CN203430894U - Double hydraulic cylinder synchronous control system and engineering machinery applying same - Google Patents
Double hydraulic cylinder synchronous control system and engineering machinery applying same Download PDFInfo
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- CN203430894U CN203430894U CN201320440262.0U CN201320440262U CN203430894U CN 203430894 U CN203430894 U CN 203430894U CN 201320440262 U CN201320440262 U CN 201320440262U CN 203430894 U CN203430894 U CN 203430894U
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Abstract
The utility model discloses a double hydraulic cylinder synchronous control system. The double hydraulic cylinder synchronous control system comprises a direction control valve and two backpressure valves, wherein the direction control valve is used for controlling two hydraulic cylinders to do telescopic motion; the two backpressure valves are respectively and fixedly arranged on the two hydraulic cylinders, and the guide opening pressure of one backpressure valve is larger than that of the other backpressure valve; the double hydraulic cylinder synchronous control system is configured that oil inlet branches and oil return branches of the two hydraulic cylinders are all in parallel connection during a stretching out process, the oil inlet branches of the two hydraulic cylinders are in series connection and the oil outlet branches of the two hydraulic cylinders are in parallel connection during a retraction process, and the serial connection is formed from the backpressure valve in small guide opening pressure to the backpressure valve in large guide opening pressure. The double hydraulic cylinder synchronous control system disclosed by the utility model is capable of effectively controlling the system manufacturing cost on the basis that the synchronous control accuracy is ensured; on the basis, the utility model also provides engineering machinery applying the double hydraulic cylinder synchronous control system.
Description
Technical field
The utility model relates to technical field of engineering machinery, is specifically related to a kind of double hydraulic cylinder synchronous control system and applies the engineering machinery of this control system.
Background technique
Hydraulic synchronous system is technical task eternal in hydraulics application practice, guarantees on the one hand the operation precision of executable operations, the safety reliability that lifting gear is carried out on the other hand.At present, there is the executive system of multiple employing Double-hydraulic-cylinder in the variation based on new architecture lifting performance, for example, and the jib lubbing mechanism ,Chao Qi mechanism of hoist and elevator latch ratchet mechanism etc.
Increase along with lifting tonnage, the load of each executive system all can be in various degree increase, mechanism structure size and movement range all increase accordingly simultaneously, therefore, in practical work process, very easily there is nonsynchronous phenomenon in two hydraulic jacks of each executive system.As everyone knows, asynchrony phenomenon directly affects mechanism action stability, affects the execution of whole mechanism, and comparatively serious words will cause damage or the cut-out of two hydraulic jacks.For example, two derricking cylinder hydraulic systems are widely used on various working trucks, comprise engineering vehicle, fire-fighting vehicle etc.; Derricking cylinder is in the process of retraction, for example, for the device (jib) of its supporting can steadily be fallen, need to two identical equilibrium valves be installed at two derricking cylinder rodless cavities, equilibrium valve produces certain back pressure, prevents that derricking cylinder from falling voluntarily under the effect of load.
Refer to Fig. 1, this figure is the synchronizing control loop schematic diagram of a kind of typical pair of amplitude oil cylinder in prior art.
In actual using process, along with the variation of load center of gravity, the pressure that left and right derricking cylinder is subject to is not necessarily completely equal, and meanwhile, the return oil pressure of two derricking cylinders also not necessarily equates.Therefore, although left and right derricking cylinder has been selected identical equilibrium valve 1a, but due to machining error, assembly error etc., still there is the difference of opening feature, because equilibrium valve belongs to dynamic balancing control unit, fine motion difference is easy to be amplified by liquid inhibition effect, shows as left and right equilibrium valve valve core opening in different size, thereby cause left and right derricking cylinder back pressure different, cause twin-tub retraction asynchrony phenomenon.
Refer to Fig. 2, this figure is the synchronizing control loop schematic diagram of another kind of typical two amplitude oil cylinder in prior art.
In order to overcome the nonsynchronous problem of twin-tub, control system shown in Fig. 2 adopts an equilibrium valve 2a to control two derricking cylinders.But the equilibrium valve of this scheme cannot be directly installed on oil cylinder, needs to connect with pipeline between oil cylinder and equilibrium valve.Once in use pipeline is between the two because wearing and tearing or collision cause breaking, derricking cylinder just can be uncontrolled under heavy duty automatic retracted, the device of its support just can fall, and causes security incident.Therefore, this scheme is equipped with the explosion-proof control valve 2b of pipeline in the joint of oil cylinder and pipeline.
Thus, greatly increased the complexity of pipeline assembling, system manufacture cost is also higher; Explosion-proof control valve belongs to flow control valve in addition, further can cause due to various errors the difference of left and right return oil pressure.
In view of this, urgently look for another way a kind of hydraulic jack synchronizing control loop is provided, guaranteeing on the basis of Double-hydraulic-cylinder synchronism, effectively control system manufacture cost.
Model utility content
For above-mentioned defect, the technical problem that the utility model solves is to provide a kind of double hydraulic cylinder synchronous control system, by the effective control system manufacture cost of Optimized System Design.On this basis, the utility model also provides a kind of engineering machinery of this control system of application.
The double hydraulic cylinder synchronous control system that the utility model provides, comprises the position control valve of controlling two hydraulic cylinder extension actions, and two are fixedly installed on respectively two back pressure valves on described oil hydraulic cylinder; In two described back pressure valves, wherein guide's cracking pressure of one is greater than guide's cracking pressure of another one, and is configured to: stretch out in process, the oil-feed branch road of two described oil hydraulic cylinders and oil return branch road are all in parallel; In retraction process, the oil-feed branch circuit parallel connection of two described oil hydraulic cylinders, the series connection of oil return branch road, described series connection is formed by the described back pressure valve of the extremely large guide's cracking pressure of described back pressure valve of little guide's cracking pressure.
Preferably, described back pressure valve is specially equilibrium valve, and guide's cracking pressure of the first equilibrium valve is greater than guide's cracking pressure of the second equilibrium valve.
Preferably, the cracking pressure of described the first equilibrium valve is greater than the complete cracking pressure of described the second equilibrium valve.
Preferably, the rated flow of described the first equilibrium valve is the twice of the rated flow of described the second equilibrium valve.
Preferably, return opening under the opening state of described the first equilibrium valve is to the return opening one-way conduction under the opening state of described the second equilibrium valve, and the return opening under the opening state of described the second equilibrium valve is to the filler opening one-way conduction under the opening state of described the first equilibrium valve.
Preferably, described one-way conduction adopts one-way valve to form.
Preferably, described the first equilibrium valve becomes one with the one-way valve that forms described one-way conduction.
The engineering machinery that the utility model provides, comprises the executive system that adopts two oil cylinder synchronization telescope actions, also comprises foregoing double hydraulic cylinder synchronous control system.
Preferably, described executive system is specially luffing range of cantilever support system.
Compared with prior art, two oil hydraulic cylinders of the present utility model adopt two different back pressure valves of guide's cracking pressure, stretch out in process, and the oil-feed branch road of two oil hydraulic cylinders and oil return branch road are all in parallel, that is, the working oil path that two oil hydraulic cylinders stretch out process is independent of each other; In retraction process, the oil-feed branch circuit parallel connection of two oil hydraulic cylinders, the series connection of oil return branch road, this series connection is formed by the back pressure valve of the extremely large guide's cracking pressure of back pressure valve of little guide's cracking pressure, that is to say, one oil hydraulic cylinder oil return of retraction process is the back pressure valve to large guide's cracking pressure via the back pressure valve of little guide's cracking pressure, and flows back to fuel tank with the back pressure valve that another oil hydraulic cylinder oil return converges via large guide's cracking pressure.Obviously, during oil return, the back pressure valve of little guide's cracking pressure is first opened, coupled oil hydraulic cylinder oil return can flow to the back pressure valve of large guide's cracking pressure smoothly by this back pressure valve, the return oil pressure of double hydraulic cylinder is determined and is controlled by large back pressure valve, can eliminate the different problem of return oil pressure that the difference because of two back pressure valves causes completely, guarantee twin-tub synchronization motion.
In addition, this scheme connects oil cylinder and back pressure valve without pipeline is additionally set, and can evade the pipeline issuable hidden danger of wearing and tearing completely, does not need additionally to arrange pipeline and is equipped with explosion-proof valve simultaneously, and pipeline assembling is simple, reliable, has reduced system manufacture cost.
Back pressure valve in the utility model preferred version adopts equilibrium valve, and the cracking pressure of the first equilibrium valve is greater than the complete cracking pressure of the second equilibrium valve, in working procedure, when pilot pressure reaches the complete cracking pressure of the second equilibrium valve, when the second equilibrium valve is opened completely, the first equilibrium valve is just opened, so arrange, make the directly actuated oil hydraulic cylinder oil return of the second equilibrium valve via the second equilibrium valve, the first equilibrium valve, realize and refueling successively more smoothly, can further improve the precision of twin-tub synchronization control.
In another preferred version of the present utility model, the rated flow of the first equilibrium valve is set as the twice of the rated flow of the second equilibrium valve, like this, even if two equilibrium valves are all operated in maximum rated flow, also can guarantee the precision of twin-tub synchronization control.
The double hydraulic cylinder synchronous control system that the utility model provides, applicable to the executive system of any employing double hydraulic cylinder control, is specially adapted to the luffing range of cantilever support system of hoist.
Accompanying drawing explanation
Fig. 1 is the fundamental diagram of a kind of typical pair of amplitude oil cylinder synchronous control system in prior art;
Fig. 2 is the fundamental diagram of another kind of typical two amplitude oil cylinder synchronous control systems in prior art;
Fig. 3 is the fundamental diagram of two amplitude oil cylinder synchronous control systems described in embodiment.
In Fig. 3:
Left hydraulic cylinder 1, right oil hydraulic cylinder 2, position control valve 3, the first back pressure valve 4, the second back pressure valve 5, the first one-way valve 6, the second one-way valve 7.
Embodiment
Core of the present utility model is to provide a kind of double hydraulic cylinder synchronous control system, by the optimization of arrangements of components, can guarantee Double-hydraulic-cylinder synchronism, and effective control system manufacture cost.Below in conjunction with Figure of description, illustrate present embodiment.
Without loss of generality, present embodiment be take the luffing range of cantilever support oil cylinder of hoist and is elaborated as main body, should be appreciated that luffing range of cantilever support oil cylinder is not construed as limiting for present techniques scheme, this double hydraulic cylinder synchronous control system goes for the executive system of two oil hydraulic cylinders of any employing.
Referring to Fig. 3, should be the fundamental diagram of two amplitude oil cylinder synchronous control systems described in present embodiment.
Same as the prior art, two oil hydraulic cylinders of this synchronous control system, by the switching controls of position control valve 3, are realized and being stretched out or the action that bounces back.As shown in the figure, when position control valve 3 is positioned at right position, system pressure fluid enters the rodless cavity of two oil hydraulic cylinders via its A mouth, and the fluid of rod chamber flows back to fuel tank via the B mouth of position control valve 3 simultaneously.
Wherein, two are fixedly installed on respectively in two back pressure valves on oil hydraulic cylinder, wherein guide's cracking pressure of the first back pressure valve (3) is greater than guide's cracking pressure of the second back pressure valve (4), and be configured to: stretch out in process, the oil-feed branch road of two oil hydraulic cylinders and oil return branch road are all in parallel, as shown in the figure, the first back pressure valve (3) is fixedly connected with left hydraulic cylinder 1, the second back pressure valve (4) is fixedly connected with right oil hydraulic cylinder 2, the working oil path that two oil hydraulic cylinders stretch out process is independent of each other, obviously, two of different cracking pressures back pressure valves can exchange completely; In retraction process, the oil-feed branch circuit parallel connection of two oil hydraulic cylinders, the series connection of oil return branch road, particularly, this series connection is for by second back pressure valve (4) of little guide's cracking pressure, the first back pressure valve (3) to large guide's cracking pressure forms, that is to say, right oil hydraulic cylinder 2 oil returns of retraction process are the first back pressure valve 4 to large guide's cracking pressure via the second back pressure valve 5 of little guide's cracking pressure, and flows back to fuel tank with the first back pressure valve (3) that left hydraulic cylinder 1 oil return converges via large guide's cracking pressure.So arrange, during oil return, second back pressure valve (4) of little guide's cracking pressure is first opened, coupled left hydraulic cylinder 1 oil return can flow to first back pressure valve (3) of large guide's cracking pressure smoothly by this second back pressure valve 5, the return oil pressure of double hydraulic cylinder is determined and is controlled by the first back pressure valve (3), guaranteeing twin-tub synchronization motion.
It should be noted that, in conjunction with state of the art, can realize in different ways and set up specific back pressure, for example, back pressure valve can adopt equilibrium valve, also can adopt Pilot operated check valve applied in any combination, and specific implementation repeats no more herein.Certainly, it is optimal case that the particular job parameter requiring according to overall system is selected the equilibrium valve that technology is relatively ripe, guide's cracking pressure of the first equilibrium valve 3 is greater than guide's cracking pressure of the second equilibrium valve 4, and cost is controlled on the one hand, and Performance Ratio is more reliable and more stable on the other hand.
Particularly, the return opening one-way conduction under the opening state of return opening to the second equilibrium valve 4 under the opening state of the first equilibrium valve 1, the filler opening one-way conduction under the opening state of return opening to the first equilibrium valve 3 under the opening state of the second equilibrium valve 1.Aforementioned two one-way conductions adopt respectively the first one-way valve 6 and the second one-way valve 7 to form, and further, in order to reduce connecting pipeline, the design that becomes one of the first equilibrium valve 3 and the first one-way valve 6 and the second one-way valve 7, is convenient to system maintenance and management.
Illustrate the working procedure of aforementioned pair of luffing hydraulic cylinder synchronous control system below.
When (P-A mouth connects, and B-T mouth is communicated with) connected in the right position of position control valve 3.The high pressure oil of A mouth flows into the first equilibrium valve 3 entry ends, now a part of hydraulic oil flows into the rodless cavity of left hydraulic cylinder 1 by the first equilibrium valve 3 spools, another part hydraulic oil flows into the second equilibrium valve 4 by the first one-way valve 6 through exterior line, through the second equilibrium valve 4, flows into right oil hydraulic cylinder 2 rodless cavities.Left hydraulic cylinder 1 and the 2 rodless cavity oil-feeds of right oil hydraulic cylinder, complete extend action.Now, the first equilibrium valve 1 and the second equilibrium valve 4 parallel connections.
When the left position of position control valve 3, connect (P-B mouth is communicated with, and A-T mouth is communicated with), the high pressure oil of B mouth flows into the rod chamber of double hydraulic cylinder simultaneously, can pass through respectively oil circuit control (dotted line oil circuit in figure) two equilibrium valves are opened simultaneously.Guide's cracking pressure of the second equilibrium valve 4 is lower, therefore the second equilibrium valve 4 is first opened, the oil return of right oil hydraulic cylinder 2 flows to the first equilibrium valve 3 by the second equilibrium valve 4 via the second one-way valve 7, and via the first equilibrium valve 3, flows back to fuel tank in the lump after converging with the oil return of left hydraulic cylinder 1.Obviously, the return oil pressure of two derricking cylinders is controlled by the first equilibrium valve 3 in fact, has eliminated the different problem that causes left and right derricking cylinder return oil pressure because of the difference of equilibrium valve.Now, the first equilibrium valve 1 and the second equilibrium valve 4 series connection.
Certainly, in order to make the rodless cavity oil return of right oil hydraulic cylinder 2, can carry out more smoothly, can do further to optimize to the setting parameter of two equilibrium valves, the cracking pressure of the first equilibrium valve 3 is greater than the complete cracking pressure of the second equilibrium valve 4, here, " cracking pressure " refers to the minimum pressure values of opening main valve plug, and now oil return aperture is minimum, " cracking pressure completely " refers to the maximum pressure value of opening main valve plug, and now oil return is maximum opening.So arrange, make directly actuated right oil hydraulic cylinder 2 oil returns of the second equilibrium valve 4 via the second equilibrium valve 4, realize oil return more smoothly, guarantee the precision of twin-tub synchronization control.
In addition, under special operation condition, two equilibrium valves need to be operated in maximum rated flow, in order to make not affect synchronization accuracy under this operating mode, the rated flow of the first equilibrium valve 3 can be chosen to be the twice of the rated flow of the second equilibrium valve 4, like this, even if two equilibrium valves are all operated in maximum rated flow, also can guarantee the precision of twin-tub synchronization control.
Except aforementioned double hydraulic cylinder synchronous control system, the utility model also provides a kind of engineering machinery that adopts two oil cylinder synchronization telescope action executing systems that has.Same as the prior art, this project machinery comprises the jib hinged with chassis, and is arranged on the amplitude oil cylinder between jib and chassis.It should be noted that, other functional parts such as the chassis of this project machinery, electrical system, power system all can adopt existing techniques in realizing, thus repeat no more herein, and do not carry out corresponding diagram.
Wherein, adopting two oil cylinder synchronization telescope action executing systems can be luffing range of cantilever support system.
The above is only preferred implementation of the present utility model; it should be pointed out that for those skilled in the art, do not departing under the prerequisite of the utility model principle; can also make some improvements and modifications, these improvements and modifications also should be considered as protection domain of the present utility model.
Claims (9)
1. a double hydraulic cylinder synchronous control system, comprises the position control valve of controlling two hydraulic cylinder extension actions, and two are fixedly installed on respectively two back pressure valves on described oil hydraulic cylinder; It is characterized in that, in two described back pressure valves, wherein guide's cracking pressure of one is greater than guide's cracking pressure of another one, and is configured to: stretch out in process, the oil-feed branch road of two described oil hydraulic cylinders and oil return branch road are all in parallel; In retraction process, the series connection of the oil-feed branch circuit parallel connection of two described oil hydraulic cylinders, oil return branch road, described series connection forms for the described back pressure valve of the described back pressure valve by little guide's cracking pressure to large guide's cracking pressure.
2. double hydraulic cylinder synchronous control system according to claim 1, is characterized in that, described back pressure valve is specially equilibrium valve, and guide's cracking pressure of the first equilibrium valve is greater than guide's cracking pressure of the second equilibrium valve.
3. double hydraulic cylinder synchronous control system according to claim 2, is characterized in that, the cracking pressure of described the first equilibrium valve is greater than the complete cracking pressure of described the second equilibrium valve.
4. according to the double hydraulic cylinder synchronous control system described in claim 2 or 3, it is characterized in that, the rated flow of described the first equilibrium valve is the twice of the rated flow of described the second equilibrium valve.
5. double hydraulic cylinder synchronous control system according to claim 2, it is characterized in that, return opening under the opening state of described the first equilibrium valve is to the return opening one-way conduction under the opening state of described the second equilibrium valve, and the return opening under the opening state of described the second equilibrium valve is to the filler opening one-way conduction under the opening state of described the first equilibrium valve.
6. double hydraulic cylinder synchronous control system according to claim 5, is characterized in that, described one-way conduction adopts one-way valve to form.
7. double hydraulic cylinder synchronous control system according to claim 6, is characterized in that, described the first equilibrium valve becomes one with the one-way valve that forms described one-way conduction.
8. an engineering machinery, comprises the executive system that adopts two oil cylinder synchronization telescope actions; It is characterized in that, also comprise the double hydraulic cylinder synchronous control system as described in any one in claim 1 to 7.
9. engineering machinery according to claim 8, is characterized in that, described executive system is specially luffing range of cantilever support system.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201320440262.0U CN203430894U (en) | 2013-07-23 | 2013-07-23 | Double hydraulic cylinder synchronous control system and engineering machinery applying same |
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| CN201320440262.0U CN203430894U (en) | 2013-07-23 | 2013-07-23 | Double hydraulic cylinder synchronous control system and engineering machinery applying same |
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| CN203430894U true CN203430894U (en) | 2014-02-12 |
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| CN201320440262.0U Withdrawn - After Issue CN203430894U (en) | 2013-07-23 | 2013-07-23 | Double hydraulic cylinder synchronous control system and engineering machinery applying same |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103334979A (en) * | 2013-07-23 | 2013-10-02 | 徐州重型机械有限公司 | Double hydraulic cylinder synchronous control system and engineering machine applying control system |
| CN109114056A (en) * | 2018-10-19 | 2019-01-01 | 吉特利环保科技（厦门）有限公司 | One kind one pumps multi-cylinder energy-saving hydraulic device |
-
2013
- 2013-07-23 CN CN201320440262.0U patent/CN203430894U/en not_active Withdrawn - After Issue
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103334979A (en) * | 2013-07-23 | 2013-10-02 | 徐州重型机械有限公司 | Double hydraulic cylinder synchronous control system and engineering machine applying control system |
| CN103334979B (en) * | 2013-07-23 | 2015-08-19 | 徐州重型机械有限公司 | Double hydraulic cylinder synchronous control system and apply the engineering machinery of this control system |
| CN109114056A (en) * | 2018-10-19 | 2019-01-01 | 吉特利环保科技（厦门）有限公司 | One kind one pumps multi-cylinder energy-saving hydraulic device |
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| C14 | Grant of patent or utility model | ||
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| AV01 | Patent right actively abandoned |
Granted publication date: 20140212 Effective date of abandoning: 20150819 |
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| AV01 | Patent right actively abandoned |
Granted publication date: 20140212 Effective date of abandoning: 20150819 |
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| RGAV | Abandon patent right to avoid regrant |