model has been cancelled piston and has been adopted the double-plunger oil cylinder; Inner wall of cylinder to double-plunger is not processed, and need only carry out super precision processing to the cylindrical of double-plunger, and its process equipment adopts high-precision cylindrical grinder just to polish to foreign round can reach technical requirements.Because no piston only need adopt the axle seal element, China has working pressure 45MPa, back and forth linear velocity reaches 10～15 meter per seconds series Wellendichtring, can satisfy seal request of the present utility model, therefore fully, manufacture cost of the present utility model is compared and can be reduced about 70% with external like product with maintenance cost.
Description of drawings
Below in conjunction with embodiment's accompanying drawing the utility model is described in further detail
Fig. 1 is that the utility model is as the hydraulic pile hammer structural representation
Fig. 2 is the partial top view among Fig. 1
Fig. 3 hammers structural representation for the utility model into shape as hydrostatic forging
Fig. 4 is the plan view of Fig. 3
Fig. 5 is hydraulic circuit control device () structural drawing
Fig. 6 is hydraulic circuit control device (a two) structural drawing
Fig. 7, Fig. 8 are the electric control schematic diagram of hydraulic pile hammer
Among the figure: 1A, 1B-hydraulic pumping unit 2A, 2B-electromagnetic relief valve 3A, 3B-one-way valve 4A, 45-unloading electromagnetic valve, 5-pilot-actuated valve, 6- short valve 8A, 8B- high pressure accumulator 9A, 9B-low pressure accumulator 10-down towards double-plunger oil cylinder 11-rising double-plunger oil cylinder 12-frame seat (outstanding seat) 13-connecting body, 14-tup 15A, 15B-fuel tank 16-break 17-elevator oil hydraulic motor 18-1-equilibrium valve 18-2-one-way throttle valve 19-three position four-way electromagnetic valve 20-two-position four-way solenoid valve 21-stake positional cylinder 22-stake 23-pile cover 24-tracking signal (JN
2) limited signal (JN under the 26-hammering of 25-hydraulic circuit control device () control box
1) 27-servo-actuated cable, pulley, balladeur train 28-static pulley group 29-multistage assembled frame overhead section 30-multistage assembled frame intermediate section (multistage) 31-outstanding seat lifting wire rope 32-outstanding seat upper saw pulley 33-counterweight wire rope 34-pile cover upper saw pulley 35-accent gradient support 36-counterweight, 37-multistage assembled frame underlying section 38-support, 39-hydraulic circuit control device (two) control box 40-traveller 41-electric control box 42-assembled frame supporting free bearing 43-guide rail 44-anvil 45-electric control box D
0, D
1-Pilot operated check valve D
2-one-way valve M-motor DT-d, d
0, d
1-plunger outer diameter
Embodiment
Here the utility model embodiment of Jie Shaoing is two, the one, the double-plunger hydraulic pile hammer, the 2nd, double-plunger hydraulic forging hammer, both hydraulic control devices have all adopted hydraulic circuit control device () as shown in Figure 5, and hydraulic pile hammer also has hydraulic circuit control device (two) as shown in Figure 6.Below these two embodiments are introduced respectively.
One, double-plunger hydraulic pile hammer
This double-plunger hydraulic pile hammer comprises movable part, standing part, hydraulic circuit control device part, circuit control device part.
Movable part is mounted on the frame seat 12 (in the present embodiment, because frame seat 12 is to hang under the static pulley of standing part, so be called outstanding seat 12 again), remove rising twin columns plug cylinder 11 (2) is arranged, down towards twin columns plug cylinder 10 (2), outside hydraulic circuit control device () control box 25, connecting body 13, the tup 14, also have high pressure accumulator 8A and low pressure accumulator 9A, the tracking signal (JN of hydraulic circuit
2) device 24, limited signal (JN under the hammering
1) device 26, servo-actuated cable (containing power line, guide line)/balladeur train 27, an outstanding seat upper saw pulley 32 (2).Hammer be by connecting body 13 with top two under be connected with two rising twin columns plug cylinders 11 again with following tup 14 towards twin columns plug cylinder 10 and be connected, the three is fixed to be holistic general name.Three's quality sum is the gross mass of hammer.Movable part also comprises pile cover 23, the pile cover upper saw pulley 34 (4) that is worn in the stake 22.
Standing part is mounted on the support 38, and critical piece has: static pulley group 28 (each 2 groups of elevator, counterweights), multistage assembled frame overhead section 29, multistage assembled frame intermediate section 30, outstanding seat lifting wire rope 31, counterweight wire rope 33, accent gradient support 35 (are used for batter piling and transfer draft angle), counterweight 36, multistage assembled frame underlying section 37, hydraulic circuit control device (two) control box 39, electric control box 41, assembled frame supporting free bearing 42 (2), the guide rail 43 of seat (12) hanged in elevator oil hydraulic motor 17, stake positional cylinder 21 (2), traction.The traveller 40 that also has support pedestal 38.
The hydraulic circuit control device part is made up of with (two) two live hydraulic systems of hydraulic circuit control device of stake positional cylinder (21) control double-plunger oil cylinder rising twin columns plug cylinders (11), following hydraulic circuit control device () and the tracking of control set a distance towards twin columns plug cylinder (10).Hydraulic circuit control device (one) control box 25 places on the outstanding seat 12 of servo-actuated; Hydraulic circuit control device (two) control box 39 places fixedly on the support 38.All there is independently hydraulic power unit in two systems, hydraulic actuator, hydraulic control component and auxiliary device.Electric controlling then adopts two systems shared, realizes centralized control, and electric control box 41 places on the fixing support 38.Two live hydraulic systems are all established independently hydraulic power unit.Each pumping plant provides hydraulic power by the permanent power and variable pump of motoring for system separately respectively.Outstanding seat 12 inner chambers of servo-actuated are hydraulic circuit control device (one's) fuel tank; Fixing support 38 inner chambers are hydraulic circuit control device (twos') fuel tank.
