CN102398866B - 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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- CN102398866B CN102398866B CN 201110330251 CN201110330251A CN102398866B CN 102398866 B CN102398866 B CN 102398866B CN 201110330251 CN201110330251 CN 201110330251 CN 201110330251 A CN201110330251 A CN 201110330251A CN 102398866 B CN102398866 B CN 102398866B
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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 main arm of crane carries out the luffing action.The invention still further relates to the crane variable-amplitude hydraulic system that is provided with described control cock.
Background technology
Car hosit is before carrying out hoisting operation, need to be the principal arm luffing to certain angle, while carrying out hoisting operation, principal arm need to frequently carry out luffing and rise and fall, while especially by luffing, weight accurately being located, the stationarity of its luffing and fine motion 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 ' while stretching out, make that main arm of crane 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 ' retraction, make that main arm of crane 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, the hydraulic amplitude conversion system schematic diagram that Fig. 2 is the car hosit principal arm; The cut-away view that Fig. 3 is luffing control cock shown in Fig. 2.
As shown in the figure, when crane amplitude variation control handle 1 during in meta, without luffing, move, the pressure that the valve rod outlet of control cock 5 is passed to flow divider valve 3 is zero, the inlet pressure of control cock 5 only need overcome the spring force of flow divider valve 3, opens flow divider valve 3, thereby will enter luffing control cock P mouth fluid, lets out back the T mouth, at this moment the delivery pressure of hydraulic oil pump is especially little, thus energy-conservation purpose while having reached attonity.
When luffing rises, control handle 1 action, the spool commutation of control cock 5, the fluid of its oil inlet enters 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, although load constantly changes, but due to the continuous adjustment of pressure-compensated valve 4, make the inlet outlet pressure differential of spool remain a steady state value, thereby guarantee to provide a regime flow to amplitude oil cylinder, reach spool when a fixing aperture position, certain flow is just arranged, and the amplitude oil cylinder kinematic velocity is not subject to the impact of load variations, and other flow returns the T mouth by flow divider valve.
When luffing falls, when control handle 1 moves from the meta to the dominant bit, the spool commutation, the fluid part of its oil inlet enters the rod chamber 8 of oil cylinder by the rod chamber oil inlet, open balance cock 10 simultaneously piston rod 9 is retracted, and realizes that luffing falls to moving; Another part flows back to fuel tank by flow divider valve 3; Because the oil inlet of spool is provided with pressure-compensated valve 4, spool is when different positions, although load constantly changes, but due to the continuous adjustment of pressure-compensated valve 4, make the inlet outlet pressure differential of spool remain a steady state value, thereby guarantee to provide a regime flow to the rod chamber 8 of oil cylinder, reach spool when a fixing aperture position, certain flow is just arranged, and cylinder movement speed is not subject to the impact of load variations, and other flow is by 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 ratio system, and its control cock is integrated and connected by valve body by a plurality of valves and other element.When luffing falls, the flow that enters 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 enter 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 variable amplitude hydraulic system that luffing falls.
When luffing control handle 1, during in meta and luffing lifting working condition, this variable amplitude hydraulic system is similar to the principle of work of above-mentioned variable amplitude hydraulic system, and its difference just is the luffing operating mode that falls.
When luffing falls, when control handle 1 moves from the meta to the dominant bit, when control oil makes control cock 5 commutation, open balance cock 10, the fluid of amplitude oil cylinder rodless cavity 7 is flowed out, the fluid of rodless cavity 7 flows back to fuel tank by change-over valve, and rod chamber 8 is by the self-priming repairing.Control handle 1 is corresponding certain balance cock opening just in certain position, makes the opening of balance cock 10 not be subject to the impact of rodless cavity 7, 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 is better, not there will be jitter phenomenon.But this system need to be mated complicated balance cock, and change mode, productive costs is higher.
Therefore, how lift crane carries out the fine motion of luffing while falling, and the shake while eliminating crack mouthful of handle, be the current technical issues that need to address of those skilled in the art.
