CN202688982U - Vibration reducing system for dynamic compactor and dynamic compactor therewith - Google Patents
Vibration reducing system for dynamic compactor and dynamic compactor therewith Download PDFInfo
- Publication number
- CN202688982U CN202688982U CN 201220262242 CN201220262242U CN202688982U CN 202688982 U CN202688982 U CN 202688982U CN 201220262242 CN201220262242 CN 201220262242 CN 201220262242 U CN201220262242 U CN 201220262242U CN 202688982 U CN202688982 U CN 202688982U
- Authority
- CN
- China
- Prior art keywords
- jib
- valve
- mitigation system
- shock mitigation
- dynamic compaction
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Images
Landscapes
- Investigation Of Foundation Soil And Reinforcement Of Foundation Soil By Compacting Or Drainage (AREA)
Abstract
The utility model discloses a vibration reducing system for a dynamic compactor, comprising at least one oil cylinder, a first energy accumulator, a second energy accumulator, a first overflowing valve, a second overflowing valve, a first throttling valve, a second throttling valve, a first one-way valve and a second one-way valve, wherein the oil cylinder comprises a cylinder body with an inner cavity and a piston for dividing the inner cavity into a rod cavity and a rodless cavity; the first energy accumulator and the second energy accumulator are respectively communicated with the rod cavity and the rodless cavity by a first oil path channel and a second oil path channel; the first overflowing valve and the second overflowing valve can be used for controlling the oil pressure of hydraulic oil in the first oil path channel and the second oil path channel respectively; inlets of the first throttling valve and the second throttling valve are respectively communicated with one end of the first energy accumulator and one end of the second energy accumulator, and a flow discharging channel is connected between outlets of the first throttling valve and the second throttling valve; outlets of the first one-way valve and the second one-way valve are respectively communicated with the first oil path channel and the second oil path channel, and an oil return channel is connected between inlets of the first one-way valve and the second one-way valve; and the pressure in the flow discharging channel is lower than that in the oil return channel. The vibration reducing system disclosed by the utility model has the advantages that more-effective vibration reduction can be carried out on an arm frame of the dynamic compactor, so that the service life of the dynamic compactor and the arm rest can be prolonged. The utility model also discloses the dynamic compactor.
Description
Technical field
The utility model relates to engineering machinery field, especially relates to a kind of shock mitigation system for dynamic compaction machinery and has its dynamic compaction machinery.
Background technology
Dynamic compaction machinery is mainly used in dynamic consolidation construction, a height of dynamic compaction machinery normal operation wire rope connects detacher and vehicle frame, regulate the lifting altitude of hammer ram by boom hoist cable, after hammer ram arrives certain altitude during the strong rammer operation, can control the hammer ram that detacher discharges the below, because thereby the release of hammer ram load causes strong impact to jib, the jib damping is the mechanical spring devices that adopt at present more, but the elastic force that the mechanical spring device can provide is limited, in the process of direction vibration, can not provide well jib required damping force, preferably damping effect be can't obtain, and then the application life of jib and stability and the safety of car load affected.
The utility model content
The utility model is intended to solve at least one of technical problem that exists in the prior art.
For this reason, a purpose of the present utility model is to propose a kind of shock mitigation system for dynamic compaction machinery, and described shock mitigation system can be carried out more effectively damping to the jib of dynamic compaction machinery, prolongs the application life of dynamic compaction machinery and jib.
Another purpose of the present utility model is to propose a kind of dynamic compaction machinery with above-mentioned shock mitigation system.
The shock mitigation system that is used for dynamic compaction machinery according to the utility model first aspect embodiment, comprise: at least one oil cylinder, each described oil cylinder includes the cylinder body with inner chamber and is located at movably the interior piston of described inner chamber, and described piston is separated into rod chamber and rodless cavity with described inner chamber; The first and second accumulators, described the first accumulator are communicated with described rod chamber by the first asphalt channel and described the second accumulator is communicated with described rodless cavity by the second asphalt channel; The first and second overflow valves, the hydraulic oil pressure that described the first and second overflow valves can be respectively applied to control in described the first and second asphalt channels is not higher than predefined threshold value; The first and second choke valves, the import of described the first and second choke valves are communicated with a described end of described the first and second accumulators respectively, and are connected with current by pass between the outlet of described the first and second choke valves; The first and second one way valves, the outlet of described the first and second one way valves is communicated with described the first and second asphalt channels respectively, and be connected with drainback passage between the import of described the first and second one way valves, the pressure in the wherein said current by pass is lower than the pressure in the described drainback passage.