The core component of double-plunger hydraulic hammer is by down towards double-plunger oil cylinder 10 and rising double-plunger oil cylinder 11 totally four hydraulic actuators that the double-plunger oil cylinder constitutes; The center of its four plunger cases all with the center of tup 14 symmetry (seeing that Fig. 2, Fig. 4 overlook) one by one.Wherein: down towards totally two of double-plunger oil cylinders 10, the upper end plunger outer diameter is d
1, the lower end plunger outer diameter is d
0, its active area is: A
10=π (d
0 2-d
2 1)/4, totally two of rising double-plunger oil cylinders 11 (backhaul), the upper end plunger outer diameter is d
0, the lower end plunger outer diameter is d, its active area is A
11=π (d
0 2-d
2)/4; If d
0＞d＞d
1, and d and d
1The phase difference is very little; So A
10＞A
11(see figure 5) during instantly towards double-plunger oil cylinder 10 and rising double-plunger oil cylinder 11 formation differential circuits, its differential area is Δ A=A
10-A
11=π (d
2-d
1 2)/4; Obviously, Δ A value is very little.Under the 10 pressure oil effects of double-plunger oil cylinder, hammer will be to be a bit larger tham a g (g=9.8 meter per second following
2) acceleration impact downwards, again because the differential area of Δ A is very little, though the flow that this moment, pump was supplied with is little, the impact final velocity of hammer is very big, if the gross mass of hammer is bigger, then the kinetic energy of Chong Jiing is very big.
Hydraulic pressure stake positional cylinder 21 totally two be used for a positional cylinder, cylinder piston locating basis of wonderful works stake slightly wherein.17 2 kinds of purposes of elevator oil hydraulic motor: an is used for outstanding seat 12 and keeps set a distance to follow the tracks of with pile cover 23.In the piling work cycle, when hammering blow pile cover 23, it is dark that soil layer h is promptly sunk in stake, and former set a distance promptly differs the h value between outstanding seat 12 and the pile cover 23; If do not eliminate this difference automatically, will reduce the h value to the given impact stroke of next round work cycle, tup 14 just can't be hammered onto pile cover 23.The tracking technique that the utility model adopts can solve and sink to soil layer h when dark, and the realization oil hydraulic motor is clockwise, and frame seat promptly moves down the h value automatically fast, thereby eliminates this difference automatically, guarantees that frame seat and pile cover keep set a distance in automatic working cycle.The second, be used for fast lifting frame seat and pile cover to predetermined altitude, be the preceding preparation of driving piles.
Hydraulic control component: hydraulic circuit control device (), referring to Fig. 5: electromagnetic relief valve 2A:1DT outage, relief valve is opened, and comes the hydraulic oil of self-pumping directly to flow back to case through this valve; During the 1DT energising, relief valve works, and the pressure in feasible system loop is regulated and element protection.One-way valve 3A: prevent that hydraulic oil from flowing to its left end from the one-way valve right-hand member.Solenoid valve 4A is unloading valve: 2DT outage, this opening of valves, and oil circuit is connected fuel tank, hydraulic oil in the delivery system loop; System loads: 2DT energising, this valve cuts out, and system is in loaded state.Pilot operated check valve D
0, D
1: and two valve parallel connections, shunting is by the flow of short valve 6.One-way valve D
2: be used under the equal off-position of electromagnet of all solenoid valves, rising twin columns plug cylinder 11 inner chambers are in air-tight state, and lock glides because of deadweight toward hammer, realize that hammer reliably stops at arbitrary position.Solenoid directional control valve 5 is a pilot-actuated valve, is used for controlling short valve 6 and realizes commutation fast.The 3DT outage, the spool of short valve 6 moves to upper, and its upper end is connected with high tension loop, and lower end and low tension loop are connected; When short valve 6 was in state of equilibrium, high pressure oil one tunnel directly entered down towards cylinder 10 through short valve 6, and another road is through one-way valve D
2Enter rising cylinder 11, constitute differential circuit towards cylinder 10 and upper punch cylinder 11 down; Under the pressure oil effect, because A
10＞A
11, the oil of rising cylinder 11 is by Pilot operated check valve D
1Conflux fast in descending, hammer is impacted downwards with the acceleration that is a bit larger tham a g towards cylinder 10.When 3DT switches on, short valve 6 commutations, spool moves to the next, and the pressure oil of pump and high pressure accumulator 8A is through one-way valve D
2Pressure oil is provided for rising cylinder 11; Down towards 10 in cylinder by short valve 6 and Pilot operated check valve D
0Two passes link to each other oil circuit mesolow accumulator 9A absorption portion return pressure oil with the low pressure oil circuit.Hydraulic circuit control device (two), referring to Fig. 6: solenoid directional control valve 19 is controlled electro-hydraulic reversing valve for the guide; Be mainly used in the tracking that realizes that outstanding seat 12 and pile cover 23 keep set a distance.When 4DT switched on, elevator oil hydraulic motor 17 was clockwise fast, and outstanding seat promptly moves down the tracking pile cover fast, 4DT outage when outstanding seat reaches to set a distance with pile cover, and break 16 brakes, outstanding seat promptly is parked in given location.When 5DT switched on, elevator oil hydraulic motor 17 middling speeds reversed, and outstanding seat and pile cover make the 5DT outage when being risen to predetermined altitude by middling speed, break 16 brakes, outstanding seat and pile cover promptly rest on predetermined altitude, are the piling solenoid directional control valve 20 of preparing, and are used to control the location (centering) of 21 pairs of stakes of oil cylinder.The 6DT outage, positioning work piece original position (returning releasing orientation); During the 6DT energising, two positioning work pieces are held location (centering) state near realizing to pile holder in opposite directions fast.
