CN102398866A - Crane luffing control valve and crane luffing hydraulic system - Google Patents
Crane luffing control valve and crane luffing hydraulic system Download PDFInfo
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- CN102398866A CN102398866A CN2011103302512A CN201110330251A CN102398866A CN 102398866 A CN102398866 A CN 102398866A CN 2011103302512 A CN2011103302512 A CN 2011103302512A CN 201110330251 A CN201110330251 A CN 201110330251A CN 102398866 A CN102398866 A CN 102398866A
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Abstract
The invention discloses a crane luffing control valve, comprising a valve body and a valve core. The valve body is provided with an oil inlet, a first oil outlet, a second oil outlet and an oil return opening. One end of the valve core seals the second oil outlet shoulder and is equipped with a first groove for connecting the oil inlet and the second oil outlet; the other end of the valve core is equipped with a second groove for connecting the second oil outlet and the oil return opening; at least one of the second groove and the first groove has an axial spacing less than a width of an under cut groove of the second oil outlet. The control valve can substantially enhance jiggle characteristic of the crane during luffing and eliminate jitter phenomenon of a handle in a micro opening. The invention also discloses a crane luffing hydraulic system equipped with the crane luffing control valve.
Description
Technical field
The present invention relates to technical field of engineering machinery, particularly control the fluid control valve that the hoisting crane principal arm carries out the luffing action.The invention still further relates to the crane amplitude variation hydraulic efficiency pressure system that is provided with said control cock.
Background technology
Car hosit is before carrying out hoisting operation; Need be the principal arm luffing to certain angle, when carrying out hoisting operation, principal arm need frequently carry out luffing and rise and fall; When especially through luffing weight accurately being located, the stationarity of its luffing and fine motion property are particularly important.
Please refer to Fig. 1, Fig. 1 is the luffing mechanism schematic diagram of existing car hosit.
As shown in the figure, HYDRAULIC CONTROL SYSTEM amplitude oil cylinder 4 ' piston rod 3 ' when stretching out, make that hoisting crane principal arm 2 ' around the hinge left-hand revolution, change angle α increases, thereby realize the purpose of amplitude-variation hoisting, be called for short luffing and rise; During amplitude oil cylinder piston rod 3 ' withdrawal, make that hoisting crane principal arm 2 ' around the hinge clickwise, change angle α reduces, thereby realize the purpose that luffing falls, be called for short luffing and fall.
Please refer to Fig. 2, Fig. 3, Fig. 2 is the hydraulic luffing systematic schematic diagram of car hosit principal arm; Fig. 3 is the cut-away view of luffing control cock shown in Fig. 2.
As shown in the figure, when crane amplitude variation control handle 1 is in meta, no luffing action; The pressure that the valve rod outlet of control cock 5 is passed to flow divider valve 3 is zero; The oil inlet pressure of control cock 5 only need overcome the spring force of flow divider valve 3, promptly opens flow divider valve 3, lets out back the T mouth thereby will get into luffing control cock P mouth fluid; At this moment the delivery pressure of hydraulic oil pump is especially little, thus purpose of energy saving when having reached attonity.
The luffing time-out, control handle 1 action, the spool switching-over of control cock 5, the fluid of its oil inlet gets into the rodless cavity 7 of amplitude oil cylinder, and piston rod 9 is stretched out, and realizes that luffing plays action; Because the oil inlet of spool is provided with pressure-compensated valve 4, spool is when different positions, though load constantly changes; But, thereby guarantee one regime flow to be provided to amplitude oil cylinder because the continuous adjustment of pressure-compensated valve 4 makes the inlet outlet pressure differential of spool remain a steady state value; Reach spool when the aperture position that fixes; Certain flow is just arranged, and the amplitude oil cylinder kinematic velocity does not receive the influence of load variations, and other flow returns the T mouth through flow divider valve.
When luffing falls, when control handle 1 moves from the meta to the dominant bit, the spool switching-over, a part of rod chamber 8 through rod chamber oil inlet entering oil cylinder of the fluid of its oil inlet is opened balance cock 10 simultaneously and is made piston rod 9 withdrawals, realizes that luffing falls to moving; Another part flows back to fuel tank through flow divider valve 3; Because the oil inlet of spool is provided with pressure-compensated valve 4, spool is when different positions, though load constantly changes; But, thereby guarantee one regime flow to be provided to the rod chamber 8 of oil cylinder because the continuous adjustment of pressure-compensated valve 4 makes the inlet outlet pressure differential of spool remain a steady state value; Reach spool when the aperture position that fixes; Certain flow is just arranged, and the oil cylinder kinematic velocity does not receive the influence of load variations, and other flow is through 3 times T mouths of flow divider valve.