The shock mitigation system that is used for dynamic compaction machinery according to the utility model embodiment, can be after dynamic compaction machinery carries out ramming operation release hammer ram, effectively provide damping force to the i.e. reciprocal vibrations of two-way vibrations of jib, the amplitude of vibration of quick decay jib, make dynamic compaction machinery can enter fast next ramming operation, improve ramming efficient, reduce simultaneously the jib vibrations to the impact of dynamic compaction machinery, improve the stability of dynamic compaction machinery working environment, comfortableness and safety, thereby prolong the application life of dynamic compaction machinery and jib, reduce use cost, in addition, this shock mitigation system is simple in structure, structure rationally, need not increase electrical equipment and additional energy source, need not complicated operating process control and power supply, saved the energy, further reduced cost.
In addition, according to the shock mitigation system strong adaptability of the utility model embodiment, and can be made into independently module use, only need native system be set at the anti-hypsokinesis bar of jib to existing dynamic compaction machinery and get final product.
In addition, the shock mitigation system that is used for dynamic compaction machinery according to the utility model embodiment can also have following additional technical feature:
In an embodiment of the present utility model, described oil cylinder is two, and the described rod chamber of each described oil cylinder is connected with described the first asphalt channel, and the described rodless cavity of each described oil cylinder is connected with described the second asphalt channel.
Advantageously, described the first asphalt channel is communicated with the top of described rod chamber and described the second asphalt channel is communicated with the bottom of described rodless cavity.Can take full advantage of thus the interior space of chamber of rod chamber and rodless cavity.
In embodiment more of the present utility model, described the first overflow valve is pilot operated compound relief valve or direct-acting overflow valve, and described the second overflow valve is pilot operated compound relief valve or direct-acting overflow valve.
In an embodiment of the present utility model, described shock mitigation system also comprises: the first and second fuel tanks, and the end of wherein said drainback passage is communicated with described the first fuel tank, and the end of described current by pass is communicated with described the second fuel tank.
Dynamic compaction machinery according to the utility model second aspect embodiment comprises: car body; Jib, the lower end of described jib are located on the described car body pivotly; At least one anti-hypsokinesis bar, each described anti-hypsokinesis bar is located at respectively between described jib and the described car body; According to the shock mitigation system of the utility model first aspect embodiment, the free end of the described piston rod of wherein said shock mitigation system links to each other with the rear end of described anti-hypsokinesis bar; Balanced component, described balanced component are located on the described car body with the described jib of balance; Lifting subassembly, described lifting subassembly comprise suspension hook and be located at described suspension hook below, be used for hanging the detacher of holding hammer ram, and the front end of the hoisting rope of wherein said dynamic compaction machinery links to each other with described suspension hook; With the control module that is used for controlling described lifting subassembly work.
Alternatively, described anti-hypsokinesis bar is two, and the described oil cylinder of described shock mitigation system is two.
In an embodiment of the present utility model,, turn up the soil and be arranged between described jib and the described car body in described two anti-hypsokinesis bar along continuous straight runs intervals.
In an embodiment of the present utility model, described balanced component comprises: man-like shelf, described man-like shelf are located on the described car body and are positioned at the rear side of described jib and spaced apart with described jib; Jib stay cord, the two ends of described jib stay cord link to each other with the upper end of described jib and the top of described man-like shelf respectively.
According to the dynamic compaction machinery of the utility model embodiment, by shock mitigation system is set, when operating, ramming can carry out damping to jib better, and the amplitude of vibration of the jib of decaying fast improves ramming efficient, prolongs the application life of dynamic compaction machinery.
Additional aspect of the present utility model and advantage in the following description part provide, and part will become obviously from the following description, or recognize by practice of the present utility model.
Description of drawings
Above-mentioned and/or additional aspect of the present utility model and advantage are from obviously and easily understanding becoming the description of embodiment in conjunction with following accompanying drawing, wherein:
Fig. 1 is the structural representation according to the shock mitigation system that is used for dynamic compaction machinery of the utility model embodiment; With
Fig. 2 is the structural representation according to the dynamic compaction machinery of the utility model embodiment.
The specific embodiment
The below describes embodiment of the present utility model in detail, and the example of described embodiment is shown in the drawings, and wherein same or similar label represents same or similar element or the element with identical or similar functions from start to finish.Be exemplary below by the embodiment that is described with reference to the drawings, be intended to for explaining the utility model, and can not be interpreted as restriction of the present utility model.
In description of the present utility model, it will be appreciated that, term " " center "; " vertically "; " laterally "; " front "; " afterwards "; " left side ", " right side ", " vertically ", " level ", " top ", " end " " interior ", orientation or the position relationship of indications such as " outward " are based on orientation shown in the drawings or position relationship, only be for convenience of description the utility model and simplified characterization, rather than device or the element of indication or hint indication must have specific orientation, with specific orientation structure and operation, therefore can not be interpreted as restriction of the present utility model.