Main auxiliary device: high pressure accumulator 8A and low pressure accumulator 9A.In the work cycle of double-plunger hydraulic hammer, required changes in flow rate is bigger, and the impact that system produces is also bigger; Therefore, must adopt accumulator to regulate.Hammer impacts downwards and is with the acceleration movement of being a bit larger tham a g, needs the flow of confession ascending, and high pressure accumulator 8A stores from the unnecessary pressure oil of oil hydraulic pump, promptly deposits excess energy.In the process of hammer rising (backhaul), need a large amount of pressure oil; At this moment, not only supply with rising double-plunger oil cylinder 11 from the hydraulic oil of oil hydraulic pump, high pressure accumulator 8A also discharges the pressure oil that stores simultaneously and gives rising double-plunger oil cylinder 11, has improved rising (backhaul) speed of hammer, has saved energy.After short valve 6 commutated fast, when hammer began to rise, a large amount of hydraulic oil was from flowing back to fuel tank towards double-plunger oil cylinder 10 down, and system produces surge pressure, utilizes pressure surge in the low pressure accumulator 9A absorption circuit, reduces pressure peak.Low pressure accumulator 9A absorbs in the hammer uphill process from following partial pressure oil towards double-plunger oil cylinder 10; In the downward impact process of hammer, then discharge its energy stored.
Hydraulic work principle (referring to Fig. 5 and Fig. 6):
Pump startup-under the equal off-position of electromagnet 1DT, the 11DT of relief valve, start the drive motor of two hydraulic system oil hydraulic pumps respectively, making pump is to start operation under zero the state at oil pressure relief; The system Maximum operating pressure sets up and safety protection-at 1DT,, under the 1DT "on" position, set up the electromagnetic relief valve 2A of two hydraulic systems and the Maximum operating pressure of 2B respectively; Behind the stake location (centering)-refer to an injection soil layer, working condition requirement pile center line vertical with the ground horizontal plane or with the tilt location of a certain angle value of ground horizontal plane.After the soil layer certain depth was squeezed in stake, it is stable that desired angle value has become, and its positioning work piece can unclamp returns original position; Therefore, the stake location only is provided with manually, does not list the piling automatic working cycle lasts in.
The dust cycle of double-plunger hydraulic hammer is divided into: hammer rises (backhaul), hammer decline (dashing down) and pressurize/tracking three phases.
(1) hammer rising (backhaul)
1DT, 2DT energising, JN simultaneously
1Signal is arranged, and the 3DT energising of selector valve 5 makes short valve 6 commutations, and the pressure oil of pump and high pressure accumulator 8A is through one-way valve D
2Provide pressure oil for rising cylinder 11 simultaneously; Down towards 10 in cylinder by short valve 6 and Pilot operated check valve D
0Two passes link to each other the low pressure accumulator 9A absorption portion return pressure oil in the oil circuit with low tension loop.
(2) piling motion (hammer dashes down)
When hammer rises to setting height, the 3DT of selector valve 5 outage, short valve 6 commutations, high pressure oil one tunnel directly enters down towards double-plunger oil cylinder 10 through short valve 6, and another road is through one-way valve D
2Enter rising double-plunger oil cylinder 11; Constitute differential circuit towards double-plunger oil cylinder 10 and rising double-plunger oil cylinder 11 down, under the effect of pressure oil, the oil of rising double-plunger oil cylinder 11 is through Pilot operated check valve D
1Conflux fast in descending, hammer is impacted, the motion of driving piles with the acceleration that is a bit larger tham a g downwards towards double-plunger oil cylinder 10.At this moment, oil hydraulic pump is supplied with the differential required partial pressure oil towards double-plunger oil cylinder 10 except that giving down, returns high pressure accumulator 8A and stores unnecessary pressure oil; Under break through journey, four cylinders and oil return circuit all disconnect, low pressure accumulator 9A then discharges the energy that absorbs (down towards double-plunger oil cylinder 10) in the hammer uphill process gradually.
(3) pressurize/tracking phase
During hammering blow pile cover 23, make stake 22 sink to the soil layer certain depth, hammer continues to dash down to be parked on the pile cover.For preventing back-slabbing of stake, tup must stay for some time on pile cover and carry out pressurize.At this moment, pile cover leaves tracking signal JN
2Variation has taken place to set a distance in promptly outstanding seat 12 and 23 of pile covers; Thereby tracking signal JN
2Produce error signal (JN
2).According to the dwell time END instruction, the 3DT of selector valve 5 energising, the one tunnel makes short valve 6 commutations, and hammer begins to rise; Another road makes the 4DT outage of electro-hydraulic reversing valve 19, and elevator oil hydraulic motor 17 is clockwise, and outstanding seat 12 moves down fast follows the tracks of pile cover 23, makes error signal (JN
2) to disappear be the 4DT outage, break 17 brakes, outstanding seat 12 and pile cover 23 are promptly finished the pursuit movement of a set a distance.System begins new round automatic working cycle again.