The above-mentioned medium and small tonnage crane amplitude variation hydraulic efficiency pressure system of rising and falling is a ratio system, and its control cock is integrated and connected through valve body by a plurality of valves and other element.When luffing falls; The flow that gets into amplitude oil cylinder is only relevant with the spool open area, when load variations, can cause the pressure of main valve outlet to change; And the variation of main valve delivery pressure can cause the valve rod of flow divider valve 3 to move; The flow divider valve shake occurs, thereby the flow and the pressure that get into amplitude oil cylinder rod chamber 8 are changed, cause system pressure shake to occur.
To this, can adopt the deadweight that utilizes principal arm as shown in Figure 4 to realize the luffing hydraulic efficiency pressure system that luffing falls.
When luffing control handle 1 was in meta and luffing lifting working condition, this luffing hydraulic efficiency pressure system was similar with the principle of work of above-mentioned luffing hydraulic efficiency pressure system, and its difference just is the luffing operating mode that falls.
When luffing falls, when control handle 1 moves, when control oil makes control cock 5 switching-overs, open balance cock 10 from the meta to the dominant bit, the fluid of amplitude oil cylinder rodless cavity 7 is flowed out, the fluid of rodless cavity 7 flows back to fuel tank through change-over valve, and rod chamber 8 is through the self-priming repairing.The balance cock opening that control handle 1 is just corresponding certain in certain position makes the opening of balance cock 10 not receive the influence of rodless cavity 7, and is only relevant with the position of control handle 1.
The mode that this luffing falls, the deadweight of dependence principal arm is carried out luffing and is fallen, and speed is controlled by handle, and fine motion property is better, jitter phenomenon can not occur.But complicated balance cock need be mated in this system, and changes mode, and productive costs is higher.
Therefore, how to upgrade heavy-duty machine and carry out the fine motion property of luffing when falling, the shake when eliminating crack mouthful of handle is the present technical issues that need to address of those skilled in the art.
Summary of the invention
First purpose of the present invention provides a kind of crane amplitude variation control cock.This control cock can significantly upgrade heavy-duty machine and carry out the fine motion property of luffing when falling, and the jitter phenomenon when eliminating crack mouthful of handle.
Second purpose of the present invention provides a kind of crane amplitude variation hydraulic efficiency pressure system that is provided with said crane amplitude variation control cock.
In order to realize above-mentioned first purpose, the present invention provides a kind of crane amplitude variation control cock, comprises valve body and spool, and said valve body is provided with oil inlet, first oil outlet, second oil outlet and return opening; Shoulder one end of said second oil outlet of said seal spool is provided with first groove that is used to be communicated with the said oil inlet and second oil outlet; The other end is provided with second groove that is used to be communicated with said second oil outlet and return opening, and the axial spacing of at least one said second groove and said first groove is less than the undercut groove width of said second oil outlet.
Preferably, the axial spacing of each said second groove and said first groove is all less than the undercut groove width of said second oil outlet.
Preferably, the difference of said undercut groove width and said spacing equals crack mouthful of stroke of the said oil inlet of said spool conducting and second oil outlet.
Preferably, the width of said second groove and the degree of depth become big outward gradually from the inner.
Preferably, have three control positioies: at first control position, said oil inlet is communicated with first oil outlet, and said second oil outlet is communicated with return opening; At second control position, said oil inlet is communicated with second oil outlet, and said first oil outlet is communicated with return opening; At the 3rd control position, the said oil inlet and first oil outlet all end, and said second oil outlet is communicated with return opening.
Preferably, be specially three position four-way directional control valve.
Preferably, this control cock is integrated with pressure-compensated valve, and said pressure-compensated valve is located on the oil-feed oil circuit of said valve body, and at first control position of said control cock, its control port is communicated with said first oil outlet; At second control position of said control cock, its control port is communicated with said second oil outlet; At the 3rd control position of said control cock, its control port is communicated with said return opening.