In addition, term " first ", " second " only are used for describing purpose, and can not be interpreted as indication or hint relative importance or the implicit quantity that indicates indicated technical characterictic.Thus, one or more these features can be expressed or impliedly be comprised to the feature that is limited with " first ", " second ".In description of the present utility model, the implication of " a plurality of " is two or more, unless clear and definite concrete restriction is arranged in addition.
In the utility model, unless clear and definite regulation and restriction are arranged in addition, First Characteristic Second Characteristic it " on " or D score can comprise that the first and second features directly contact, can comprise that also the first and second features are not directly contacts but by the other feature contact between them.And, First Characteristic Second Characteristic " on ", " top " and " above " comprise First Characteristic directly over Second Characteristic and oblique upper, or only represent that the First Characteristic level height is higher than Second Characteristic.First Characteristic Second Characteristic " under ", " below " and " below " comprise First Characteristic under the Second Characteristic and tiltedly, or only represent that the First Characteristic level height is less than Second Characteristic.
Below with reference to the shock mitigation system 100 that be used for dynamic compaction machinery 1000 of Fig. 1-Fig. 2 description according to the utility model embodiment, shock mitigation system 1000 is used for the jib 300 of dynamic compaction machinery 1000 is carried out effective damping.
According to the shock mitigation system 100 of the utility model embodiment, comprise at least one oil cylinder 1, the first accumulator 2a, the second accumulator 2b, the first overflow valve 3a, the second overflow valve 3b, first throttle valve 4a, the second choke valve 4b, the first one way valve 5a and the second one way valve 5b.
As shown in Figure 1, each oil cylinder 1 includes the cylinder body 11 with inner chamber and is located at movably the interior piston 12 of inner chamber, piston 12 is separated into rod chamber 13 and rodless cavity 14 with inner chamber, and wherein piston 12 is provided with piston rod 15, and the free end of piston rod 15 extends in rod chamber 13.Particularly, in an example of the present utility model, oil cylinder 1 is two, and the spaced apart setting of along continuous straight runs (be the A direction among Fig. 1, among Fig. 2 perpendicular to the paper direction).
The first accumulator 2a is communicated with rod chamber 13 by the first asphalt channel 6a and the second accumulator 2b is communicated with rodless cavity 14 by the second asphalt channel 6b.Particularly, when piston rod 15 drive pistons 12 move downward, piston 12 can push rodless cavity 14 interior hydraulic oil so that hydraulic oil flows in the second accumulator 2b by the second asphalt channel 6b, same, when piston rod 15 drive pistons 12 moved upward, piston 12 can push rod chambers 13 interior hydraulic oil so that it flows in the first accumulator 2a by the first asphalt channel 6a.
The hydraulic oil pressure that the first overflow valve 3a is used for control the first asphalt channel 6a is not higher than predefined threshold value, and the hydraulic oil pressure that the second overflow valve 3b is used for control the second asphalt channel 6b is not higher than predefined threshold value.That is to say, when the oil pressure of the hydraulic oil in the first asphalt channel 6a is higher than predefined threshold, the first overflow valve 3a opens overflow and is not higher than described threshold value to guarantee the hydraulic oil pressure in the first asphalt channel 6a, same, when the oil pressure of the hydraulic oil in the second asphalt channel 6b is higher than predefined threshold, the second overflow valve 3b opens overflow and is not higher than described threshold value to guarantee the hydraulic oil pressure in the second asphalt channel 6b, and the hydraulic oil that is wherein overflowed by the first overflow valve 3a and the second overflow valve 3b can flow back to the first fuel tank by drainback passage 7.The purpose that the first overflow valve 3a and the second overflow valve 3b are set is not exceed predefined threshold value for the hydraulic oil pressure of controlling in the first asphalt channel 6a and the second asphalt channel 6b, guarantee shock mitigation system 100 normal, steady operations, prevent the excessive damage pipeline of oil pressure or the Other related equipment of the hydraulic oil in the first asphalt channel 6a and the second asphalt channel 6b.
The import of first throttle valve 4a is communicated with the described end of the first accumulator 2a, be first throttle valve 4a import and, the first accumulator 2a is connected with the end that the first asphalt channel 6a is communicated with, the import of the second choke valve 4b is communicated with the described end of the second accumulator 2b, the i.e. import of the second choke valve 4b and, the second accumulator 2b is connected with the end that the second asphalt channel 6b is communicated with, wherein be connected with current by pass 8 between first throttle valve 4a and the second choke valve 4b, current by pass 8 is used for guiding the hydraulic oil that flows out from the outlet of first throttle valve 4a and the second choke valve 4b and flows back to the second fuel tank.The effect of first throttle valve 4a and the second choke valve 4b is to reduce the oil pressure of the hydraulic oil in the first accumulator 2a and the second accumulator 2b, realizes the release of pressure energy.