The electrical control working principle:
Industrial electronic control gear-PC the programmable controller of contemporary processor technology is adopted in electrical control.It is mainly by programmable device, cpu central processing unit, compositions such as input/output module; Have functions such as counting, timing (time-delay), displacement, arithmetic/logic, supervision, automatic fault diagnosis, current failure memory; It can adapt to bad working environment, antijamming capability is strong, programming is easy and can according to working condition requirement change arbitrarily program, reliability height, response fast, be easy to advantage such as maintenance.
Be applied to the utility model double-plunger hydraulic pile hammer aspect, two independently the electric control system of hydraulic system adopt centralized control.Three kinds of working staties are set: a) manual, b) crawl, c) automatic.
Electric control principle PC ladder diagram [referring to Fig. 7, Fig. 8]
Electric control principle PC ladder diagram according to U.S. GE company series III-PC programmable controller handbook by technical flow design.The definition of the numeral of ladder diagram is number as follows with corresponding title contrast:
I, operation base key (panel key) numeral definition code name marking-up numeral definition code name marking-up (1) 4041 1TA (can not Self-resetting) unloading key (2) 4111 1QA (can not Self-resetting) manual loading key (3) 4121 ZK (can not Self-resetting) automatic cycle (4) 9021 2QA (Self-resetting) crawls hammer rises (5) 4112 3QA (can not Self-resetting) manual positioning (6) 4042 2TA (can not Self-resetting) and locates and unclamp (7) 9022 4QA (Self-resetting) crawl suspension seats tracking (8) 9023 5QA (Self-resetting) crawl suspension seat liters
II impact energy options button (panel key) (1) 4011 CM
1(can not reset certainly) membrane keyboard 1 (2) 4012 CM
2(can not reset certainly) membrane keyboard 2 (3) 4013 CM
3(can not reset certainly) membrane keyboard 3 (4) 4014 CM
4(can not reset certainly) membrane keyboard 4 (5) 4015 CM
5(can not reset certainly) membrane keyboard 5 (6) 4016 CM
6(can not reset certainly) membrane keyboard 6 (7) 4017 CM
7(can not reset certainly) membrane keyboard 7 (8) 4018 CM
8(can not reset certainly) membrane keyboard 8
III Check point (see figure 1) (1) 9001-hammer is limited signal JN down
1For near switch.JN
1Inductive head places on the outstanding seat 12, JN
1Detecting body (installation) the hammer on appropriate location (Vertical direction is adjustable up and down); (2) 9002-frame seat tracking signal JN
2Be two near switch in parallel, place the lower end in the hollow steel pipe stretched under two respectively; Its two hollow steel pipe upper ends are fixed with outstanding 12 respectively, JN
2Inductive head be contained in the steel pipe lower end and 3～5 millimeters apart from the steel pipe lower end surface; JN
2Detecting body promptly be the end face of pile cover 23 (metal).The fixed length of frame seat 12 bottom surfaces to hollow steel pipe lower end surface is called the set a distance of frame seat to the pile cover end face.
Limited signal (JN under (1) 0001-hammering of IV timer
1) 9001 make contact, timer T
1Energising pressurize time-delay reaches t
01(second) promptly moves closed; (2) 0011-press membrane keyboard (CM
1) 4011 make contact (4121 and T
1When all closed), timer T
11On-delay reaches t
11Promptly moving closing; (3) 0012-press membrane keyboard (CM
2) 4012 make contact (4121 and T
1When all closed), timer T
12On-delay reaches t
12Promptly moving closing; (4) 0013-press membrane keyboard (CM
3) 4013 make contact (4121 and T
1When all closed), timer T
13On-delay reaches t
13Promptly moving closing; (5) 0014-press membrane keyboard (CM
4) 4014 make contact (4121 and T
1When all closed), timer T
14On-delay reaches t
14Promptly moving closing; (6) 0015-press membrane keyboard (CM
5) 4015 make contact (4121 and T
1When all closed), timer T
15On-delay reaches t
15Promptly moving closing; (7) 0016-press membrane keyboard (CM
6) 4016 make contact (4121 and T
1When all closed), timer T
16On-delay reaches t
16Promptly moving closing; (8) 0017-press membrane keyboard (CM
7) 4017 make contact (4121 and T
1When all closed), timer T
17On-delay reaches t
17Promptly moving closing; (9) 0018-press membrane keyboard (CM
8) 4011 make contact (4121 and T
1When all closed), timer T
18On-delay reaches t
18Promptly moving closing;
V PC bosom relay (1) 7011-work as T
11The normally opened contact action is closed, and 7011 coil electricities disconnect its normally-closed contact, makes the 3DT outage; (2) 7012-work as T
12The normally opened contact action is closed, and 7012 coil electricities disconnect its normally-closed contact, makes the 3DT outage; (3) 7013-work as T
13The normally opened contact action is closed, and 7013 coil electricities disconnect its normally-closed contact, makes the 3DT outage; (4) 7014-work as T
14The normally opened contact action is closed, and 7014 coil electricities disconnect its normally-closed contact, makes the 3DT outage; (5) 7015-work as T
15The normally opened contact action is closed, and 7015 coil electricities disconnect its normally-closed contact, makes the 3DT outage; (6) 7016-work as T
16The normally opened contact action is closed, and 7016 coil electricities disconnect its normally-closed contact, makes the 3DT outage; (7) 7017-work as T
17The normally opened contact action is closed, and 7017 coil electricities disconnect its normally-closed contact, makes the 3DT outage; (8) 7018-work as T
18The normally opened contact action is closed, and 7018 coil electricities disconnect its normally-closed contact, makes the 3DT outage;
VI exports (1) 0101-hydraulic system A, relief valve electromagnet 1DT (energising loads, the outage unloading); (2) 0102-hydraulic system A, unloading valve electromagnet 2DT (energising loads, the outage unloading); (3) 0111-hydraulic system B, relief valve electromagnet 11DT (energising loads, the outage unloading); (4) 0112-hydraulic system B, unloading valve electromagnet 12DT (energising loads, the outage unloading); (5) 0203-hydraulic system A, pilot reversing valve electromagnet 3DT (the energising hammer rises, and the outage hammer impacts downwards); (6) 0204-hydraulic system B, selector valve electromagnet 4DT (the clockwise outstanding seat of energising hydraulic motor is followed the tracks of pile cover, the power-off brake brake); (7) 0205-hydraulic system B, selector valve electromagnet 5DT (the energising hydraulic motor reverses outstanding seat and promotes, the power-off brake brake); (8) 0206-hydraulic system B, selector valve electromagnet 6DT (energising folder stake location, outage is unclamped).