Preferably, this control cock is integrated with the secondary by pass valve, and the oil inlet of said secondary by pass valve is communicated with said second oil outlet, oil outlet is communicated with said return opening.
In order to realize above-mentioned second purpose; The present invention also provides a kind of crane amplitude variation hydraulic efficiency pressure system; Comprise amplitude oil cylinder, control cock and flow divider valve; Said control cock is above-mentioned each described crane amplitude variation control cock, and first oil outlet of this control cock is communicated with the rodless cavity of said amplitude oil cylinder, and second oil outlet is communicated with the rod chamber of said amplitude oil cylinder; The oil inlet of said flow divider valve is communicated with the oil inlet of said valve body, oil outlet is communicated with the return opening of said valve body, and has three mode of operations: at first mode of operation, its control port is communicated with first oil outlet of said control cock; At second mode of operation, its control port is communicated with second oil outlet of said control cock; At the 3rd mode of operation, its control port is communicated with the return opening of said control cock.
Preferably, be provided with main by pass valve between the oil inlet of said control cock and the return opening.
Crane amplitude variation control cock provided by the present invention is applied to be provided with the crane amplitude variation hydraulic efficiency pressure system of flow divider valve; At the luffing time-out; Its oil inlet is communicated with first oil outlet, second oil outlet is communicated with return opening, and flow divider valve worked before handle reached the standard-sized sheet mouth, and system is always the ratio characteristic; When luffing fell, its oil inlet was communicated with second oil outlet, first oil outlet is communicated with return opening, in crack mouthful of stage of handle; Flow part through spool gets into the rod chamber of amplitude oil cylinder, and another part is not through the direct oil sump tank of flow divider valve, but flows back to fuel tank through the bypass tool head piece; This moment, system had the characteristic of bypass throttling governing, and flow divider valve is inoperative, and system pressure is more steady; Thereby eliminated the shake in crack mouthful of stage, promoted fine motion property; The handle process is after the crack mouth stage, and the bypass tool head piece is closed, and flow divider valve works, and system becomes the ratio characteristic.This in the luffing mode that time-division in two stages control that falls, stationarity and fine motion property that luffing is fallen have obtained remarkable lifting, have not only eliminated jitter phenomenon, and make control accuracy also obtain comprehensive raising.
In addition, this control cock can reduce the requirement to balance cock, reduces the response pressure of balance cock, reaches energy-conservation effect.Owing to only improve to second groove on the spool, do not change the basis of control cock basic structure, the control cock after therefore improving does not increase cost.
Crane amplitude variation hydraulic efficiency pressure system provided by the present invention has adopted above-mentioned crane amplitude variation control cock; Because above-mentioned crane amplitude variation control cock has above-mentioned technique effect, the crane amplitude variation hydraulic efficiency pressure system with this crane amplitude variation control cock also should possess the corresponding techniques effect.
Description of drawings
Fig. 1 is the luffing mechanism schematic diagram of car hosit;
Fig. 2 is the hydraulic luffing systematic schematic diagram of car hosit principal arm;
Fig. 3 is the cut-away view of luffing control cock shown in Fig. 2;
Fig. 4 utilizes the deadweight of principal arm to realize the luffing hydraulic efficiency pressure system that luffing falls;
Fig. 5 is the cut-away view of crane amplitude variation control cock provided by the present invention;
Fig. 6 is the local enlarged diagram at I position among Fig. 5;
Position view when Fig. 7 finishes for spool described in Fig. 6 moves to " dead band ";
Fig. 8 is communicated with through first groove with second hydraulic fluid port for spool shown in Fig. 6 moves to oil inlet, and second hydraulic fluid port and the position view of return opening when second groove is communicated with;
Fig. 9 is communicated with through first groove with second hydraulic fluid port for spool shown in Fig. 6 moves to oil inlet, and the position view when second hydraulic fluid port and return opening disconnection;
Position view when Figure 10 moves to full-gear for spool shown in Fig. 6;
Figure 11 is the simplification schematic diagram of bypass tool flow liquid pressing system;
Figure 12 is the local structure scheme drawing of spool shown in Fig. 6.