The outlet of the first one way valve 5a is communicated with the first asphalt channel 6a and the outlet of the second one way valve 5b is communicated with the second asphalt channel 6b, be connected with drainback passage 7 between the import of the import of the first one way valve 5a and the second one way valve 5b, wherein the pressure in the current by pass 8 is lower than the pressure in the drainback passage 7.
Particularly, as shown in Figure 1, in the process that piston rod 15 drive pistons 12 move downward, because piston 12 is pressed into the hydraulic oil in the rodless cavity 14 in the second asphalt channel 6b, thereby make the oil pressure of the second asphalt channel 6b higher, much larger than current by pass 8 and the pressure of drainback passage 7 interior differential pressure actions on the second one way valve 5b, therefore the second one way valve 5b is at this moment closed condition and works to support oil pressure to the pressure-acting of the second one way valve 5b for it; When piston rod 15 drive pistons 12 oppositely move upward, because the pressure in the current by pass 8 is lower than the pressure in the drainback passage 7, this moment, the second one way valve 5b opened, namely have hydraulic oil in the first fuel tank by the drainback passage 7 second one way valve 5b that flows through, this part hydraulic oil part flows in the rodless cavity 14 to replenish the hydraulic oil in the rodless cavity 14 by the second asphalt channel 6b, guarantee shock mitigation system 100 normal operations, another part then flows in the second accumulator 2b by the second asphalt channel 6b, because the hydraulic fluid temperature in the first fuel tank is lower, and the hydraulic oil in the second accumulator 2b raises owing to the high-frequency operation of oil cylinder 1 and the second accumulator 2b, therefore the lower hydraulic oil of this part temperature fills in the second accumulator 2b, and the high-temperature liquid force feed in the second accumulator 2b is passed through the second choke valve 4b to current by pass 8 interior discharges, thisly in the second accumulator 2b, fill into low temperature hydraulic oil from the second one way valve 5b, the high-temperature liquid force feed of the second accumulator 2b has realized the interchange of heat of the second accumulator 2b by the endless form of the second choke valve 4b discharge simultaneously, prevent the second accumulator 2b because the rear analysis of hydraulic oil overheat that works long hours damages the second accumulator 2b body, and then the maintenance cost of reduction shock mitigation system 100, guarantee the stability and high efficiency work of shock mitigation system 100.Same, for the first one way valve 5a, its effect is identical with the second one way valve 5b with operating principle, repeats no more here.
According to shock mitigation system 100 of the present utility model, can be arranged on the end of the anti-hypsokinesis bar 400 of dynamic compaction machinery 1000, as shown in Figure 2, namely the end of anti-hypsokinesis bar 400 links to each other with piston rod 15, when dynamic compaction machinery 1000 carries out the ramming operation, since the release of hammer ram, the 300 internal force abrupt releases of dynamic compaction machinery 1000 jibs, original distortion becomes to returning in the other direction suddenly, thereby causes jib 300 violent reciprocal vibrations to occur.Vibrations are through jib 300, anti-hypsokinesis bar 400 is passed to shock mitigation system 100, this moment, anti-hypsokinesis bar 400 drive piston rods 15 and piston 12 moved downward, piston 12 moves downward the hydraulic oil that can compress in the rodless cavity 14, hydraulic oil in the rodless cavity 14 enters the second accumulator 2b by the second asphalt channel 6b, continuous compression along with piston 12, the hydraulic oil that enters in the second accumulator 2b is more and more, thereby make the hydraulic oil pressure power in the second accumulator 2b increasing, this pressure also increases the resistance to displacement of jib 300 and anti-hypsokinesis bar 400 accordingly, and then realization is to the cushioning effect of jib 300, in the process that piston 12 moves downward, the second overflow valve 3b is used for guaranteeing that the oil pressure in the second asphalt channel 6b is not higher than predefined threshold value, and in the process that the pressure of the second accumulator 2b increases gradually, hydraulic oil can produce certain vent flow that leads to current by pass 8 by the second choke valve 4b, realizes the release of hydraulic energy in the second accumulator 2b.Because the vibrations of jib 300 are shuttle, be that jib 300 can pump by drive piston rod 15, after piston rod 15 moves downward minimum point when moving, the second one way valve 5b is used for replenishing in rodless cavity 14 and in the second accumulator 2b the lower hydraulic oil of oil temperature, thereby guarantee on the one hand the continous-stable work of shock mitigation system 100, the oil temperature that guarantees on the other hand the hydraulic oil in the shock mitigation system 100 is unlikely to too high, realize interchange of heat, guarantee the working effect of shock mitigation system 100, wherein in the process that piston rod 15 moves upward, the first accumulator 2a, the first overflow valve 3a, the course of work of first throttle valve 4a and the first one way valve 5a and principle and piston rod 15 move downward the second accumulator 2b in the process, the second overflow valve 3b, the second choke valve 4b is identical with the second one way valve 5b's, no longer describes in detail herein.