Electric control principle
Halted state: manual loading key (1QA) 4111 contacts or automatic cycle key (ZK) 4121 contacts are in normally open or click unloading key (1TA) 4041 contacts is to disconnect moment by normally off, and 101 (1DT), 102 (2DT), 111 (11DT), 112 (12DT) coil all cut off the power supply; Relief valve, feather valve are all opened, and are zero directly to flow back to fuel tank from the hydraulic coupling of oil hydraulic pump.Rising twin columns plug cylinder chamber inner fluid all is in air-tight state, and hammer promptly is parked in arbitrary position.
Working state: (1) hydraulic system loads: press manual loading key (1QA) and make 4111 normally opened contacts closed or press automatic cycle key (ZK) and make 4121 normally opened contact closures, coil 101 (1DT), 102 (2DT) energising, hydraulic circuit control device () is promptly set up hydraulic coupling and is in the loading working state.In coil 204 (4DT), 205 (5DT), 206 (6DT), need only just make closed or manual (2TA) key of its normally opened contact make 4042 normally opened contact closures by one of them coil electricity, coil 111 (11DT), 112 (12DT) energising, hydraulic system B promptly sets up hydraulic coupling and is in the loading working state.(2) hammering energy/frequency selection is set: hammering energy/frequency should be provided with according to soil property situation and pile material strength grading.Setting principle is: according to parameters such as the gross mass of hammering into shape in pile monkey or the forging hammer product line, hammering stroke and electricity, hydraulic control system element responds times, divide the n level.With n membrane keyboard CM
1, CM
2, CM
3CM
nFor the code implementation parallel connection as the input signal point.In fact, its n input point in parallel promptly is to rise to n position height by PC control hammer, can determine to hammer into shape corresponding blow energy (KJ)/frequency (HZ).Place auto state: the user only need select suitable membrane keyboard CM
n, corresponding timer Tn presets time-delay t
nSecond, promptly control hammer (backhaul) time of rising is t
n(second), hammer promotes corresponding height and is: H
n=V
11t
nRice; The instantaneous velocity that hammer impacts pile cover downwards is: V
10＞(2gH
n)
1/2(meter per second); If the gross mass of hammer is m
1(Kg), then the kinetic energy of hammering is: E
k=m
1v
2 10/ 2..(3) the outstanding seat of manual adjustment promotes or moves down: hang seat 12 and promote: before the piling, must connect pile cover 23 usefulness middling speeds to outstanding seat 12 earlier and promote above a stake upper end end face.Pin (5QA) key, make 9023 normally opened contact closures (manual state: automated contact 4121 is normally off), coil 205 (5DT) energising elevator oil hydraulic motor 17 reverses middling speed lift stand and pile cover.Outstanding seat 12 moves down: crawl (4QA) key, make 9022 normally opened contact closures (the crawl state: automated contact 4121 is normally off), the instantaneous energising of coil 204 (4DT), elevator oil hydraulic motor 17 is clockwise, outstanding seat and pile cover are moved down, make pile cover be enclosed within a upper-end surface on request; Continue crawl again, tracking signal JN
2Near the pile cover end face, corresponding normally-closed contact 9002 (JN
2) promptly disconnect coil 204 (4DT) outage, the stall of elevator oil hydraulic motor, brake; Outstanding seat has reached the tracing preset distance with pile cover.Be that the preceding adjustment of automatic cycle is finished.(4) manually realize the stake location or unclamp: under the automatic working cycle state, to the location of stake or unclamp and adopt manually.The location: by (3QA) key, make 4112 normally opened contact closures, coil 206 (6DT) energising, the stake of two positioning work piece folders realizes the location to stake.Unclamp: by (2TA) key, 4042 normally-closed contacts are disconnected, coil 206 (6DT) outage, two positioning work pieces unclamp returns original position.(5) automatic working cycle: press (ZK) key automatically, 4121 corresponding normally opened contact closures (normally-closed contact disconnects simultaneously), system is in the automatic working cycle state.If press membrane keyboard (CM
2) key, corresponding 4012 normally opened contact closures are when hammer impacts approaching limited signal (JN down downwards
1), corresponding 9001 normally opened contact closures are connected T
1Timer begins the pressurize time-delay and reaches t
01Second, T
1The normally opened contact closure, coil 203 (3DT) energising, hammer begins to rise; Work as T
1In the time of the normally opened contact closure, also by logical T
12Timer and trigger reach t
12After second, T
12The normally opened contact closure, make auxiliary reclay 7012 energising, normally-closed contact 7012 disconnects, and forces coil 203 (3DT) outage, hammer stops to rise; The hammer lifting height is: H
12=V
11t
12(rice).Coil 203 (3DT) outage makes guide's solenoid directional control valve change the position of short valve, rising twin columns plug cylinder inner chamber with down towards the twin columns plug cylinder inner chamber formation differential circuit of communicating with each other; Hammer impacts pile cover downwards with the acceleration greater than a g, forces stake to sink to the soil layer certain depth; Pile cover is away from tracking signal JN
2, normally off is got back in corresponding 9002 contacts; Because T
1Finish the pressurize time-delay and reach t
01After second, T
1Normally opened contact closed again, coil 203 (3DT) switch on again, hammer begins rising again; Also make coil 204 (4DT) energising simultaneously, hydraulic motor is clockwise, and outstanding seat 12 moves down fast follows the tracks of pile cover 23, as tracking signal JN
2Near pile cover, 9002 corresponding normally-closed contacts disconnect, coil 204 (4DT) outage, and the hydraulic motor stall, braking brake is followed the tracks of and is stopped.The hammer rise time reaches t
12During second, 203 (3DT) outage, the hammer lifting height reaches H again
12=V
11t
12(rice) begins new round automatic working cycle again.(6) Zhuan bearing capacity not only available digital show but also printablely come: the kinetic energy E of hammering
K10=m
1V
2 10/ 2 (KJ) calculate function and write automatically, and the stake injection soil depth h value that is recorded by displacement transducer also writes automatically by Computing, and the resistance that stake is subjected to i.e. the average bearing capacity of stake: F=m
1v
2 10/ 2h (KN), not only available digital showed but also can print by configure printer.