Among the figure:
1 '. weight 2 '. principal arm 3 '. piston rod 4 '. amplitude oil cylinder
1. control handle 2. main by pass valve 3. flow divider valves 4. pressure-compensated valves 5. control cock 6. secondary by pass valves 7. rodless cavities 8. rod chambers 9. piston rods 10. balance cocks 11. amplitude oil cylinder rod chamber oil-feeds 12. amplitude oil cylinder rodless cavity oil-feeds 13. shuttle valves 14. control cock oil inlets
20. valve body 30. spools 21. oil-feeds 22. first fuel-displaced 23. second oil outlets, 24. oil returns, 31. shoulder 31-1., the first groove 31-2., second grooves
The specific embodiment
Core of the present invention provides a kind of crane amplitude variation control cock.This control cock can significantly upgrade heavy-duty machine and carry out the fine motion property of luffing when falling, and the jitter phenomenon when eliminating crack mouthful of handle.
Another core of the present invention provides a kind of crane amplitude variation hydraulic efficiency pressure system that is provided with said crane amplitude variation control cock.
In order to make those skilled in the art person understand the present invention program better, the present invention is done further detailed description below in conjunction with the accompanying drawing and the specific embodiment.
The term in expression orientation such as " upper and lower, left and right " among this paper is based on the position relation of accompanying drawing; Should it be interpreted as the absolute qualification to protection domain; In like manner; Terms such as " first, second " only is for the ease of describing, and with the different constituent elementss that differentiation has same names, does not represent successively or the primary and secondary relation.
Please refer to Fig. 5, Fig. 5 is the cut-away view of crane amplitude variation control cock provided by the present invention.
In a kind of specific embodiment, crane amplitude variation control cock provided by the invention is specially the 3-position 4-way pilot operated directional control valve, comprises valve body 20 and spool 30, and valve body 20 is provided with oil inlet 21, first oil outlet 22, second oil outlet 23 and return opening 24.
Have the undercut groove corresponding to each hydraulic fluid port in the valve body 20, wherein the undercut groove of return opening 24 is two, and one of them is positioned at the left side of the first oil outlet undercut groove, and another is positioned at the right side of the said second oil outlet undercut groove; Spool 30 is provided with a plurality of shoulders, the conducting or the disconnection that realize each oil circuit with cooperating of each undercut groove during through the shoulder sway, thus reach the switching-over purpose.
During work, oil inlet 21 is communicated with pressure oil-source, and first oil outlet 22 is communicated with the rodless cavity of amplitude oil cylinder, and second oil outlet 23 is communicated with the rod chamber of amplitude oil cylinder.
The structure of this control cock and existing control cock basic identical (seeing Fig. 2, Fig. 3) has three control positioies: at first control position, oil inlet 21 is communicated with first oil outlet 22, and second oil outlet 23 is communicated with return opening 24; At second control position, oil inlet 21 is communicated with second oil outlet 23, and first oil outlet 22 is communicated with return opening 24; At the 3rd control position, the oil inlet 21 and first oil outlet 22 all end, and said second oil outlet 23 is communicated with return opening 24; Difference just is the structure of spool.
Please refer to Fig. 6, Fig. 7, Fig. 6 is the local enlarged diagram at I position among Fig. 5; Position view when Fig. 7 finishes for spool described in Fig. 6 moves to " dead band ".
As shown in the figure; Has the shoulder 31 that when meta, seals the second oil outlet undercut groove on the spool 30; The left end of this shoulder 31 is along being circumferentially with a plurality of first groove 31-1 that are used to be communicated with the oil inlet 21 and second oil outlet 23; When spool 30 moves to right, the open area of the oil inlet 21 and second oil outlet 23 is increased gradually from zero; The right-hand member of shoulder 31 when spool 30 moves to left, can make second oil outlet 23 and the open area of return opening 24 from zero gradually increase through the second groove 31-2 along being circumferentially with a plurality of second groove 31-2 that are used to be communicated with second oil outlet 23 and return opening 24.
The improvements of spool 30 are, the length of at least one second groove 31-2 prolongs to the direction of the first groove 31-1, the axial spacing L of itself and the first groove 31-1
2Undercut groove width L less than second oil outlet
1, to guarantee the crack mouthful of stage in control cock, oil inlet 21 is communicated with second hydraulic fluid port 23 and open area increases gradually, and simultaneously, second hydraulic fluid port 23 is communicated with return opening 24 and open area reduces gradually.