Be appreciated that, for different dynamic compaction machinery 1000, its jib 300 desired damping effect when ramming operates is different, this moment can be by arranging shock mitigation system 100 of the present utility model and some parameters of shock mitigation system 100 being carried out corresponding improvement, force value of the nitrogen that is filled with in advance such as size, the first accumulator 2a and the second accumulator 2b of the first asphalt channel 6a and the predefined threshold value of the second asphalt channel 6b etc. is regulated the damping effect of shock mitigation system 100, thereby satisfies the damping requirement of different dynamic compaction machinery 1000 jibs 300.
The shock mitigation system 100 that is used for dynamic compaction machinery 1000 according to the utility model embodiment, can be after dynamic compaction machinery 1000 carries out ramming operation release hammer ram, effectively provide damping force to the i.e. reciprocal vibrations of two-way vibrations of jib 300, the amplitude of vibration of quick decay jib 300, make dynamic compaction machinery 1000 can enter fast next ramming operation, improve ramming efficient, reduce simultaneously jib 300 vibrations to the impact of dynamic compaction machinery 1000, improve the stability of dynamic compaction machinery 1000 working environments, comfortableness and safety, thereby prolong the application life of dynamic compaction machinery 1000 and jib 300, reduce use cost, in addition, this shock mitigation system 100 is simple in structure, structure rationally, need not increase electrical equipment and additional energy source, need not complicated operating process control and power supply, saved the energy, further reduced cost.
In addition, according to shock mitigation system 100 strong adaptabilities of the utility model embodiment, and can be made into independently module and use, existing 1000 need of dynamic compaction machinery be arranged native system at the anti-hypsokinesis bar 400 of jib 300 get final product.
In an embodiment of the present utility model, as shown in Figure 1, oil cylinder 1 is two, and the rod chamber 13 of each oil cylinder 1 is connected with the first asphalt channel 6a, and the rodless cavity 14 of each oil cylinder 1 is connected with the second asphalt channel 6b.Certainly, the utility model is not limited to this, in other embodiment of the present utility model, oil cylinder 1 can also be a plurality of, for example 4,6 or more, that is to say, for those skilled in the art, can the number of oil cylinder 1 be set to reach best damping effect according to actual dynamic compaction machinery 1000 jibs 300 required damping effects.
Advantageously, the first asphalt channel 6a is communicated with the top of rod chamber 13 and the second asphalt channel 6b is communicated with the bottom of rodless cavity 14.Can take full advantage of thus the interior space of chamber of rod chamber 13 and rodless cavity 14.
As shown in Figure 1, the first overflow valve 3a is pilot operated compound relief valve, and the second overflow valve 3b also is pilot operated compound relief valve.Certainly, in another a little embodiment of the present utility model, the first overflow valve 3a and the second overflow valve 3b also can be respectively that direct-acting overflow valve or one are that pilot operated compound relief valve, one are direct-acting overflow valves.
Describe the course of work that is used for the shock mitigation system 100 of dynamic compaction machinery 1000 according to the utility model embodiment in detail below with reference to Fig. 1 and Fig. 2, wherein for convenience of description, clear, 300 amplitudes first time that drive anti-hypsokinesis bar 400 and piston rod 15 describe for moving downward as example take oil cylinder 1 as two, jib.
At first, after dynamic compaction machinery 1000 rammings discharge hammer ram, jib 300 can drive piston rod 15 by anti-hypsokinesis bar 400 and pump, because the amplitude first time of jib 300 drives piston rod 15 and moves downward, therefore piston 12 in can extruding rodless cavities 14 hydraulic oil and flow into the second accumulator 2b by the second asphalt channel 6b, along with the increase of piston 12 to bottom offset, the hydraulic oil that enters the second accumulator 2b also increases relatively, the pressure of its generation also increases gradually, this pressure makes the resistance to displacement of jib 300 and anti-hypsokinesis bar 400 constantly become large, namely be equivalent to anti-hypsokinesis bar 400 is applied a damping force, finally reach the purpose that reduces vibration amplitude and shorten the vibrations cycle.
In the process that piston rod 15 moves downward, although the pressure in the drainback passage 7 is higher than the pressure in the current by pass 8, but the hydraulic oil in the first fuel tank can not enter in the second asphalt channel 6b by the second one way valve 5b, reason is because moving downward of piston rod 15 impacted so that the oil pressure value of the hydraulic oil in the second asphalt channel 6b is in higher scope, its effect is greater than the pressure reduction of drainback passage 7 with current by pass 8, therefore the second one way valve 5b was in closed condition and played supporting oil pressure, the i.e. effect of damping force this moment.
Because can not becoming, the hydraulic energy that the hydraulic oil that absorbs among the second accumulator 2b produces produces the oppositely power source of vibrations, therefore this energy should be discharged as early as possible, namely the second choke valve 4b is in the process that the pressure of the second accumulator 2b increases gradually, hydraulic oil among the second accumulator 2b can flow back to the second fuel tank from current by pass 8 by the second choke valve 4b, along with piston 12 reaches terminal point to bottom offset, it is maximum that this vent flow reaches, thereby realize the release of the second accumulator 2b internal pressure energy.Here, need to prove, " this vent flow reach maximum " refers in the process that piston moves downward this displacement terminal point, reaches maximum from the flow of the hydraulic oil of the second choke valve 4b earial drainage.
When actual ramming operation, after may causing owing to the hammer ram lifting altitude is too high hammer ram to discharge, the swing energy of jib 300 is too high, piston 12 moved downward and the hydraulic oil in the rodless cavity 14 can be pressed in the second asphalt channel 6b and the second accumulator 2b fast this moment, thereby cause the oil pressure in the second asphalt channel 6b too high, surpass predefined pressure threshold, the second overflow valve 3b overflow work this moment, in the second asphalt channel 6b in overflow to the first fuel tank, and then make the oil pressure in the second asphalt channel 6b not be higher than described pressure threshold to guarantee shock mitigation system 100 stable normal operations in part hydraulic oil.
When piston 12 oppositely moves upward, piston 12 can enter in the first accumulator 2a by extruding rod chamber 13 interior hydraulic oil, the oil pressure that this moment, the first overflow valve 3a controlled in the first asphalt channel 6a is no more than predefined threshold value, first throttle valve 4a is used for discharging the hydraulic energy in the first accumulator 2a, that is to say, when piston 12 moves upward, the first overflow valve 3a, the course of work of first throttle valve 4a and the first accumulator 2a and principle and piston move downward the second overflow valve 3b in the process, the second choke valve 4b is identical with the second accumulator 2b's, therefore is not described in detail herein.
The second one way valve 5b is for the process that moves upward at piston 12, in the first fuel tank, in rodless cavity 14 and the second accumulator 2b, fill into hydraulic oil by drainback passage 7 and the second one way valve 5b successively, thereby guarantee on the one hand the continous-stable work of oil cylinder 1, realize on the other hand the interchange of heat to the second accumulator 2b, prevent that oil cylinder 1 and the second accumulator 2b high-frequency operation from causing oil temperature too high, damage shock mitigation system 100, and then reduce use cost.Wherein the first one way valve 5a is used for moving downward process at piston 12, in the first fuel tank, in rod chamber 13 and the first accumulator 2a, fill into hydraulic oil by drainback passage 7 and the first one way valve 5a successively, realize the continuous operation of oil cylinder 1 and to the interchange of heat of the first accumulator 2a.
The shock mitigation system 100 that is used for dynamic compaction machinery 1000 according to the utility model embodiment has well shock-absorbing function to jib 300, can greatly improve stability, comfortableness and the safety of dynamic compaction machinery 1000 when work.
Below with reference to the dynamic compaction machinery 1000 of Fig. 2 description according to the utility model embodiment.
As shown in Figure 2, the lower end of jib 300 is located on the car body 200 pivotly, at least one anti-hypsokinesis bar 400 is located at respectively between jib 300 and the car body 200, the free end of the piston rod 15 of shock mitigation system 100 links to each other with the rear end of anti-hypsokinesis bar 400, balanced component 500 is located on the car body 200 with balance jib 300, lifting subassembly 600 comprises suspension hook 610 and is located at suspension hook 610 belows, is used for hanging the detacher 620 of holding hammer ram, and control module is used for 600 work of control lifting subassembly.
Be appreciated that for different dynamic compaction machinery 1000, can many anti-hypsokinesis bars 400 be set according to its jib 300 actual required damping effects, accordingly, shock mitigation system 100 also arranges a plurality of oil cylinders 1, thereby realizes best damping effect, prolongs the application life of dynamic compaction machinery 1000.
According to the dynamic compaction machinery 1000 of the utility model embodiment, by shock mitigation system 100 is set, when operating, ramming can carry out damping to jib 300 better, and the amplitude of vibration of the jib 300 of decaying fast improves ramming efficient, prolongs the application life of dynamic compaction machinery 1000.
Consist of according to other of the dynamic compaction machinery 1000 of the utility model embodiment that to wait be prior art, for example dynamic compaction machinery 1000 adopts caterpillar belt structure to improve the stability of car body 200, dynamic compaction machinery 1000 also can have a plurality of stabilizing legs to keep the balance of dynamic compaction machinery 1000 when the ramming, the basic structure of these dynamic compaction machineries 1000 and operating principle etc. have been known by affiliated technical field personnel, therefore describe in detail no longer one by one here.
In the description of this manual, the description of reference term " embodiment ", " some embodiment ", " illustrative examples ", " example ", " concrete example " or " some examples " etc. means to be contained at least one embodiment of the present utility model or the example in conjunction with specific features, structure, material or the characteristics of this embodiment or example description.In this manual, the schematic statement of above-mentioned term not necessarily referred to identical embodiment or example.And the specific features of description, structure, material or characteristics can be with suitable mode combinations in any one or more embodiment or example.
Although illustrated and described embodiment of the present utility model, those having ordinary skill in the art will appreciate that: in the situation that do not break away from principle of the present utility model and aim can be carried out multiple variation, modification, replacement and modification to these embodiment, scope of the present utility model is limited by claim and equivalent thereof.
Claims (9)
1. a shock mitigation system that is used for dynamic compaction machinery is characterized in that, comprising:
At least one oil cylinder, each described oil cylinder include the cylinder body with inner chamber and are located at movably the interior piston of described inner chamber, and described piston is separated into rod chamber and rodless cavity with described inner chamber;
The first and second accumulators, described the first accumulator are communicated with described rod chamber by the first asphalt channel and described the second accumulator is communicated with described rodless cavity by the second asphalt channel;
The first and second overflow valves, the hydraulic oil pressure that described the first and second overflow valves can be respectively applied to control in described the first and second asphalt channels is not higher than predefined threshold value;
The first and second choke valves, the import of described the first and second choke valves are communicated with a described end of described the first and second accumulators respectively, and are connected with current by pass between the outlet of described the first and second choke valves;
The first and second one way valves, the outlet of described the first and second one way valves is communicated with described the first and second asphalt channels respectively, and be connected with drainback passage between the import of described the first and second one way valves, the pressure in the wherein said current by pass is lower than the pressure in the described drainback passage.
2. shock mitigation system according to claim 1 is characterized in that, described oil cylinder is two, and the described rod chamber of each described oil cylinder is connected with described the first asphalt channel, and the described rodless cavity of each described oil cylinder is connected with described the second asphalt channel.
3. shock mitigation system according to claim 1 is characterized in that, described the first asphalt channel is communicated with the top of described rod chamber and described the second asphalt channel is communicated with the bottom of described rodless cavity.
4. shock mitigation system according to claim 1 is characterized in that, described the first overflow valve is pilot operated compound relief valve or direct-acting overflow valve, and described the second overflow valve is pilot operated compound relief valve or direct-acting overflow valve.
5. shock mitigation system according to claim 1 is characterized in that, also comprises: the first and second fuel tanks, and the end of wherein said drainback passage is communicated with described the first fuel tank, and the end of described current by pass is communicated with described the second fuel tank.
6. a dynamic compaction machinery is characterized in that, comprising:
Car body;
Jib, the lower end of described jib are located on the described car body pivotly;
At least one anti-hypsokinesis bar, each described anti-hypsokinesis bar is located at respectively between described jib and the described car body;
Each described shock mitigation system according to claim 1-5, the free end of the described piston rod of wherein said shock mitigation system links to each other with the rear end of described anti-hypsokinesis bar;
Balanced component, described balanced component are located on the described car body with the described jib of balance;
Lifting subassembly, described lifting subassembly comprise suspension hook and be located at described suspension hook below, be used for hanging the detacher of holding hammer ram, and the front end of the hoisting rope of wherein said dynamic compaction machinery links to each other with described suspension hook; With
Be used for controlling the control module of described lifting subassembly work.
7. dynamic compaction machinery according to claim 6 is characterized in that, described anti-hypsokinesis bar is two, and the described oil cylinder of described shock mitigation system is two.
8. dynamic compaction machinery according to claim 7 is characterized in that, turns up the soil and be arranged between described jib and the described car body in described two anti-hypsokinesis bar along continuous straight runs intervals.
9. dynamic compaction machinery according to claim 6 is characterized in that, described balanced component comprises:
Man-like shelf, described man-like shelf are located on the described car body and are positioned at the rear side of described jib and spaced apart with described jib;
Jib stay cord, the two ends of described jib stay cord link to each other with the upper end of described jib and the top of described man-like shelf respectively.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220262242 CN202688982U (en) | 2012-06-05 | 2012-06-05 | Vibration reducing system for dynamic compactor and dynamic compactor therewith |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220262242 CN202688982U (en) | 2012-06-05 | 2012-06-05 | Vibration reducing system for dynamic compactor and dynamic compactor therewith |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202688982U true CN202688982U (en) | 2013-01-23 |
Family
ID=47544622
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201220262242 Expired - Lifetime CN202688982U (en) | 2012-06-05 | 2012-06-05 | Vibration reducing system for dynamic compactor and dynamic compactor therewith |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN202688982U (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103215941A (en) * | 2013-03-28 | 2013-07-24 | 三一重工股份有限公司 | Dynamic compactor convenient for expanding ramming energy |
| CN103526740A (en) * | 2013-10-24 | 2014-01-22 | 徐工集团工程机械股份有限公司 | System and method for back-lean preventing control of dynamic compaction machine |
| CN104226876A (en) * | 2013-06-11 | 2014-12-24 | 镇江市申茂机械有限公司 | Hydraulic damping device |
| CN104420458A (en) * | 2013-09-05 | 2015-03-18 | 北汽福田汽车股份有限公司 | Oil cylinder driving lifting mechanism and dynamic compactor |
| CN103452091B (en) * | 2012-06-05 | 2016-05-04 | 北汽福田汽车股份有限公司 | For the shock mitigation system of dynamic compaction machinery and there is its dynamic compaction machinery |
| CN116219994A (en) * | 2023-03-13 | 2023-06-06 | 江苏筑港建设集团有限公司 | Energy-saving dynamic compaction construction automatic device |
-
2012
- 2012-06-05 CN CN 201220262242 patent/CN202688982U/en not_active Expired - Lifetime
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103452091B (en) * | 2012-06-05 | 2016-05-04 | 北汽福田汽车股份有限公司 | For the shock mitigation system of dynamic compaction machinery and there is its dynamic compaction machinery |
| CN103215941A (en) * | 2013-03-28 | 2013-07-24 | 三一重工股份有限公司 | Dynamic compactor convenient for expanding ramming energy |
| CN103215941B (en) * | 2013-03-28 | 2016-04-06 | 三一重工股份有限公司 | A kind of being convenient to expands the dynamic compaction machinery ramming energy |
| CN104226876A (en) * | 2013-06-11 | 2014-12-24 | 镇江市申茂机械有限公司 | Hydraulic damping device |
| CN104420458A (en) * | 2013-09-05 | 2015-03-18 | 北汽福田汽车股份有限公司 | Oil cylinder driving lifting mechanism and dynamic compactor |
| CN103526740A (en) * | 2013-10-24 | 2014-01-22 | 徐工集团工程机械股份有限公司 | System and method for back-lean preventing control of dynamic compaction machine |
| CN116219994A (en) * | 2023-03-13 | 2023-06-06 | 江苏筑港建设集团有限公司 | Energy-saving dynamic compaction construction automatic device |
| CN116219994B (en) * | 2023-03-13 | 2023-10-20 | 江苏筑港建设集团有限公司 | Automatic damping device for energy-saving dynamic compaction construction |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN202688982U (en) | Vibration reducing system for dynamic compactor and dynamic compactor therewith | |
| CN101736729B (en) | Lifting mechanism of free dropping type forced ramming machine with hammer | |
| CN104477798B (en) | The principal arm luffing control system of crane and crane | |
| CN102758812A (en) | Buffer device of hydraulic oil cylinder | |
| CN103452091B (en) | For the shock mitigation system of dynamic compaction machinery and there is its dynamic compaction machinery | |
| CN103742490B (en) | Mixed power pumping unit | |
| CN101839004B (en) | Balance excavator and hydraulic control system thereof | |
| CN102943496B (en) | Potential energy recycling system of movable arm of excavator | |
| CN201686980U (en) | Lifting mechanism of hammer free-falling type dynamic compactor | |
| CN202139584U (en) | Walking type dynamic compaction machine | |
| CN203296034U (en) | Damping system and dynamic consolidation machine with damping system | |
| CN202881925U (en) | Shock mitigation system for main engine of dynamic consolidation machine and dynamic consolidation machine provided with the same | |
| CN202833424U (en) | Buffer device of hydrocylinder | |
| CN113339361A (en) | Six-degree-of-freedom hydraulic pressure balancing device | |
| CN202658594U (en) | Device for preventing dynamic compaction machine arm frame from swaying and dynamic compaction machine | |
| CN103541342A (en) | Damping system for main machine of dynamic compactor and dynamic compactor with same | |
| CN202301249U (en) | Electro-hydraulic push rod-dedicated integrated valve bank | |
| CN215058618U (en) | Six-degree-of-freedom hydraulic pressure balancing device | |
| CN219262807U (en) | Hydraulic buffer system and engineering machinery | |
| CN114411868B (en) | Hydraulic system, breaking hammer, pile hammer and rammer | |
| CN103287980A (en) | Cantilever crane vertical lift control system | |
| CN211813080U (en) | Regenerative self-adaptive balance valve device | |
| CN203238682U (en) | Elastic rubber belt energy storage type potential energy recycling control system for movable arms of loader | |
| CN203238683U (en) | Tension spring energy storage device type loading machine movable arm potential energy recovery regenerative device | |
| SU1481336A1 (en) | Scraper with gas-lubricated bucket |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20130123 Effective date of abandoning: 20160504 |
|
| AV01 | Patent right actively abandoned |
Granted publication date: 20130123 Effective date of abandoning: 20160504 |
|
| C25 | Abandonment of patent right or utility model to avoid double patenting |