Two kinds of modes of operation of automatically controlled employing: be user's more convenient operation, key button and two kinds of feature operation modes of hand-clasping type remote controller on the electrical control panel are set.The indoor control panel key name of electrical control claims to claim identically with the key name of on-the-spot manual mode remote controller that promptly they have identical functions and using method.These two kinds of modes of operation are chosen any one kind of them and are got final product.
Two, double-plunger hydraulic forging hammer
The double-plunger hydraulic forging hammer comprises frame seat 12, rising twin columns plug cylinder 11, following to twin columns plug cylinder 10, the oil circuit of hydraulic circuit control device () is respectively with rising twin columns plug cylinder 11, be connected towards twin columns plug cylinder 10 down, hydraulic oil pressure is to down towards the plunger active area of the twin columns plug cylinder 10 plunger active area greater than rising twin columns plug cylinder 11, rising twin columns plug cylinder 11, down the bottom towards twin columns plug cylinder 10 connects tups 14 by connecting body 13, anvil 44 is arranged at the bottom of the frame seat.Hammer be by connecting body 13 with top two under be connected with two rising twin columns plug cylinders 11 again with following tup 14 towards twin columns plug cylinder 10 and be connected, the three is fixed to be holistic general name.Three's quality sum is the gross mass of hammer.The structure of hydraulic circuit control device () is identical with the hydraulic circuit control device () of double-plunger hydraulic pile hammer, and as shown in Figure 5, the hydraulic principle of this part and hydraulic work process are identical with the double-plunger hydraulic pile hammer, no longer repeat at this.
The utility model double-plunger hydraulic hammer and external modern hydraulic hammer all belong to the impact type hydraulic hammer.Operating characteristic is similar substantially: input parameter is the working pressure and the working flow of liquid stream; Output parameter is final velocity, ballistic throw, frequency of impact and impact energy.The main distinction is:
The first, what external modern liquid hammer adopted is stepped piston (oil cylinder) principle, and the employing of this patent liquid hammer is differential and double plunger (oil cylinder) principle.Since hydraulic hammer work in the impact process be greater than a g acceleration movement, piston or plunger to-and-fro motion linear velocity are up to 4～8 meter per seconds, and be more much higher than general hydraulic equipment.High like this active line speed is high especially to the manufacturing technology and the seal request of oil hydraulic cylinder.External liquid hammer adopts piston and floating piston, must carry out super precision processing to inner wall of cylinder (deep and long hole), even adopt modern high-precision, sharp deep hole processing equipment, and the also difficult requirement of guaranteeing the precision and the surface roughness of its endoporus; For adopting the floating piston technology, also must adopt floating piston and inner wall of cylinder pairing abrasive process during manufacturing, can guarantee the strict seal request of isolating of oil and nitrogen; The fretting wear that piston and the relative movement of inner wall of cylinder high speed produce reduces the sealability aggravation.So manufacture cost and maintenance cost height.The utility model double-plunger hydraulic hammer has been cancelled piston and has been adopted the double-plunger oil cylinder; Inner wall of cylinder to double-plunger is not processed, and need only carry out super precision processing to the cylindrical of double-plunger, and its process equipment adopts high-precision cylindrical grinder just to polish to foreign round then can reach technical requirements.Because no piston only need adopt the axle seal element.China has working pressure 45MPa, back and forth linear velocity reaches 10～15 meter per seconds series Wellendichtring, can satisfy the seal request of this patent product, therefore fully, the manufacture cost of this patent series product is compared and can be reduced about 70% with external like product with maintenance cost.