The hydraulic principle of its simplification is shown in figure 11, and in the moving process of the spool of control cock from the meta to the standard-sized sheet, total flow is Q; Restriction B reduced when restriction A increased; The flow that gets into oil cylinder increases, and the fluid of restriction B oil sump tank reduces, and restriction B plays the effect of bypass throttling.
Please in the lump with reference to figure 8 to Figure 10, Fig. 8 is communicated with through first groove with second hydraulic fluid port for spool shown in Fig. 6 moves to oil inlet, and second hydraulic fluid port and return opening warp second groove position view when being communicated with; Fig. 9 is communicated with through first groove with second hydraulic fluid port for spool shown in Fig. 6 moves to oil inlet, and the position view when second hydraulic fluid port and return opening disconnection; Position view when Figure 10 moves to full-gear for spool shown in Fig. 6.
The concrete principle of work of above-mentioned control cock is following:
At the luffing time-out, its oil inlet 21 is communicated with first oil outlet 22, second oil outlet 23 is communicated with return opening 24, and flow divider valve worked before spool reached the standard-sized sheet mouth, and system is always the ratio characteristic.
When luffing fell, its oil inlet 21 was communicated with second oil outlet 23, first oil outlet 22 is communicated with the distance L that spool 30 initial movable are minimum with return opening 24
3The time, there is not fluid to pass through spool 30, be " dead band " concerning spool 30 these sections, crossed " dead band " afterwards, because the first groove 31-1 of spool 30 has less fluid through spool 30.
In crack mouthful of stage of spool; Return opening 24 oil returns; The pressure reduction that spool 30 is imported and exported is smaller; Flow divider valve can't be opened, and pump the oil inlet 21 of the whole control of access valves of pressure oil that come this moment, and through being divided into two-way behind the spool: one road second oil outlet 23 from control cock flows out the rod chamber that gets into oil cylinder makes the oil cylinder withdrawal; Surplus oil liquid flows back to T mouth (shown in arrow) from another road through return opening 24; This moment, system had the characteristic of bypass throttling governing, and flow divider valve is inoperative, and system pressure is more steady, thereby had eliminated the shake in crack mouthful of stage, had promoted fine motion property.
When spool has been crossed crack port area; Return opening 24 is closed, and the fluid that flows into from oil inlet 21 all gets into amplitude oil cylinder, and this moment, spool pressure reduction was opened certain aperture with flow divider valve; Make unnecessary fluid flow back to fuel tank from flow divider valve, at this moment system returns to original ratio characteristic again.
This in the luffing mode that time-division in two stages control that falls, stationarity and fine motion property that luffing is fallen have obtained remarkable lifting, have not only eliminated jitter phenomenon, and make control accuracy also obtain comprehensive raising.
In addition, this control cock can reduce the requirement to balance cock, reduces the response pressure of balance cock, reaches energy-conservation effect.Owing to only improve to second groove on the spool, do not change the basis of control cock basic structure, the control cock after therefore improving does not increase cost.
In order more accurately to prevent control cock crack mouthful of stage shake, the difference DELTA L of undercut groove width and spacing should equal crack mouthful of stroke of the spool 30 conducting oil inlets 21 and second oil outlet 23.So, when the crack mouthful of stage of control cock finished, spool 30 can break off second oil outlet 23 and return opening 24 immediately, thereby changes whole hydraulic efficiency pressure system into the ratio characteristic by the bypass tool properties of flow in time.
The oil inlet 21 that above-mentioned crack mouthful stroke refers to control cock is during with 23 conductings of second oil outlet, begins the stroke that oil-feeds cause shake spool 30 when this shake relaxes gradually from spool 30.Generally speaking, the trip is less than 1/3rd of spool 30 conducting oil inlets 21 and second oil outlet, 23 total kilometragies, and this paper does not do qualification to its concrete numerical value and relative scale, and those skilled in the art can design according to actual needs.
Making improved can be the part second groove 31-2, if adopt this kind mode, second groove that then prolongs and do not prolong can be circumferentially spaced apart along shoulder 31.Certainly, making improved also can be whole second groove 31-2.
Please refer to Figure 12, Figure 12 is the local structure scheme drawing of spool shown in Fig. 6.
After the improvement, the general shape of the second groove 31-2 is shown in figure 12, and it is big that its width and the degree of depth become from the inner outward gradually.Certainly; The concrete shape of the second groove 31-2 is not limited thereto; Every can second oil outlet 23 connection with return opening 24 crack mouthful of stage, and open area all can be realized the object of the invention with mobile the diminishing gradually of spool 30 until second groove of closing.
Can control cock and pressure-compensated valve 4 be carried out the system integration, pressure-compensated valve 4 is located on the oil-feed oil circuit of valve body 31, and at first control position of control cock, its control port is communicated with first oil outlet 22; At second control position of control cock, its control port is communicated with second oil outlet 23; At the 3rd control position of control cock, its control port is communicated with the return opening 24 of control cock.
Can also be on control cock integrated secondary by pass valve 6, the oil inlet of secondary by pass valve 6 is communicated with second oil outlet 23 of control cock, oil outlet is communicated with the return opening 24 of control cock.
Certainly, above-mentioned crane amplitude variation control cock only is a kind of preferred version, specifically is not limited thereto, and can make pointed adjustment according to actual needs on this basis, thereby obtain different embodiment.
Except above-mentioned crane amplitude variation control cock, the present invention also provides a kind of crane amplitude variation hydraulic efficiency pressure system, comprises amplitude oil cylinder, control cock 5 and flow divider valve 3, and wherein control cock 5 is above-mentioned each described crane amplitude variation control cock (can referring to Fig. 2).
The oil inlet of flow divider valve 3 is communicated with the oil inlet 21 of control cock 5, oil outlet is communicated with the return opening 24 of control cock 5; And have three mode of operations: at first mode of operation; Its control port is communicated with first oil outlet 22 of control cock, corresponding to first control position of control cock 5; At second mode of operation, its control port is communicated with second oil outlet 23 of control cock 5, corresponding to second control position of control cock 5; At the 3rd mode of operation, its control port is communicated with the return opening 24 of control cock 5, corresponding to the 3rd control position of control cock 5.
In order to protect hydraulic efficiency pressure system, be provided with main by pass valve 2 between the oil inlet of control cock 5 and the return opening, all the other structures please refer to prior art, just repeat no more.
More than crane amplitude variation control cock provided by the present invention and crane amplitude variation hydraulic efficiency pressure system have been carried out detailed introduction.Used concrete example among this paper principle of the present invention and embodiment are set forth, the explanation of above embodiment just is used for helping to understand core concept of the present invention.Should be pointed out that for those skilled in the art, under the prerequisite that does not break away from the principle of the invention, can also carry out some improvement and modification to the present invention, these improvement and modification also fall in the protection domain of claim of the present invention.
Claims (10)
1. a crane amplitude variation control cock comprises valve body and spool, and said valve body is provided with oil inlet, first oil outlet, second oil outlet and return opening; Shoulder one end of said second oil outlet of said seal spool is provided with first groove that is used to be communicated with the said oil inlet and second oil outlet; The other end is provided with second groove that is used to be communicated with said second oil outlet and return opening; It is characterized in that the axial spacing of at least one said second groove and said first groove is less than the undercut groove width of said second oil outlet.
2. crane amplitude variation control cock according to claim 1 is characterized in that, the axial spacing of each said second groove and said first groove is all less than the undercut groove width of said second oil outlet.
3. the crane amplitude variation according to claim 1 and 2 control cock of rising and falling is characterized in that, the difference of said undercut groove width and said spacing equals crack mouthful of stroke of the said oil inlet of said spool conducting and second oil outlet.
4. crane amplitude variation control cock according to claim 1 and 2 is characterized in that, it is big that the width of said second groove and the degree of depth become from the inner outward gradually.
5. crane amplitude variation control cock according to claim 3 is characterized in that, has three control positioies: at first control position, said oil inlet is communicated with first oil outlet, and said second oil outlet is communicated with return opening; At second control position, said oil inlet is communicated with second oil outlet, and said first oil outlet is communicated with return opening; At the 3rd control position, the said oil inlet and first oil outlet all end, and said second oil outlet is communicated with return opening.
6. crane amplitude variation control cock according to claim 5 is characterized in that, is specially three position four-way directional control valve.
7. according to claim 5 or 6 described crane amplitude variation control cock; It is characterized in that this control cock is integrated with pressure-compensated valve, said pressure-compensated valve is located on the oil-feed oil circuit of said valve body; At first control position of said control cock, its control port is communicated with said first oil outlet; At second control position of said control cock, its control port is communicated with said second oil outlet; At the 3rd control position of said control cock, its control port is communicated with said return opening.
8. according to claim 5 or 6 described crane amplitude variation control cock, it is characterized in that this control cock is integrated with the secondary by pass valve, the oil inlet of said secondary by pass valve is communicated with said second oil outlet, oil outlet is communicated with said return opening.
9. crane amplitude variation hydraulic efficiency pressure system; Comprise amplitude oil cylinder, control cock and flow divider valve; It is characterized in that; Said control cock is aforesaid right requirement 1 to 8 each described crane amplitude variation control cock, and first oil outlet of this control cock is communicated with the rodless cavity of said amplitude oil cylinder, and second oil outlet is communicated with the rod chamber of said amplitude oil cylinder; The oil inlet of said flow divider valve is communicated with the oil inlet of said valve body, oil outlet is communicated with the return opening of said valve body, and has three mode of operations: at first mode of operation, its control port is communicated with first oil outlet of said control cock; At second mode of operation, its control port is communicated with second oil outlet of said control cock; At the 3rd mode of operation, its control port is communicated with the return opening of said control cock.
10. crane amplitude variation hydraulic efficiency pressure system according to claim 9 is characterized in that, is provided with main by pass valve between the oil inlet of said control cock and the return opening.
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| CN 201110330251 CN102398866B (en) | 2011-10-26 | 2011-10-26 | Crane luffing control valve and crane luffing hydraulic system |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102661298A (en) * | 2012-05-04 | 2012-09-12 | 徐州重型机械有限公司 | Hydraulic valve and crane provided with same |
| CN103723640A (en) * | 2013-12-25 | 2014-04-16 | 三一汽车起重机械有限公司 | Amplitude falling hydraulic system and engineering machinery |
| CN105201943A (en) * | 2015-01-23 | 2015-12-30 | 徐州重型机械有限公司 | Reversing valve, oil cylinder falling control valve and crane amplitude variation system |
| CN106672870A (en) * | 2016-12-22 | 2017-05-17 | 徐州海伦哲专用车辆股份有限公司 | Insulated folding arm high-altitude operation car with amplitude limiting control valve and amplitude limiting method |
| CN112551398A (en) * | 2020-12-08 | 2021-03-26 | 三一汽车起重机械有限公司 | Self-weight amplitude-falling hydraulic control method and system and crane |
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| CN102661298A (en) * | 2012-05-04 | 2012-09-12 | 徐州重型机械有限公司 | Hydraulic valve and crane provided with same |
| CN102661298B (en) * | 2012-05-04 | 2016-02-24 | 徐州重型机械有限公司 | A kind of hydrovalve and there is this hydrovalve hoist |
| CN103723640A (en) * | 2013-12-25 | 2014-04-16 | 三一汽车起重机械有限公司 | Amplitude falling hydraulic system and engineering machinery |
| CN105201943A (en) * | 2015-01-23 | 2015-12-30 | 徐州重型机械有限公司 | Reversing valve, oil cylinder falling control valve and crane amplitude variation system |
| CN105201943B (en) * | 2015-01-23 | 2017-05-03 | 徐州重型机械有限公司 | Reversing valve, oil cylinder falling control valve and crane amplitude variation system |
| CN106672870A (en) * | 2016-12-22 | 2017-05-17 | 徐州海伦哲专用车辆股份有限公司 | Insulated folding arm high-altitude operation car with amplitude limiting control valve and amplitude limiting method |
| CN106672870B (en) * | 2016-12-22 | 2022-05-17 | 徐州海伦哲专用车辆股份有限公司 | Insulated folding arm high-altitude operation vehicle with amplitude limiting control valve and amplitude limiting method |
| CN112551398A (en) * | 2020-12-08 | 2021-03-26 | 三一汽车起重机械有限公司 | Self-weight amplitude-falling hydraulic control method and system and crane |
| CN112551398B (en) * | 2020-12-08 | 2023-03-10 | 三一汽车起重机械有限公司 | Self-weight dropping hydraulic control method and system and crane |
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