CN203603138U - Anti-back-tilting control system of dynamic compactor - Google Patents
Anti-back-tilting control system of dynamic compactor Download PDFInfo
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- CN203603138U CN203603138U CN201320657713.6U CN201320657713U CN203603138U CN 203603138 U CN203603138 U CN 203603138U CN 201320657713 U CN201320657713 U CN 201320657713U CN 203603138 U CN203603138 U CN 203603138U
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- oil cylinder
- strut
- spring
- jib
- guide rod
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Abstract
The utility model relates to an anti-back-titling control system of a dynamic compactor. The anti-back-titling control system comprises a supporting rod, a guide rod, an oil cylinder, a spring and a hydraulic control device. A limit part is arranged on the outer side wall of one end of the guide rod, and the supporting rod is a hollow pillar with an open end and a closed end. The closed end of the supporting rod is fixedly connected with the oil cylinder. The guide rod is inserted into a cavity of the supporting rod from the open end of the supporting rod, and the limit part is located outside the supporting rod. The spring is installed outside the guide rod in a sleeved mode and located between the limit part and the open end of the supporting rod. In the working process of the dynamic compactor, the hydraulic control device provides constant pretightening force for the supporting rod through the oil cylinder, so that the precompression amount of the spring is kept constant under different working conditions. The bouncing amount of a boom can be minimized after a pounder is unhooked, and the problem that in the prior art, after the pounder is unhooked, the boom shakes excessively is solved.
Description
Technical field
The utility model relates to engineering machinery field, relates in particular to the anti-back-tipping control system of a kind of dynamic compaction machinery.
Background technology
At present, as shown in Figure 1, in use, when hammer ram 1 ' breaks off relations, the spring in anti-squat system 2 ' will have certain decrement to dynamic compaction machinery, and during than Compress Spring not, the rebound amount of jib is little.Because the operating angle (operating angle of jib refers to the angle between jib and horizontal plane) of jib 3 ' is a scope, therefore the spring in anti-squat system 2 ' can not guarantee all the time certain pretightning force within the scope of the operating angle of jib 3 ', or the spring in anti-squat system 2 ' does not have pretightning force at all when jib 3 ' work, after Condition of Sudden Unloading, jib 3 ' will produce and significantly rock and vibrations repeatedly under the effect of luffing drag-line 4 ' power.
Existing anti-squat system 2 ' can only play the function that jib 3 ' does not turn over afterwards, can not effectively control jib 3 ' and rock.Dynamic compaction machinery when construction jib rocks greatly, makes car load gravity center shift, causes variable-amplitude steel wire rope 6 ' to slide down or raising line 5 ' slides down, and has increased the danger of constructing.Jib 3 ' rocks and causes that greatly car load rocks, and also can make operating personnel feel very uncomfortable.
Utility model content
The purpose of this utility model is to propose a kind of dynamic compaction machinery anti-back-tipping control system, and the rebound amount minimum that it can make jib after rammer unhooking has solved in prior art jib after rammer unhooking and rocked excessive problem.
For achieving the above object, the utility model provides following technical scheme:
The anti-back-tipping control system of a kind of dynamic compaction machinery, it comprises strut, guide rod, oil cylinder, spring and hydraulic control device, wherein: the lateral wall of described guide rod one end has limiting section; Described strut is a hollow posts with openend and blind end; The blind end of described strut is fixedly connected with described oil cylinder; Described guide rod inserts the cavity of described strut from the openend of described strut, and described limiting section is positioned at outside described strut; Described spring housing is contained in outside described guide rod, and between described limiting section and the openend of described strut; In the dynamic compaction machinery course of work, described hydraulic control device for described strut provides constant pretightning force, makes described spring under different operating modes be maintained constant pre compressed magnitude by described oil cylinder.
Further, described hydraulic control device comprises reducing valve and equalizing valve, wherein: the oil-out of described reducing valve is connected with the oil-in of described equalizing valve; The oil-out of described equalizing valve is connected with the rodless cavity of described oil cylinder; The pilot pressure hydraulic fluid port of described equalizing valve is used for connecting luffing hoist brake pressure oil.
Further, described equalizing valve is one-way balance valve.
Further, the cylinder barrel of described oil cylinder bottom is connected or welds with the blind end bolt of described strut.
Further, described oil cylinder is plunger case.
Based on the arbitrary technical scheme in technique scheme, the utility model embodiment at least can produce following technique effect:
Because the utility model is provided with strut, guide rod, oil cylinder, spring and hydraulic control device, in the dynamic compaction machinery course of work, hydraulic control device provides constant pretightning force by oil cylinder for strut, make the spring under different operating modes be maintained constant pre compressed magnitude, therefore jib plays arm from 0 degree to the first operating angle, spring does not compress, and anti-back-tipping control system is zero to jib active force; Jib plays arm from the first operating angle to the second operating angle, spring-compressed, and anti-back-tipping control system has active force to jib, and amount of force is less than the constant pretightning force that the oil cylinder of setting provides for strut; Jib is from the second operating angle to the three operating angles, and by spring-compressed and cylinder piston rod motion, anti-back-tipping control system is always the constant pretightning force that the oil cylinder of setting provides for strut to jib active force; When the bounce-back of rammer unhooking jib, oil cylinder is a rigidity cylinder, the piston rod of oil cylinder keeps original position motionless, jib bounce-back drives guide rod, act on strut and oil cylinder by Compress Spring again, thereby passive storage power in spring, provide support reaction to jib, absorb by spring the energy that luffing drag-line, jib etc. store, and effectively controlling jib by the stroke of spring swings or shakes, make the rebound amount minimum of jib after rammer unhooking, solved in prior art jib after rammer unhooking and rocked excessive problem.
Accompanying drawing explanation
Accompanying drawing described herein is used to provide further understanding of the present utility model, forms the application's a part, and schematic description and description of the present utility model is used for explaining the utility model, does not form improper restriction of the present utility model.In the accompanying drawings:
Fig. 1 is the structural representation of dynamic compaction machinery in prior art;
Fig. 2 is the part-structure schematic diagram of anti-back-tipping control system one embodiment of dynamic compaction machinery provided by the utility model;
Fig. 3 is the decomposing schematic representation of Fig. 2;
Fig. 4 is the principle schematic of hydraulic control device one embodiment in the anti-back-tipping control system of dynamic compaction machinery provided by the utility model;
Fig. 5 is the force analysis schematic diagram of dynamic compaction machinery.
The specific embodiment
For object, technical scheme and advantage that the utility model is implemented are clearer, below in conjunction with the accompanying drawing in the utility model embodiment, the technical scheme in the utility model embodiment is further described in more detail.In the accompanying drawings, same or similar label represents same or similar element or has the element of identical or similar functions from start to finish.Described embodiment is the utility model part embodiment, rather than whole embodiment.Be exemplary below by the embodiment being 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.Based on the embodiment in the utility model, those of ordinary skills are not making the every other embodiment obtaining under creative work prerequisite, all belong to the scope of the utility model protection.Below in conjunction with accompanying drawing, embodiment of the present utility model is elaborated.
In description of the present utility model, it will be appreciated that, term " " center ", " longitudinally ", " 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 the utility model and simplified characterization for convenience of description, 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 the restriction to the utility model protection domain.
As in Figure 2-4, the anti-back-tipping control system of dynamic compaction machinery provided by the utility model comprises strut 1, guide rod 2, oil cylinder 3, spring 4 and hydraulic control device 5.Wherein: strut 1 is a hollow cylinder with openend and blind end, the blind end of strut 1 is fixedly connected with the cylinder barrel bottom of oil cylinder 3, and for example the two carries out bolt connection by flange, also can adopt the mode of welding to be fixed together.The openend of strut 1 is used for inserting guide rod 2.
The lateral wall of one end of guide rod 2 has limiting section 21, and guide rod 2 inserts the cavity of strut 1 from the openend of strut 1, and limiting section 21 is positioned at outside strut 1.The external part of guide rod 2 is connected with the jib 6 of dynamic compaction machinery by bearing pin clamp.Limiting section 21 can be a circle flange, can be also the projection that interval arranges and forms a circle, and it can be one-body molded with guide rod 2, and it can adopt existing integrated method to obtain, and also can be fixed on by the mode of welding the lateral wall of guide rod 2.
The piston rod of oil cylinder 3 is connected with the turntable of dynamic compaction machinery by bearing pin clamp.Oil cylinder 3 is as executing agency, and the jib 6 that is the dynamic compaction machinery in the course of work by strut 1 and guide rod 2 provides pretightning force and reaction of bearing.In the present embodiment, what oil cylinder 3 adopted is plunger case, but is not limited to this.
Carry in hammer or de-hammer process at dynamic compaction machinery, hydraulic control device 5 provides constant pretightning force or reaction of bearing by oil cylinder 3 for strut 1, and this active force is delivered to spring 4 and guide rod 2 successively via strut 1, is finally applied on jib 6.By making different operating mode lower springs 4 be maintained constant pre compressed magnitude, thereby make jib 6 be subject to constant pretightning force.
When the assembling of the anti-back-tipping control system of dynamic compaction machinery provided by the utility model, as shown in Figure 5, first, use bolt and nut by the cylinder barrel bottom of oil cylinder 3 be fixedly connected with the blind end of strut 1; Then, spring 4 is sleeved on guide rod 2; Afterwards the guide rod 2 that is set with spring 4 is fitted together with strut 1, assemble complete.
When the anti-back-tipping control system of dynamic compaction machinery provided by the utility model is assemblied on dynamic compaction machinery, the external part of the guide rod of whole anti-squat system 2 is assembled by the hinge on the jib 6 coxopodite arms of bearing pin clamp and dynamic compaction machinery, then the hinge on the turntable of the piston rod of oil cylinder 3 and dynamic compaction machinery is fitted together.
As the preferred embodiment of hydraulic control device 5, as shown in Figure 4, hydraulic control device 5 comprises reducing valve 51 and equalizing valve 52, wherein: the oil-out of reducing valve 51 is connected with the oil-in of equalizing valve 52, the oil-out of equalizing valve 52 is connected with the rodless cavity 31 of oil cylinder 3, and reducing valve 51 is used for providing low pressure oil for oil cylinder 3.What equalizing valve 52 adopted is one-way balance valve, and equalizing valve 52 is as the drainback passage of oil cylinder 3, and its pilot pressure hydraulic fluid port is connected with luffing hoist brake, and being used for provides height two-stage reverse back pressure for oil cylinder 3.
The course of work of the present utility model is as follows:
(1) carry in hammer process at dynamic compaction machinery, initiatively low pressure oil supply of hydraulic control device 5, oil cylinder 3 provides constant pretightning force F
0:
When jib 6 in 0 degree in the first operating angle θ 1 scope time, guide rod 2 and spring 4 are not all subject to the pressure-acting of jib 6, now oil cylinder 3 does not bear external applied load.High pressure fuel source is after reducing valve 51 decompressions, provide a low pressure oil to oil cylinder 3, pressure size and the product of the cross-sectional area of the piston rod of oil cylinder 3 of low pressure oil are just in time the size of described constant pretightning force F0, now the piston rod of oil cylinder 3 is overhanging, until to entirely stretching state, that is to say, the pretightning force size that now oil cylinder 3 provides is F
0.
In the time that jib 6 is in the first operating angle θ 1 to second operating angle θ 2 scopes, guide rod 2 and spring 4 are all subject to the pressure-acting of jib 6, now oil cylinder 3 bears the counter-force effect of spring 4, the elastic force F<F0 of spring 4, and oil cylinder 3 still provides a pretightning force F
0, in entirely stretching state.
When jib 6 in the second operating angle θ 2 in the 3rd operating angle θ 3 scopes time, guide rod 2 and spring 4 are all subject to the pressure-acting of jib 6, now oil cylinder 3 bears the counter-force effect of spring 4, the elastic force F=F of spring 4
0, the length of spring 4 remains unchanged, and oil cylinder 3 is also to provide a pretightning force F
0.Now, jib 6 is done luffing action, and luffing hoist brake pressure oil acts on the first guide cavity of equalizing valve 52, and equalizing valve 52 is in low reverse back pressure state.When luffing rises, the piston rod pressurized of oil cylinder 3 is retracted, and the fluid of oil cylinder 3 is through equalizing valve 52 and reducing valve 51, reverse flow oil sump tank; When luffing falls, hydraulic control device 5 is to oil cylinder 3 fuel feeding, and the piston rod of oil cylinder 3 stretches out, but the length of spring 4 remains unchanged, and the pretightning force of spring 4 remains unchanged, and is still F0.
That is to say, hammer ram 9 is under non-unhook state, and oil cylinder 3 provides a constant pretightning force F0 to jib 6.
(2) in the de-hammer process of dynamic compaction machinery, oil cylinder 3 provides large reaction of bearing:
In the time that luffing action stops, the pressure release of luffing hoist brake, the also pressure release thereupon of the first guide cavity of equalizing valve 52, equalizing valve 52 is in the reverse back pressure state of height.After unhook, jib 6 is given 4 one impact compress power of spring, after spring 4 pressurizeds, power is passed to oil cylinder 3.But due to the high back pressure of equalizing valve 52, the fluid that oil cylinder is 3 li can form high pressure, make the power output of oil cylinder 3 become large, the piston rod of final oil cylinder 3 keeps original position motionless, and the active force of jib 6 is absorbed by spring 4 completely.
That is to say, in hammer ram 9 unhook processes, oil cylinder 3 provides a large reaction of bearing that approaches rigidity to jib 6.
The utility model can also provide a kind of anti-hypsokinesis control method of dynamic compaction machinery that adopts the anti-back-tipping control system of dynamic compaction machinery in the various embodiments described above, and it comprises the following steps:
Under the static state of hammer ram 9, according to the stressing conditions of the jib 6 of dynamic compaction machinery, calculate the needed constant pretightning force size of strut 1 in the anti-back-tipping control system of dynamic compaction machinery;
According to the constant pretightning force calculating, regulate rodless cavity hydraulic fluid pressure in oil cylinder 3 by the hydraulic control device 5 in the anti-back-tipping control system of dynamic compaction machinery, until the support force that oil cylinder 3 provides for strut 1 is constant pretightning force size.
The pressure oil that reducing valve 51 exports can directly enter the rodless cavity of oil cylinder 3 through the one way valve 521 in equalizing valve 52, the piston rod of realizing oil cylinder 3 stretches out; In the time of oil cylinder 3 passive compression, pressure oil oppositely flows back to through equalizing valve 52, thereby produces reverse back pressure.Because the pilot pressure hydraulic fluid port of equalizing valve 52 connects luffing hoist brake pressure oil.In the time that the luffing hoist brake pressure oil of dynamic compaction machinery has pressure, the elevator action of dynamic compaction machinery, now equalizing valve is reverse low back pressure, can make oil cylinder 3 remain unchanged for spring 4 provides pretightning force; When luffing hoist brake pressure oil is during without pressure, elevator stops action, and now equalizing valve 5 is reverse high back pressure, and when jib 6 rebounds, the passive pressurized of oil cylinder 3, can produce the large reaction of bearing that approaches rigidity.
In above-mentioned steps, calculate the needed constant pretightning force F of strut 1 in the anti-back-tipping control system of dynamic compaction machinery
0size, specifically comprises:
1) setup parameter: the initial compression amount Δ l of the anti-back-tipping control system medi-spring 4 of dynamic compaction machinery, the decrement Δ l' of bounce-back rear spring 4, oil cylinder 3 is that in the first hinge A, the anti-back-tipping control system of dynamic compaction machinery, guide rod 2 is that the second hinge B, jib 6 are tri-joint mechanism C with the hinge of turntable with the hinge of jib 6 with the hinge of turntable.
2) image data: the distance s of the first hinge A and the second hinge B, the spacing b of the second hinge B and tri-joint mechanism C, the spacing c of the first hinge A and tri-joint mechanism C, jib 6 length L, the spacing a of jib 6 centers of gravity and tri-joint mechanism, the operating angle θ of jib 6, main chord and lower main chord angle α on jib 6 coxopodite arms, angle β between the first hinge and line and the horizontal plane of tri-joint mechanism, before hammer ram 9 breaks off relations and the jib 6 gravity Gs of hammer ram 9 under remaining static
jib(G1 in Fig. 5), hammer ram 9 gravity G
hammer ram(G2 in Fig. 5) and the tensile force f of raising line 8 to jib 6
raising line.
3) jib 6 is carried out to force analysis, according to jib 6 torque equilibrium equations, calculate luffing drag-line 7 power F
luffing drag-line, particularly, according to following formula:
F
anti-hypsokinesis=k Δ l
R
jib=α cos θ
R
hammer ram=Lcos θ
R
jib=acos θ
G
jibr
jib+ G
hammer ramr
hammer ram+ F
anti-hypsokinesisr
anti-hypsokinesis=F
raising liner
raising line+ F
luffing drag-liner
luffing drag-linecalculate F
luffing drag-line.
Wherein, by length s, b, c and the b on three articles of limits in the triangle that in Fig. 5, the first hinge A, the second hinge B and tri-joint mechanism C surround and the angle on c limit (180-θ-β-α/2), can be in the hope of R
anti-hypsokinesis.
In like manner, according to known triangle sine and cosine theorem and triangle area formula, can obtain respectively R by elevator, man-like shelf position and corresponding angle
raising line, R
luffing drag-line.
4) dynamic compaction machinery is carried in hammer process, luffing drag-line 7, raising line 8, jib 6 and anti-back-tipping control system have all stored energy, the luffing drag-line 7 of (after de-hammer) after hammer ram 9 discharges, the energy of raising line 8 and jib 6 is all stored into energy on anti-back-tipping control system after discharging and shifting, carry the jib 6 in hammer process, luffing drag-line 7, raising line 8 all remains static, obtain the energy that the spring 4 in anti-hypsokinesis system now stores, therefore, calculate the initial compression amount of spring 4, calculate the energy (scope of rocking of jib 6) storing in dynamic compaction machinery unhook rear defence back-tipping control system, again by the scope of rocking of rational selection jib, can know the needed constant pretightning force size of strut in anti-back-tipping control system.The step of the reduction length of calculating unhook rear spring 4 is as follows:
(4-1) according to following formula:
P
static energy=P
luffing drag-line+ P
raising line+ P
spring+ P
jib
Above-mentioned various in, E is modulus of elasticity, A is cross-sectional area, k is rigidity, F is the axial force acting on luffing drag-line or spring or raising line or jib, Δ l is stroke (or deflection), l is the length of luffing drag-line or spring or raising line or jib.
Wherein: P
luffing drag-line, P
raising line, P
spring, P
jibcan adopt P
iany expression formula try to achieve.And because the initial compression amount Δ l of spring 4 is unknown number, therefore P
springfor the function of Δ l, i.e. P
static energyfor the function of Δ l.
(4-2) according to following formula:
The P that step (4-1) is calculated
static energyin substitution above formula, try to achieve the decrement Δ l' of bounce-back rear spring 4, the decrement Δ l' of the rear spring that therefore rebounds 4 is the function of the initial compression amount Δ l of spring 4.
(4-3) by asking for the minimum value of the decrement Δ l' of bounce-back rear spring in step (4-2), calculate the initial compression amount Δ l of spring 4.
(5) according to the initial compression amount Δ l of the spring 4 drawing in step (4-3), by its substitution formula F
springin=k Δ l, calculate the needed constant pretightning force F of strut 1 in the anti-back-tipping control system of dynamic compaction machinery
0.
In above-mentioned steps, because the length L of current jib 6 products is on the market divided into 19m, 22m, 25m etc., if the horizontal length that need to make jib 6 stretch out, the projection length L cos θ of jib 6 on horizontal plane is identical, now need to adjust the stroke of oil cylinder 3, supply stroke.Therefore, provide constant pretightning force F at control oil cylinder 3
0under precondition, also need according to the length L of different jibs 6, calculate the stroke of supplying of oil cylinder 3, and control the stroke of supplying of oil cylinder 3.
Finally should be noted that: above embodiment is only in order to illustrate that the technical solution of the utility model is not intended to limit; Although the utility model is had been described in detail with reference to preferred embodiment, those of ordinary skill in the field are to be understood that: still can modify or part technical characterictic is equal to replacement the specific embodiment of the present utility model; And not departing from the spirit of technical solutions of the utility model, it all should be encompassed in the middle of the technical scheme scope of the utility model request protection.
Claims (5)
1. the anti-back-tipping control system of dynamic compaction machinery,
It is characterized in that:
Comprise strut, guide rod, oil cylinder, spring and hydraulic control device, wherein:
The lateral wall of described guide rod one end has limiting section;
Described strut is a hollow posts with openend and blind end;
The blind end of described strut is fixedly connected with described oil cylinder;
Described guide rod inserts the cavity of described strut from the openend of described strut, and described limiting section is positioned at outside described strut;
Described spring housing is contained in outside described guide rod, and between described limiting section and the openend of described strut;
In the dynamic compaction machinery course of work, described hydraulic control device for described strut provides constant pretightning force, makes described spring under different operating modes be maintained constant pre compressed magnitude by described oil cylinder.
2. the system as claimed in claim 1,
It is characterized in that:
Described hydraulic control device comprises reducing valve and equalizing valve, wherein:
The oil-out of described reducing valve is connected with the oil-in of described equalizing valve;
The oil-out of described equalizing valve is connected with the rodless cavity of described oil cylinder;
The pilot pressure hydraulic fluid port of described equalizing valve is used for connecting luffing hoist brake pressure oil.
3. system as claimed in claim 2,
It is characterized in that:
Described equalizing valve is one-way balance valve.
4. system as claimed in claim 3,
It is characterized in that:
The cylinder barrel bottom of described oil cylinder is connected or welds with the blind end bolt of described strut.
5. system as claimed in claim 4,
It is characterized in that:
Described oil cylinder is plunger case.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320657713.6U CN203603138U (en) | 2013-10-24 | 2013-10-24 | Anti-back-tilting control system of dynamic compactor |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320657713.6U CN203603138U (en) | 2013-10-24 | 2013-10-24 | Anti-back-tilting control system of dynamic compactor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203603138U true CN203603138U (en) | 2014-05-21 |
Family
ID=50715819
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201320657713.6U Withdrawn - After Issue CN203603138U (en) | 2013-10-24 | 2013-10-24 | Anti-back-tilting control system of dynamic compactor |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
-
2013
- 2013-10-24 CN CN201320657713.6U patent/CN203603138U/en not_active Withdrawn - After Issue
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
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| AV01 | Patent right actively abandoned |
Granted publication date: 20140521 Effective date of abandoning: 20150923 |
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