Second this patent is applied to the hydraulic pile hammer series product, adopts the set a distance tracking technique, at home and abroad beyond example still.Hydraulic pile hammer is in the piling process, and each work cycle is impacted a kinetic energy to pile cover, just transmits stake one this kinetic energy of corresponding kinetic energy simultaneously and makes stake overcome soil layer resistance injection soil layer one depthkeeping.In fact, hammer is exactly the mutual collision process of two objects to the impact process of pile cover and stake.In collision process, hammer all is considered as elastomer with the object of two mutual collisions of pile cover (and stake); Can think that in theory the total kinetic energy of two object collisions front and back objects systems is constant.According to heart elastic impact theory is had following relation:
If hammer collides the speed of back hammer by v to pile cover and stake
10Become v
1(meter per second):
v
1＝[(m
1-m
2)v
10+2m
2v
20]/(m
1+m
2)……….(1)
Acquisition speed in back is v if pile cover and stake are collided
2(meter per second);
v
2＝[(m
1-m
2)v
20+2m
1v
10]/(m
1+m
2)……….(2)
In the following formula: m
1--the gross mass (Kg) of hammer; m
1=4 double-plunger quality sum+connecting body quality+tup quality; m
2--by impacted object quality (Kg); m
2The quality of=pile cover quality+stake+(associated mass); v
10--preceding instant (end) speed (meter per second) of collision mutually takes place to pile cover in hammer as yet; v
10＞(2gH)
1/2G--gravity accleration (g=9.8 meter per second
2); H
n--the impact working stroke (rice) of hammer; V
20--pile cover and stake are not subjected to hammering into shape the preceding speed (meter per second) of collision; Because before the downward impact of hammer fashion did not collide pile cover, pile cover and stake were static, so V
20=0 thus following formula (1), (2) should be:
V
1＝(m
1-m
2)v
10/(m
1+m
2)…………(3)
V
2＝2m
1v
10/(m
1+m
2)…………… (4)
By formula (3) as can be seen: work as m
1=m
2The time, after collision mutually takes place to pile cover in hammer, the instantaneous velocity v of hammer
1=0; Work as m
1＞m
2The time, v
1＞0, promptly hammer to after the mutual collision of pile cover generation the instantaneous velocity v before the instantaneous velocity of hammer collides with generation is mutual as yet into shape
10Direction in the same way, its big or small v
1Much smaller than v
10, hammer promptly slows down and continues to move downward; Work as m
1＜m
2The time, v
1＜0, promptly hammer to after the mutual collision of pile cover generation the instantaneous velocity v of hammer into shape
1With the instantaneous velocity v that takes place as yet before the collision mutually
10Direction opposite, its big or small v
1Less than v
10Upwards bounce-back motion appears in hammer.Make m when therefore, designing liquid hammer as far as possible
1＞m
2
By formula (4) as can be known: after hammer to pile cover collision mutually took place, pile cover and stake had promptly obtained speed v
2, its kinetic energy is: E
K2=m
2v
2 2/ 2.Gross mass m when hammer
1, collision instantaneous velocity v constantly
10The time its impact kinetic energy be: E
K1=m
1v
10 2/ 2; If the kinetic energy conversion kept E when collision mutually took place
K2=E
K1Be definite value: work as m
2Gross mass is big, v
2Value is just little; Work as m
2Gross mass is little, v
2Value is just big.
External modern hydraulic pile hammer is that the gross weight of similar outstanding seat is shelved on the pile cover behind the counterweight loss of weight.This has just added certain mass to pile cover and stake, promptly m
2Gross mass strengthened, make v
2Value has diminished, and the kinetic energy that stake and pile cover obtain has reduced; Thereby pile sinking power reduces the reduction of pile sinking efficient.
The utility model has adopted tracking technique, the gross weight of outstanding seat behind the counterweight loss of weight, with the elevator oil hydraulic motor by wire rope outstanding seat suspention (actual pulling force is the weight that deducts after the counterweight), pile cover and stake upward no impost (are m
2In do not contain associated mass).Obviously increased v
2Value has increased pile sinking power, has improved pile sinking efficient.
Three, in every twin columns plug cylinder, to be that two external diameters are unequal combine a ladder major axis to its double-plunger, in the end that the less guide sleeve of plunger outer diameter is inner and plunger outer diameter is bigger hydraulic cushion is set, when the prevention double-plunger is in cylinder end upper and lower position to cylinder end generation mechanical collision.
The 4th, two design of Hydraulic System of hydraulic pile hammer are two autonomous systems, and a hydraulic system places on the outstanding seat of servo-actuated, and its hydraulic element all adopt integrated package, save pipeline between the element and connect, and the oil pipe that links to each other with the double-plunger oil cylinder is short as far as possible; Therefore, the system pressure loss is little, reliability is high.The power line of the drive motor of its hydraulic system and automatically controlled I/O cable are followed the slippage up and down of outstanding seat.
The 5th, modern microelectronic PC industrial control unit (ICU) able to programme is adopted in electrical control, can change program arbitrarily according to working condition requirement, and energy automatic diagnosis fault can monitor full working procedure runnability.
The 6th, easy and simple to handle, the automaticity height.
The user is the primer fluid press pump at first, carries out the adjustment before the automatic working cycle by crawl, manipulated key again; Then options button is placed automatic mode:, select corresponding by relevant rule acenaphthene according to the intensity of soil property situation and pile material " hammering energy/frequency " digital code name membrane keyboard, piling promptly enters automatic working cycle.
Claims (6)
1, a kind of double-plunger hydraulic hammer, comprise frame seat (12), rising twin columns plug cylinder (11), following towards twin columns plug cylinder (10), it is characterized in that hydraulic circuit control device the is arranged oil circuit of () is respectively with rising twin columns plug cylinder (11), be connected towards twin columns plug cylinder (10) down, towards the plunger active area of twin columns plug cylinder (10) the plunger active area greater than rising twin columns plug cylinder (11), rising twin columns plug cylinder (11), the bottom towards twin columns plug cylinder (10) connects tup (14) by connecting body (13) to hydraulic oil pressure down to down.