Summary of the invention
The first purpose of the present invention is to provide a kind of crane variable-amplitude control valve.This control cock significantly lift crane is carried out the fine motion of luffing while falling, and the jitter phenomenon while eliminating crack mouthful of handle.
The second purpose of the present invention is to provide a kind of crane variable-amplitude hydraulic system that is provided with described crane variable-amplitude control valve.
In order to realize above-mentioned the first purpose, the invention provides a kind of crane variable-amplitude control valve, comprise valve body and spool, described valve body is provided with oil inlet, the first oil outlet, the second oil outlet and return opening; Shoulder one end of described the second oil outlet of described seal spool is provided with for being communicated with the first groove of described oil inlet and the second oil outlet, the other end is provided with for being communicated with the second groove of described the second oil outlet and return opening, and the axial spacing of at least one described the second groove and described the first groove is less than the undercut groove width of described the second oil outlet.
Preferably, the axial spacing of each described the second groove and described the first groove all is less than the undercut groove width of described the second oil outlet.
Preferably, the difference of described undercut groove width and described spacing equals crack mouthful of stroke of the described oil inlet of described spool conducting and the second oil outlet.
Preferably, the width of described the second groove and the degree of depth become large outward gradually from the inner.
Preferably, have three control positioies: at the first control position, described oil inlet is communicated with the first oil outlet, and described the second oil outlet is communicated with return opening; At the second control position, described oil inlet is communicated with the second oil outlet, and described the first oil outlet is communicated with return opening; At the 3rd control position, described oil inlet and the first oil outlet all end, and described the 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 described pressure-compensated valve is located on the oil-feed oil circuit of described valve body, and at the first control position of described control cock, its control port is communicated with described the first oil outlet; At the second control position of described control cock, its control port is communicated with described the second oil outlet; At the 3rd control position of described control cock, its control port is communicated with described return opening.
Preferably, this control cock is integrated with the secondary by pass valve, and the oil inlet of described secondary by pass valve is communicated with described the second oil outlet, oil outlet is communicated with described return opening.
In order to realize above-mentioned the second purpose, the present invention also provides a kind of crane variable-amplitude hydraulic system, comprise amplitude oil cylinder, control cock and flow divider valve, described control cock is the described crane variable-amplitude control valve of above-mentioned any one, the first oil outlet of this control cock is communicated with the rodless cavity of described amplitude oil cylinder, and the second oil outlet is communicated with the rod chamber of described amplitude oil cylinder; The oil inlet of described flow divider valve is communicated with the oil inlet of described valve body, oil outlet is communicated with the return opening of described valve body, and has three mode of operations: at the first mode of operation, its control port is communicated with the first oil outlet of described control cock; At the second mode of operation, its control port is communicated with the second oil outlet of described control cock; At the 3rd mode of operation, its control port is communicated with the return opening of described control cock.
Preferably, be provided with main by pass valve between the oil inlet of described control cock and return opening.
Crane variable-amplitude control valve provided by the present invention is applied to be provided with the crane variable-amplitude hydraulic system of flow divider valve, when luffing rises, its oil inlet is communicated with the first oil outlet, the second oil outlet is communicated with return opening, and handle reaches flow divider valve before open and works, and system is always the ratio characteristic; When luffing falls, its oil inlet is communicated with the second oil outlet, the first oil outlet is communicated with return opening, in the crack mouthful of stage of handle, the flow part of process spool enters the rod chamber of amplitude oil cylinder, and another part is not through the direct oil sump tank of flow divider valve, but flow back to fuel tank by the bypass tool head piece, now system has the characteristic of bypass throttle speed 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; Handle is after crack mouthful of 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 are controlled that falls, the stationarity that luffing is fallen and fine motion 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 being improved for the second groove on spool, do not change the basis of control cock basic structure, the control cock after therefore improving does not increase cost.
Crane variable-amplitude hydraulic system provided by the present invention has adopted above-mentioned crane variable-amplitude control valve, because above-mentioned crane variable-amplitude control valve has above-mentioned technique effect, the crane variable-amplitude hydraulic system with this crane variable-amplitude control valve also should possess corresponding technique effect.
The accompanying drawing explanation
The luffing mechanism schematic diagram that Fig. 1 is car hosit;
The hydraulic amplitude conversion system schematic diagram that Fig. 2 is the car hosit principal arm;
The cut-away view that Fig. 3 is luffing control cock shown in Fig. 2;
Fig. 4 utilizes the deadweight of principal arm to realize the variable amplitude hydraulic system that luffing falls;
The cut-away view that Fig. 5 is crane variable-amplitude control valve provided by the present invention;
The local enlarged diagram that Fig. 6 is I position in Fig. 5;
Fig. 7 is the position view of spool described in Fig. 6 when moving to " dead band " and finishing;
Fig. 8 is that spool shown in Fig. 6 moves to oil inlet and is communicated with through the first groove with the second hydraulic fluid port, and the second hydraulic fluid port and the position view of return opening when the second groove is communicated with;
Fig. 9 is that spool shown in Fig. 6 moves to oil inlet and is communicated with through the first groove with the second hydraulic fluid port, and the second hydraulic fluid port and the return opening position view while disconnecting;
Figure 10 is position view when shown in Fig. 6, spool moves to full-gear;
The simplification schematic diagram that Figure 11 is the bypass throttle hydraulic efficiency pressure system;
The local structure schematic diagram that Figure 12 is spool shown in Fig. 6.
In figure:
1 '. weight 2 '. principal arm 3 '. piston rod 4 '. amplitude oil cylinder
1. main by pass valve 3. flow divider valve 4. pressure-compensated valve 5. control cock 6. secondary by pass valve 7. rodless cavity 8. rod chamber 9. piston rod 10. balance cock 11. amplitude oil cylinder rod chamber oil-feed 12. amplitude oil cylinder rodless cavity oil-feed 13. shuttle valve 14. control cock oil inlets of control handle 2.
20. fuel-displaced 23. second oil outlet 24. oil return 31. shoulder 31-1. first groove 31-2. the second grooves of valve body 30. spool 21. oil-feeds 22. first
The specific embodiment
Core of the present invention is to provide a kind of crane variable-amplitude control valve.This control cock significantly lift crane is carried out the fine motion of luffing while falling, and the jitter phenomenon while eliminating crack mouthful of handle.
Another core of the present invention is to provide a kind of crane variable-amplitude hydraulic system that is provided with described crane variable-amplitude control valve.
In order to make those skilled in the art person understand better the present invention program, below in conjunction with the drawings and specific embodiments, the present invention is described in further detail.
The term in expression orientation such as " upper and lower, left and right " herein is based on the position relationship of accompanying drawing; should not be understood as the absolute restriction to protection domain; in like manner; terms such as " first, second " is only for convenience of description; the different constituent elementss that have same names with differentiation, do not mean successively or the primary and secondary relation.
Please refer to Fig. 5, the cut-away view that Fig. 5 is crane variable-amplitude control valve provided by the present invention.
In a kind of specific embodiment, crane variable-amplitude control valve 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, the first oil outlet 22, the second oil outlet 23 and return opening 24.
Have the undercut groove corresponding to each hydraulic fluid port in 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 described the second oil outlet undercut groove; Spool 30 is provided with a plurality of shoulders, during by the shoulder sway with the conducting or the disconnection that realize each oil circuit coordinating of each undercut groove, thereby reach the commutation purpose.
During work, oil inlet 21 is communicated with pressure oil-source, and the first oil outlet 22 is communicated with the rodless cavity of amplitude oil cylinder, and the 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 the first control position, oil inlet 21 is communicated with the first oil outlet 22, and the second oil outlet 23 is communicated with return opening 24; At the second control position, oil inlet 21 is communicated with the second oil outlet 23, and the first oil outlet 22 is communicated with return opening 24; At the 3rd control position, oil inlet 21 and the first oil outlet 22 all end, and described the second oil outlet 23 is communicated with return opening 24; Difference just is the structure of spool.
Please refer to Fig. 6, Fig. 7, the local enlarged diagram that Fig. 6 is I position in Fig. 5; Fig. 7 is the position view of spool described in Fig. 6 when moving to " dead band " and finishing.
As shown in the figure, there is the shoulder 31 that seals the second oil outlet undercut groove when meta on spool 30, the left end of this shoulder 31 is a plurality of for being communicated with the first groove 31-1 of oil inlet 21 and the second oil outlet 23 along being circumferentially with, when spool 30 moves to right, by the first groove 31-1, can make the open area of oil inlet 21 and the second oil outlet 23 increase gradually from zero; The right-hand member of shoulder 31 is a plurality of for being communicated with the second groove 31-2 of the second oil outlet 23 and return opening 24 along being circumferentially with, and when spool 30 moves to left, by the second groove 31-2, can make the second oil outlet 23 and the open area of return opening 24 increase gradually from zero.
The improvements of spool 30 are, the length of at least one the second groove 31-2 extends to the direction of the first groove 31-1, the axial spacing L of itself and the first groove 31-1
2be less than the undercut groove width L of the second oil outlet
1, to guarantee the crack mouthful of stage in control cock, oil inlet 21 is communicated with the second hydraulic fluid port 23 and open area increases gradually, and simultaneously, the second hydraulic fluid port 23 is communicated with return opening 24 and open area reduces gradually.
As shown in figure 11, in the moving process of the spool of control cock from the meta to the standard-sized sheet, total flow is Q to the hydraulic principle of its simplification, when restriction A increases, restriction B reduces, the flow that enters oil cylinder increases, and the fluid of restriction B oil sump tank reduces, and restriction B plays the effect of bypass throttle.
Please in the lump with reference to figure 8 to Figure 10, Fig. 8 is that spool shown in Fig. 6 moves to oil inlet and is communicated with through the first groove with the second hydraulic fluid port, and the second hydraulic fluid port and the position view of return opening when the second groove is communicated with; Fig. 9 is that spool shown in Fig. 6 moves to oil inlet and is communicated with through the first groove with the second hydraulic fluid port, and the second hydraulic fluid port and the return opening position view while disconnecting; Figure 10 is position view when shown in Fig. 6, spool moves to full-gear.
The specific works principle of above-mentioned control cock is as follows:
When luffing rises, its oil inlet 21 is communicated with the first oil outlet 22, the second oil outlet 23 is communicated with return opening 24, and spool reaches flow divider valve before open and works, and system is always the ratio characteristic.
When luffing falls, its oil inlet 21 is communicated with the second oil outlet 23, the first oil outlet 22 is communicated with return opening 24, the distance L that spool 30 initial movable are minimum
3the time, do not have fluid to pass through spool 30, concerning spool 30 these sections, be " dead band ", crossed " dead band " afterwards, due to the first groove 31-1 of spool 30, less fluid is arranged by spool 30.
In the 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, now pump the pressure oil come and all enter the oil inlet 21 of control cock, by being divided into two-way after spool: the rod chamber that enters oil cylinder is flowed out from the second oil outlet 23 of control cock in a road retracts oil cylinder; Unnecessary fluid flows back to T mouth (as shown by arrows) from another road by return opening 24; Now system has the characteristic of bypass throttle speed governing, and flow divider valve is inoperative, and system pressure is more steady, thereby has eliminated the shake in crack mouthful of stage, has promoted fine motion.
When spool has been crossed crack port area, return opening 24 is closed, and the fluid flowed into from oil inlet 21 all enters amplitude oil cylinder, and now spool pressure reduction is opened certain aperture by flow divider valve, make unnecessary fluid flow back to fuel tank from flow divider valve, at this moment system returns to again original ratio characteristic.
This in the luffing mode that time-division in two stages are controlled that falls, the stationarity that luffing is fallen and fine motion 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 being improved for the second groove on 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 that control cock is crack mouthful of stage shake, the difference DELTA L of undercut groove width and spacing should equal crack mouthful of stroke of spool 30 conducting oil inlets 21 and the second oil outlet 23.So, when the crack mouthful of stage of control cock finishes, spool 30 can disconnect the second oil outlet 23 and return opening 24 immediately, thereby changes whole hydraulic efficiency pressure system into the ratio characteristic by the bypass throttle characteristic in time.
The oil inlet 21 that above-mentioned crack mouthful stroke refers to control cock is during with the second oil outlet 23 conducting, starts oil-feeds from spool 30 and causes the stroke of shaking spool 30 while relaxing gradually to this shake.Generally speaking, the trip is less than 1/3rd of spool 30 conducting oil inlets 21 and the second oil outlet 23 total kilometragies, and this paper does not do restriction to its concrete numerical value and relative scale, and those skilled in the art can be designed according to actual needs.
That make improvements can be part the second groove 31-2, if adopt this kind of mode, the second groove that extends and do not extend can be circumferentially spaced apart along shoulder 31.That certainly, make improvements can be also whole the second groove 31-2.
Please refer to Figure 12, the local structure schematic diagram that Figure 12 is spool shown in Fig. 6.
After improvement, as shown in figure 12, it is large that its width and the degree of depth become from the inner the general shape of the second groove 31-2 outward gradually.Certainly, the concrete shape of the second groove 31-2 is not limited to this, every can the second oil outlet 23 connection with return opening 24 in crack mouthful stage, and open area diminishes until second groove of closing all can be realized the object of the invention gradually with the movement of spool 30.
Control cock and pressure-compensated valve 4 can be carried out to the system integration, pressure-compensated valve 4 is located on the oil-feed oil circuit of valve body 31, and at the first control position of control cock, its control port is communicated with the first oil outlet 22; At the second control position of control cock, its control port is communicated with the 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 the second oil outlet 23 of control cock, oil outlet is communicated with the return opening 24 of control cock.
Certainly, above-mentioned crane variable-amplitude control valve is only a kind of preferred version, specifically is not limited to this, can make according to actual needs pointed adjustment on this basis, thereby obtains different embodiments.
Except above-mentioned crane variable-amplitude control valve, the present invention also provides a kind of crane variable-amplitude hydraulic system, comprises amplitude oil cylinder, control cock 5 and flow divider valve 3, and wherein control cock 5 is the described crane variable-amplitude control valve of above-mentioned any one (can referring to Fig. 2).
The first oil outlet 22 of control cock 5 is communicated with the rodless cavity 7 of amplitude oil cylinder, and the second oil outlet 23 is communicated with the rod chamber 8 of amplitude oil cylinder.
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 there are three mode of operations: at the first mode of operation, its control port is communicated with the first oil outlet 22 of control cock, corresponding to the first control position of control cock 5; At the second mode of operation, its control port is communicated with the second oil outlet 23 of control cock 5, corresponding to the 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 return opening, all the other structures please refer to prior art, just repeat no more.
Above crane variable-amplitude control valve provided by the present invention and crane variable-amplitude hydraulic system are described in detail.Applied specific case herein principle of the present invention and embodiment are set forth, the explanation of above embodiment is just for helping to understand core concept of the present invention.It should be pointed out that for those skilled in the art, under the premise without departing from the principles 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 the claims in the present invention.
Claims (10)
1. a crane variable-amplitude control valve, comprise valve body and spool, and described valve body is provided with oil inlet, the first oil outlet, the second oil outlet and return opening; Shoulder one end of described the second oil outlet of described seal spool is provided with for being communicated with the first groove of described oil inlet and the second oil outlet, the other end is provided with for being communicated with the second groove of described the second oil outlet and return opening, it is characterized in that, the axial spacing of at least one described the second groove and described the first groove is less than the undercut groove width of described the second oil outlet.
2. crane variable-amplitude control valve according to claim 1, is characterized in that, the axial spacing of described the second groove and described the first groove is less than the undercut groove width of described the second oil outlet.
3. crane variable-amplitude control valve according to claim 1 and 2, is characterized in that, the difference of described undercut groove width and described axial spacing equals crack mouthful of stroke of the described oil inlet of described spool conducting and the second oil outlet.
4. crane variable-amplitude control valve according to claim 1 and 2, is characterized in that, it is large that the width of described the second groove and the degree of depth become outward gradually from the inner.
5. crane variable-amplitude control valve according to claim 3, is characterized in that, has three control positioies: at the first control position, described oil inlet is communicated with the first oil outlet, and described the second oil outlet is communicated with return opening; At the second control position, described oil inlet is communicated with the second oil outlet, and described the first oil outlet is communicated with return opening; At the 3rd control position, described oil inlet and the first oil outlet all end, and described the second oil outlet is communicated with return opening.
6. crane variable-amplitude control valve according to claim 5, is characterized in that, is specially three position four-way directional control valve.
7. according to the described crane variable-amplitude control valve of claim 5 or 6, it is characterized in that, this control cock is integrated with pressure-compensated valve, described pressure-compensated valve is located on the oil-feed oil circuit of described valve body, at the first control position of described control cock, the control port of described pressure-compensated valve is communicated with described the first oil outlet; At the second control position of described control cock, the control port of described pressure-compensated valve is communicated with described the second oil outlet; At the 3rd control position of described control cock, the control port of described pressure-compensated valve is communicated with described return opening.
8. according to the described crane variable-amplitude control valve of claim 5 or 6, it is characterized in that, this control cock is integrated with the secondary by pass valve, and the oil inlet of described secondary by pass valve is communicated with described the second oil outlet, oil outlet is communicated with described return opening.
9. a crane variable-amplitude hydraulic system, comprise amplitude oil cylinder, control cock and flow divider valve, it is characterized in that, described control cock is the described crane variable-amplitude control valve of the claims 1 to 8 any one, the first oil outlet of this control cock is communicated with the rodless cavity of described amplitude oil cylinder, and the second oil outlet is communicated with the rod chamber of described amplitude oil cylinder; The oil inlet of described flow divider valve is communicated with the oil inlet of described valve body, oil outlet is communicated with the return opening of described valve body, and has three mode of operations: at the first mode of operation, its control port is communicated with the first oil outlet of described control cock; At the second mode of operation, its control port is communicated with the second oil outlet of described control cock; At the 3rd mode of operation, its control port is communicated with the return opening of described control cock.
10. crane variable-amplitude hydraulic system according to claim 9, is characterized in that, is provided with main by pass valve between the oil inlet of described control cock and 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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| 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 |
| 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 |
| 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 |
| 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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| DE3802672C2 (en) * | 1988-01-29 | 1993-12-16 | Danfoss As | Hydraulic control valve with pressure sensing device |
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| DE19957952A1 (en) * | 1999-12-02 | 2001-06-07 | Mannesmann Rexroth Ag | Hydraulic directional control valve for load-independent control of a hydraulic consumer, especially of a mobile machine |
| CN101749447B (en) * | 2008-12-03 | 2010-12-29 | 徐州重型机械有限公司 | Flow control valve |
| CN102116327A (en) * | 2009-12-30 | 2011-07-06 | 徐州重型机械有限公司 | Hydraulic valve and double variable-amplitude oil cylinder control system applying same |
| CN202296922U (en) * | 2011-10-26 | 2012-07-04 | 徐州重型机械有限公司 | Crane variable-amplitude control valve and crane variable-amplitude hydraulic system |
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2011
- 2011-10-26 CN CN 201110330251 patent/CN102398866B/en active Active
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| CN102398866A (en) | 2012-04-04 |
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