2, double-plunger hydraulic hammer according to claim 1, it is characterized in that this double-plunger hydraulic hammer is the double-plunger hydraulic pile hammer, comprise movable part, standing part, hydraulic circuit control device part, circuit control device part, movable part is mounted in as the outstanding seat (12) of frame seat and goes up, removes and rising twin columns plug cylinder (11) is arranged, descend towards twin columns plug cylinder (10), connecting body (13), tup (14) tracking signal (JN
2) limited signal (JN under device (24), the hammering
1) install (26), servo-actuated cable/balladeur train (27), hang a seat upper saw pulley (32), standing part is mounted on the support (38), has elevator oil hydraulic motor (17), stake positional cylinder (21), traction to hang the static pulley group (28) of seat (12), multistage assembled frame (29,30,37), outstanding seat lifting wire rope (31), counterweight wire rope (33), transfer gradient to support (35), counterweight (36), electric control box (41), assembled frame supporting free bearing (42), guide rail (43).
3, double-plunger hydraulic hammer according to claim 2, it is characterized in that the hydraulic circuit control device part is by control double-plunger oil cylinder rising twin columns plug cylinders (11), form towards the hydraulic circuit control device () of twin columns plug cylinder (10) and (two) two live hydraulic systems of hydraulic circuit control device of control stake positional cylinder (21) down, hydraulic circuit control device (one) control box (25) places on the outstanding seat (12) of servo-actuated, hydraulic circuit control device (two) control box (39) places fixedly on the support (38), two systems all have and independently flow the press pump station, hydraulic actuator, hydraulic control component.
4, double-plunger hydraulic hammer according to claim 3 is characterized in that hydraulic circuit control device partly has auxiliary device high pressure accumulator (8A, 8B) and low pressure accumulator (9A, 9B).
5, double-plunger hydraulic hammer according to claim 2 is characterized in that circuit control device partly adopts electric control device-PC programmable controller, and it is mainly by programmable device, cpu central processing unit, and input/output module is formed.
6, double-plunger hydraulic hammer according to claim 1, it is characterized in that this double-plunger hydraulic hammer is the double-plunger hydraulic forging hammer, remove and comprise frame seat (12), rising twin columns plug cylinder (11), down towards twin columns plug cylinder (10), the oil circuit of hydraulic circuit control device () respectively with rising twin columns plug cylinder (11), connect towards twin columns plug cylinder (10) down, hydraulic oil pressure is to down towards the plunger active area of twin columns plug cylinder (10) the plunger active area greater than rising twin columns plug cylinder (11), rising twin columns plug cylinder (11), down the bottom towards twin columns plug cylinder (10) connects outside the tup (14) by connecting body (13), also has anvil (44) at the bottom of the frame seat.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 02223944 CN2537848Y (en) | 2002-04-26 | 2002-04-26 | Double plunger hydraulic hammer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 02223944 CN2537848Y (en) | 2002-04-26 | 2002-04-26 | Double plunger hydraulic hammer |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2537848Y true CN2537848Y (en) | 2003-02-26 |
Family
ID=33701501
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 02223944 Expired - Fee Related CN2537848Y (en) | 2002-04-26 | 2002-04-26 | Double plunger hydraulic hammer |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2537848Y (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100469480C (en) * | 2007-01-05 | 2009-03-18 | 广东工业大学 | High speed punch cutting device and its control method |
| CN102418723A (en) * | 2011-12-05 | 2012-04-18 | 海卓泰克液压技术（苏州）有限公司 | Compound oil cylinder device |
| CN106545530A (en) * | 2016-07-22 | 2017-03-29 | 中聚信海洋工程装备有限公司 | A kind of hydraulic pump is superimposed the hydraulic quick forging unit of fuel feeding with high pressure accumulator |
| CN108757648A (en) * | 2018-05-21 | 2018-11-06 | 广东力源液压机械有限公司 | A kind of hydraulic pile hammer control method and its system |
| CN114961551A (en) * | 2022-05-09 | 2022-08-30 | 中国地质大学（北京） | All-metal axial double-plunger rotary impact type downhole positive displacement motor |
-
2002
- 2002-04-26 CN CN 02223944 patent/CN2537848Y/en not_active Expired - Fee Related
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100469480C (en) * | 2007-01-05 | 2009-03-18 | 广东工业大学 | High speed punch cutting device and its control method |
| CN102418723A (en) * | 2011-12-05 | 2012-04-18 | 海卓泰克液压技术（苏州）有限公司 | Compound oil cylinder device |
| CN106545530A (en) * | 2016-07-22 | 2017-03-29 | 中聚信海洋工程装备有限公司 | A kind of hydraulic pump is superimposed the hydraulic quick forging unit of fuel feeding with high pressure accumulator |
| CN106545530B (en) * | 2016-07-22 | 2017-12-12 | 中聚信海洋工程装备有限公司 | A kind of hydraulic pump is superimposed the hydraulic quick forging unit of fuel feeding with high pressure accumulator |
| CN108757648A (en) * | 2018-05-21 | 2018-11-06 | 广东力源液压机械有限公司 | A kind of hydraulic pile hammer control method and its system |
| CN108757648B (en) * | 2018-05-21 | 2023-06-23 | 广东斯巴达重工科技有限公司 | Hydraulic pile hammer control method and system |
| CN114961551A (en) * | 2022-05-09 | 2022-08-30 | 中国地质大学（北京） | All-metal axial double-plunger rotary impact type downhole positive displacement motor |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C19 | Lapse of patent right due to non-payment of the annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |