CN202209447U - Converging valve and crane hydraulic control system with converging valve - Google Patents
Converging valve and crane hydraulic control system with converging valve Download PDFInfo
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- CN202209447U CN202209447U CN2011203190796U CN201120319079U CN202209447U CN 202209447 U CN202209447 U CN 202209447U CN 2011203190796 U CN2011203190796 U CN 2011203190796U CN 201120319079 U CN201120319079 U CN 201120319079U CN 202209447 U CN202209447 U CN 202209447U
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Abstract
The utility model discloses a converging valve, which comprises a first shuttle valve, a solenoid valve with a first oil port and a second oil port, a first hydraulic control change valve with a first oil port and a second oil port and a hydraulic control valve with a first oil port and a second oil port. The first oil port of the solenoid valve is connected with an oil outlet of the first shuttle valve, a control oil port of the first hydraulic control change valve is connected with the second oil port of the solenoid valve, a control oil port of the hydraulic control valve is connected with the second oil port of the solenoid valve, and the hydraulic control valve has two working conditions. Under a first working condition, the first oil port and the second oil port of the hydraulic control valve are disconnected, and under the second working condition, the first oil port and the second oil port of the hydraulic control valve are communicated. The converging valve can guarantee telescopic oil cylinders and amplitude oil cylinders of the crane to not only have higher stretching efficiency but also have lower retraction energy consumption. A crane hydraulic control system with the converging valve is further disclosed.
Description
Technical field
The utility model relates to technical field of engineering machinery, particularly is applied to the interflow valve of hoist hydraulic control system.The utility model also relates to the hoist hydraulic control system that is provided with said interflow valve.
Background technique
At present; In truck crane; Main action is master winch, secondary elevator, flexible, luffing and revolution; Wherein preceding four actions generally are integrated on the main valve and (are called multi-way valve), and multi-way valve is the core component of hoist hydraulic control system, and it has determined master winch, secondary elevator, flexible and the efficient of luffing four big-movements and the energy consumption level of complete machine.
The control mode of existing hoist master winch and secondary elevator is more unified; Be the double pump interflow; When promptly carrying out an action, give the elevator fuel feeding simultaneously by first oil pump and second oil pump, to improve the working efficiency of executive component; Flexible and luffing then mainly concentrates on two kinds of control modes, and is specific as follows:
Please refer to Fig. 1, Fig. 1 be in the existing technology telescopic oil cylinder and amplitude oil cylinder by first oil pump and second oil pump hydraulic schematic diagram of fuel feeding simultaneously.
As shown in the figure, in first kind of control mode, telescopic oil cylinder 3 is the same as first oil pump 5 and second oil pump, 6 while fuel feeding with master winch 1, secondary elevator 2 with amplitude oil cylinder 4, and promptly flexible big loculus with luffing all adopts the mode at double pump interflow.Because telescopic oil cylinder 3 is the oil return of big chamber oil-feed loculus when stretching out with amplitude oil cylinder 4, therefore this mode can satisfy it with the big requirement of oil mass, can guarantee the speed of stretching out, and has higher efficient.But when telescopic oil cylinder 3 during with amplitude oil cylinder 4 retractions because loculus is less relatively with oil mass, if still with the mode fuel feeding at interflow, have a large amount of fluid in the high pressure conditions underflow stream to hydraulic oil container, cause energy consumption to increase.
Please refer to Fig. 2, Fig. 2 be in the existing technology telescopic oil cylinder and amplitude oil cylinder by the hydraulic schematic diagram of the independent fuel feeding of second oil pump.
As shown in the figure, in second kind of control mode, telescopic oil cylinder 3 is its fuel feeding with 4 of amplitude oil cylinder by second oil pump 6, and promptly the large and small chamber of telescopic oil cylinder 3 and amplitude oil cylinder 4 all adopts single pump mode to control.Energy consumption when this mode can effectively guarantee telescopic oil cylinder 3 with amplitude oil cylinder 4 retractions is reduced by at least the loss that first oil pump produces during than first oil pump 5 and second oil pump, 6 while fuel feeding.But because the oil inlet quantity during the 4 big chamber oil-feeds of telescopic oil cylinder 3 and amplitude oil cylinder is less, speed is restricted when causing stretching out.
To this; Speed when the flow that existing little tonnage hoist hydraulic control system is flexible through limiting on the basis of first kind of control mode, luffing joins valve rod entering loculus is controlled retraction; Also promptly make asymmetric valve rod, can alleviate the problem of energy consumption to a certain extent.
Please refer to Fig. 3, Fig. 3 is for controlling the hydraulic schematic diagram of telescopic oil cylinder through the multi-way valve with asymmetric valve rod.
When the telescopic oil cylinder selector valve 3-1 in the multi-way valve is in when upper, the hydraulic oil that first oil pump 5 and second oil pump 6 pump again through getting into the big chamber of telescopic oil cylinder 3 behind the equilibrium valve 3-2, stretches out telescopic oil cylinder 3 through upper path; Simultaneously loculus fluid is flowed through equally and is flowed back to fuel tank behind the telescopic oil cylinder selector valve 3-1.This moment, valve rod did not limit flow, and the flow that first oil pump 5 and second oil pump 6 pump can all get into the big chamber of telescopic oil cylinder 3 through valve rod.
When the telescopic oil cylinder selector valve 3-1 in the multi-way valve is in when the next, the hydraulic oil that first oil pump 5 and second oil pump 6 pump directly gets into the loculus of telescopic oil cylinder 3 through the next path, opens equilibrium valve 3-2 simultaneously, makes telescopic oil cylinder 3 retractions; The fluid telescopic oil cylinder selector valve 3-1 that behind equilibrium valve 3-2, flows through equally in simultaneously big chamber flows back to fuel tank again.This moment, valve rod limited flow, and the flow that first oil pump 5 and second oil pump 6 pump has only part to get into the loculus of telescopic oil cylinder 3 through valve rod.
When stretching out control; Relation below the volume that flows to and flow out telescopic oil cylinder exists, A1/A2=Q1/Q2 (A1 is that the big cavity area area of oil cylinder, A2 are the little cavity area of oil cylinder), i.e. Q2=(Q1 * A2)/A1; Because the ratio of A1 and A2 area is about 5, so Q2 is 1/5 of Q1 approximately; When bouncing back control, different according to load, there are following two kinds of situation:
A kind of situation is that the pressure of telescopic oil cylinder 3 big chambeies generations is less, and pressure does not reach the setting value of relief valve after being passed to loculus, and this moment, flow loss was the flow and the difference of the flow that gets into loculus and the product of pressure that first oil pump 5 and second oil pump 6 produce.
Another kind of situation is that the pressure of telescopic oil cylinder 3 big chambeies generations is bigger; Pressure reaches the setting value of relief valve after being passed to loculus, and this moment, flow loss was the flow and the difference of the flow that gets into loculus and the product of relief valve setting value that first oil pump 5 and second oil pump 6 produce.
It is thus clear that; The control mode of this asymmetric valve rod only is under the situation of retraction pressure less than the retraction relief valve set pressure, can play a role; When retraction pressure reaches retraction secondary relief valve setting value; Its energy consumption is identical when collaborating with double pump, still can not effectively reduce energy loss.
Therefore, how guaranteeing that telescopic oil cylinder and the amplitude oil cylinder of hoist not only had higher stretching out efficient but also have lower retraction energy consumption, is the present technical issues that need to address of those skilled in the art.
The model utility content
First purpose of the utility model provides a kind of interflow valve.This interflow valve can guarantee that telescopic oil cylinder and the amplitude oil cylinder of hoist had not only had higher stretching out efficient but also have lower retraction energy consumption.
Second purpose of the utility model provides a kind of hoist hydraulic control system that is provided with said interflow valve.
In order to realize above-mentioned first purpose, the utility model provides a kind of interflow valve, comprising:
First shuttle valve;
Solenoid valve has first hydraulic fluid port and second hydraulic fluid port, and its first hydraulic fluid port connects the oil outlet of said first shuttle valve; And have two working staties: in first working state; Its first hydraulic fluid port and second hydraulic fluid port break off, and in second working state, its first hydraulic fluid port is communicated with second hydraulic fluid port;
First pilot operated directional control valve has first hydraulic fluid port and second hydraulic fluid port, and its control port connects second hydraulic fluid port of said solenoid valve; And have two working staties: in first working state; Its first hydraulic fluid port and second hydraulic fluid port break off, and in second working state, its first hydraulic fluid port is communicated with second hydraulic fluid port;
Hydraulic control valve has first hydraulic fluid port and second hydraulic fluid port, and its control port connects second hydraulic fluid port of said solenoid valve; And have two working staties: in first working state; Its first hydraulic fluid port and second hydraulic fluid port break off, and in second working state, its first hydraulic fluid port is communicated with second hydraulic fluid port.
Preferably, said hydraulic control valve is a combination brake switch and proporting, comprising:
Second shuttle valve;
Second pilot operated directional control valve; Have first hydraulic fluid port, second hydraulic fluid port and the 3rd hydraulic fluid port, its first hydraulic fluid port connects the oil outlet of said second shuttle valve, and the 3rd hydraulic fluid port is a return opening; And have two working staties: in first working state; Its first hydraulic fluid port is communicated with second hydraulic fluid port, and in second working state, its second hydraulic fluid port is communicated with the 3rd hydraulic fluid port;
Two-way plug-in valve, its control port is communicated with second hydraulic fluid port of said second pilot operated directional control valve;
Two filler openings of said second shuttle valve connect the oil circuit of said two-way plug-in valve first hydraulic fluid port and second hydraulic fluid port respectively.
Preferably, said hydraulic control valve is the hydraulic control guiding valve.
Preferably, said solenoid valve is a two-position two-way solenoid valve.
Preferably, said first pilot operated directional control valve is the two-position two-way hydraulic control selector valve.
Preferably, said second pilot operated directional control valve is the two-position three way pilot operated directional control valve.
In order to realize above-mentioned second purpose; The utility model also provides a kind of hoist hydraulic control system; Comprise first oil pump, second oil pump, telescopic oil cylinder, amplitude oil cylinder and multi-way valve; Said telescopic oil cylinder and amplitude oil cylinder be by second oil pump feed, further external above-mentioned each described interflow valve, and two filler openings of said first shuttle valve connect the big chamber oil-feed oil circuit of said telescopic oil cylinder and amplitude oil cylinder respectively; First hydraulic fluid port of said hydraulic control valve is connected said first oil pump and second oil pump respectively with second hydraulic fluid port; First hydraulic fluid port of said first pilot operated directional control valve and second hydraulic fluid port are connected the control port of first diverter valve and second diverter valve of said multi-way valve respectively.
Preferably, further comprise equilibrium valve, be separately positioned on the oil circuit that is communicated with said telescopic oil cylinder and amplitude oil cylinder rodless cavity that the oil circuit that its control port is communicated with said telescopic oil cylinder and amplitude oil cylinder rod chamber respectively is communicated with.
The utility model provides first shuttle valve of interflow valve to be responsible for the high pressure oil in telescopic oil cylinder, the big chamber of the amplitude oil cylinder oil circuit is selected; Under the control of solenoid valve, be used to drive hydraulic control valve then, the connection of working connection is controlled by hydraulic control valve between first oil pump and second oil pump; Solenoid valve gets when electric, and hydraulic oil drives hydraulic control valve, realizes the interflow of oil cylinder big chamber oil-feed; Solenoid valve must not when electricity, and high pressure oil is cut off, and hydraulic control valve can't be moved, and still keeps original single oil pump feed mode; First pilot operated directional control valve is responsible for getting when electric at solenoid valve, and the feedback oil circuit that the feedback oil circuit flexible, that luffing produces and elevator are produced carries out good linking, and the diverter valve that makes first oil pump and second oil pump simultaneously and collaborative work guarantees to realize the work of double pump interflow.
Should collaborate valve through external on former multi-way valve; When telescopic oil cylinder and the oil-feed of the big chamber of amplitude oil cylinder, can realize the interflow and not collaborate two kinds of working staties according to selecting, thereby give the user bigger selection space; When single oil pump feed; Higher system stability can be obtained, when double pump collaborates, the speed that telescopic oil cylinder, amplitude oil cylinder stretch out and the operating efficiency of complete machine can be improved; Then can only single oil pump feed when telescopic oil cylinder and the oil-feed of amplitude oil cylinder loculus, the energy consumption that this has just reduced complete machine has improved energy utilization rate; Be equivalent to integrate the advantage at single oil pump feed and double pump interflow, both guaranteed the efficient when oil cylinder stretches out, the energy consumption when having guaranteed the oil cylinder withdrawal again.
In a kind of embodiment; Said hydraulic control valve is a combination brake switch and proporting, and its two-way plug-in valve is responsible for the working connection of first oil pump with second oil pump is connected, and realizes the perforation of working connection; Only get under the electric situation at solenoid valve; Just can realize the perforation of working connection, two-way plug-in valve Small Flow Control oil capable of using is controlled big flow work fluid, the usage requirement of high pressure, big flow in the time of satisfying the double pump interflow; In addition, two-way plug-in valve not only through-current capacity is big, and response is fast when switching, and good airproof performance is simple in structure, be easy to realize standardization.
The hoist hydraulic control system that the utility model provided is provided with above-mentioned interflow valve, because above-mentioned interflow valve has above-mentioned technique effect, the hoist hydraulic control system with this interflow valve also should possess the corresponding techniques effect.
Description of drawings
Fig. 1 be in the existing technology telescopic oil cylinder and amplitude oil cylinder by first oil pump and second oil pump hydraulic schematic diagram of fuel feeding simultaneously;
Fig. 2 be in the existing technology telescopic oil cylinder and amplitude oil cylinder by the hydraulic schematic diagram of the independent fuel feeding of second oil pump;
Fig. 3 is for controlling the hydraulic schematic diagram of telescopic oil cylinder through the multi-way valve with asymmetric valve rod;
Fig. 4 is connected in the hydraulic schematic diagram of multi-way valve shown in Figure 2 for the utility model provides the interflow valve.
Among Fig. 1 to Fig. 3:
1. master winch 2. secondary elevator 3. telescopic oil cylinder 3-1. telescopic oil cylinder selector valve 3-2. equilibrium valves 4. amplitude oil cylinder 5. first oil pumps 6. second oil pumps
Among Fig. 4:
10-1. the first shuttle valve 10-2., second shuttle valve, 20. solenoid valve 30-1., the first pilot operated directional control valve 30-2., second pilot operated directional control valve, 40. two-way plug-in valves, 50. first oil pumps, 60. second oil pumps, 70. telescopic oil cylinder 70-1. equilibrium valves, 80. amplitude oil cylinder 80-1. equilibrium valves, 90. multi-way valve 90-1., the first diverter valve 90-2., second diverter valve, 100. interflow valves
Embodiment
The core of the utility model provides a kind of interflow valve.This interflow valve can guarantee that telescopic oil cylinder and the amplitude oil cylinder of hoist had not only had higher stretching out efficient but also have lower retraction energy consumption.
Another core of the utility model provides a kind of hoist hydraulic control system that is provided with said interflow valve.
In order to make those skilled in the art person understand the utility model scheme better, the utility model is done further to specify below in conjunction with accompanying drawing and 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. 4, Fig. 4 is connected in the hydraulic schematic diagram that is connected with the multi-way valve that has the hoist hydraulic control system now for the utility model provides the interflow valve.
In a kind of embodiment, the interflow valve that the utility model provides comprises the first shuttle valve 10-1, solenoid valve 20, first pilot operated directional control valve 30-1 and the hydraulic control valve.
First filler opening of the first shuttle valve 10-1 is used to connect the big chamber oil-feed of the telescopic oil cylinder oil circuit of multi-way valve 90; Second filler opening is used to connect the big chamber oil-feed of the amplitude oil cylinder oil circuit of multi-way valve 90, and its function is that to choose the pressure oil that gets into solenoid valve 20 be the higher hydraulic oil of pressure in telescopic oil cylinder big chamber oil-feed oil circuit and the big chamber oil-feed of the amplitude oil cylinder oil circuit.
The first pilot operated directional control valve 30-1 is the two-position two-way hydraulic control selector valve; Have first hydraulic fluid port and second hydraulic fluid port; Its control port connects second hydraulic fluid port of solenoid valve 20, and first hydraulic fluid port and second hydraulic fluid port are respectively applied for the first diverter valve 90-1 that is connected multi-way valve 90 and the control port of the second diverter valve 90-2; And have two working staties: in first working state, its first hydraulic fluid port and second hydraulic fluid port break off, and in second working state, its first hydraulic fluid port is communicated with second hydraulic fluid port.
Hydraulic control valve is a combination brake switch and proporting, is made up of the second shuttle valve 10-2, the second pilot operated directional control valve 30-2 and two-way plug-in valve 40.
The second pilot operated directional control valve 30-2 is the two-position three way pilot operated directional control valve, has first hydraulic fluid port, second hydraulic fluid port and the 3rd hydraulic fluid port, and its first hydraulic fluid port connects the oil outlet of the second shuttle valve 10-2; Second hydraulic fluid port connects the control port of two-way plug-in valve 40; The 3rd hydraulic fluid port is a return opening, and has two working staties: in first working state, its first hydraulic fluid port is communicated with second hydraulic fluid port; In second working state, its second hydraulic fluid port is communicated with the 3rd hydraulic fluid port.
First hydraulic fluid port of two-way plug-in valve 40 is respectively applied for first oil pump 50 and second oil pump 60 that is connected the hoist hydraulic control system with second hydraulic fluid port; Be first hydraulic fluid port of two-way plug-in valve 40 and first hydraulic fluid port and second hydraulic fluid port that second hydraulic fluid port is whole hydraulic control valve; Be responsible for the working connection of first oil pump 50 and second oil pump 60 is connected; Realize the perforation of working connection, and only get under the electric situation, just can realize the perforation of working connection at solenoid valve 20.
Two filler openings of the second shuttle valve 10-2 connect the oil circuit of two-way plug-in valve 40 first hydraulic fluid ports and second hydraulic fluid port respectively.
Certainly; Hydraulic control valve can also be for having the hydraulic control guiding valve of first hydraulic fluid port and second hydraulic fluid port; Its control port connects second hydraulic fluid port of solenoid valve, and has two working staties: in first working state, its first hydraulic fluid port and second hydraulic fluid port break off; In second working state, its first hydraulic fluid port is communicated with second hydraulic fluid port; Can realize being communicated with or breaking off the purpose of first oil pump and the second oil pump working connection equally.
For the hydraulic control guiding valve, two-way plug-in valve 40 Small Flow Control oil capable of using are controlled big flow work fluid, the usage requirement of high pressure, big flow in the time of satisfying the double pump interflow; In addition, two-way plug-in valve 40 not only through-current capacity is big, and response is fast when switching, and good airproof performance is simple in structure, be easy to realize standardization.
The working procedure of above-mentioned interflow valve is following:
Telescopic oil cylinder and amplitude oil cylinder are stretched out operating mode; Solenoid valve 20; Its right position work, filler opening is communicated with oil outlet, and the fluid of the big chamber oil-feed of telescopic oil cylinder or amplitude oil cylinder oil circuit is divided into two-way behind the first shuttle valve 10-1 and solenoid valve 20; One the tunnel gets into the control end of the first pilot operated directional control valve 30-1, and another road gets into the control end of the second pilot operated directional control valve 30-2.
Under the effect of control oil channel; The right position work of the first pilot operated directional control valve 30-1; The feedback oil circuit of feedback oil circuit flexible, that luffing produces and elevator generation is carried out good linking; Make the first diverter valve 90-1 and the second diverter valve 90-2 while and the collaborative work of multi-way valve 90, guarantee that double pump collaborates to carry out smoothly; Simultaneously; The right position work of the second pilot operated directional control valve 30-2 makes the control port release of two logical dismounting valves 40, and spool is opened; The working connection of first oil pump 50 and second oil pump 60 is communicated with, by first oil pump 50 and second oil pump 60 simultaneously to telescopic oil cylinder and amplitude oil cylinder fuel feeding.
If solenoid valve 20 must not when electricity, then high pressure oil is cut off, and the first pilot operated directional control valve 30-1 and the second pilot operated directional control valve 30-2 all can't move, and whole system still keeps original single oil pump feed mode.It is thus clear that; When telescopic oil cylinder and the oil-feed of the big chamber of amplitude oil cylinder, can realize the interflow and not collaborate two kinds of working staties according to selecting, thereby give the user bigger selection space; When single oil pump feed; Higher system stability can be obtained, when double pump collaborates, the speed that telescopic oil cylinder, amplitude oil cylinder stretch out and the operating efficiency of complete machine can be improved.
Telescopic oil cylinder and amplitude oil cylinder retraction operating mode; Because solenoid valve 20 only is connected with its big chamber oil-feed oil circuit through the first shuttle valve 10-1, no matter so solenoid valve 20 whether electric, the loculus load causes the first pilot operated directional control valve 30-1 and the second pilot operated directional control valve 30-2 to move never; The possibility at double pump interflow when having stopped the oil-feed of oil cylinder loculus; Avoid misoperation, reduced the energy consumption of complete machine, improved energy utilization rate.
The combining form of above-mentioned hydraulic control valve only is a kind of preferred version, and its concrete structure is not limited thereto, and can make pointed adjustment according to actual needs on this basis, thereby obtain different embodiment.Because mode in the cards is more, for practicing thrift length, this paper just illustrates no longer one by one.
The reason that has the area ratio owing to oil cylinder; The efficient that the energy-conservation and oil cylinder of oil cylinder retraction stretches out in the Constant Pump System is the problem of a pair of contradiction always; Function through above-mentioned interflow valve can be when being raised the efficiency and is not increased energy consumption; The advantage that this just is equivalent to integrate single oil pump feed and double pump interflow had both guaranteed the efficient when oil cylinder stretches out, the energy consumption when having guaranteed the oil cylinder withdrawal again.
Except above-mentioned interflow valve; The utility model also provides a kind of hoist hydraulic control system; Comprise first oil pump 50, second oil pump 60, telescopic oil cylinder 70, amplitude oil cylinder 80 and multi-way valve 90, wherein telescopic oil cylinder 70 and amplitude oil cylinder 80 are by second oil pump, 60 fuel feeding.
Further external above-mentioned interflow valve 100, two filler openings of its first shuttle valve 10-1 connect the big chamber oil-feed oil circuit of telescopic oil cylinder 70 and amplitude oil cylinder 80 respectively; First hydraulic fluid port of hydraulic control valve is connected first oil pump 50 and second oil pump 60 respectively with second hydraulic fluid port; First hydraulic fluid port of the first pilot operated directional control valve 30-1 is connected first diverter valve 90-1 of multi-way valve 90 and the control port of the second diverter valve 90-2 respectively with second hydraulic fluid port.
Be respectively arranged with equilibrium valve 70-1 and equilibrium valve 80-1 on big chamber (rodless cavity) the oil-feed oil circuit of telescopic oil cylinder 70 and amplitude oil cylinder 80; The oil circuit that the control port of two equilibrium valves is communicated with telescopic oil cylinder 70 and amplitude oil cylinder 80 big chambeies respectively is communicated with; Play the effect that control oil cylinder rate of descent and load keep; The load that wherein acts on telescopic oil cylinder 70 and the amplitude oil cylinder 80 relies on the one-way function of equilibrium valve to realize; Rate of descent relies on the level stream function of equilibrium valve to control, and all the other structures please refer to existing technology, and this paper repeats no more.
Here need to prove,, the casting valve body of original multi-way valve 90 need not changed, saved the trial-production that designs the longer cycle that brings because of valve body again through the interflow valve 100 that external the utility model provides; And shoulder the control working connection and feed back being connected of oil circuit by the big chamber load of telescopic oil cylinder 70 and amplitude oil cylinder 80; As long as telescopic oil cylinder 70 and not action of amplitude oil cylinder 80; First oil pump 50 and second oil pump 60 are just carried out function separately separately so, can not cause the conflict of hoisting system.
More than interflow valve and hoist hydraulic control system that the utility model provided have been carried out detailed introduction.Used concrete example among this paper the principle and the mode of execution of the utility model are set forth, above embodiment's explanation just is used to help to understand the core concept of the utility model.Should be understood that; For those skilled in the art; Under the prerequisite that does not break away from the utility model principle, can also carry out some improvement and modification to the utility model, these improvement and modification also fall in the protection domain of the utility model claim.
Claims (8)
1. an interflow valve is characterized in that, comprising:
First shuttle valve;
Solenoid valve has first hydraulic fluid port and second hydraulic fluid port, and its first hydraulic fluid port connects the oil outlet of said first shuttle valve; And have two working staties: in first working state; Its first hydraulic fluid port and second hydraulic fluid port break off, and in second working state, its first hydraulic fluid port is communicated with second hydraulic fluid port;
First pilot operated directional control valve has first hydraulic fluid port and second hydraulic fluid port, and its control port connects second hydraulic fluid port of said solenoid valve; And have two working staties: in first working state; Its first hydraulic fluid port and second hydraulic fluid port break off, and in second working state, its first hydraulic fluid port is communicated with second hydraulic fluid port;
Hydraulic control valve has first hydraulic fluid port and second hydraulic fluid port, and its control port connects second hydraulic fluid port of said solenoid valve; And have two working staties: in first working state; Its first hydraulic fluid port and second hydraulic fluid port break off, and in second working state, its first hydraulic fluid port is communicated with second hydraulic fluid port.
2. interflow according to claim 1 valve is characterized in that, said hydraulic control valve is a combination brake switch and proporting, comprising:
Second shuttle valve;
Second pilot operated directional control valve; Have first hydraulic fluid port, second hydraulic fluid port and the 3rd hydraulic fluid port, its first hydraulic fluid port connects the oil outlet of said second shuttle valve, and the 3rd hydraulic fluid port is a return opening; And have two working staties: in first working state; Its first hydraulic fluid port is communicated with second hydraulic fluid port, and in second working state, its second hydraulic fluid port is communicated with the 3rd hydraulic fluid port;
Two-way plug-in valve, its control port is communicated with second hydraulic fluid port of said second pilot operated directional control valve;
Two filler openings of said second shuttle valve connect the oil circuit of said two-way plug-in valve first hydraulic fluid port and second hydraulic fluid port respectively.
3. interflow according to claim 1 valve is characterized in that, said hydraulic control valve is the hydraulic control guiding valve.
4. according to each described interflow valve of claim 1 to 3, it is characterized in that said solenoid valve is a two-position two-way solenoid valve.
5. according to each described interflow valve of claim 1 to 3, it is characterized in that said first pilot operated directional control valve is the two-position two-way hydraulic control selector valve.
6. according to each described interflow valve of claim 1 to 3, it is characterized in that said second pilot operated directional control valve is the two-position three way pilot operated directional control valve.
7. hoist hydraulic control system; Comprise first oil pump, second oil pump, telescopic oil cylinder, amplitude oil cylinder and multi-way valve; Said telescopic oil cylinder and amplitude oil cylinder are by second oil pump feed; It is characterized in that further external aforesaid right requires 1 to 6 each described interflow valve, two filler openings of said first shuttle valve connect the big chamber oil-feed oil circuit of said telescopic oil cylinder and amplitude oil cylinder respectively; First hydraulic fluid port of said hydraulic control valve is connected said first oil pump and second oil pump respectively with second hydraulic fluid port; First hydraulic fluid port of said first pilot operated directional control valve and second hydraulic fluid port are connected the control port of first diverter valve and second diverter valve of said multi-way valve respectively.
8. hoist hydraulic control system according to claim 7; It is characterized in that; Further comprise equilibrium valve; Be separately positioned on the oil circuit that is communicated with said telescopic oil cylinder and amplitude oil cylinder rodless cavity, the oil circuit that its control port is communicated with said telescopic oil cylinder and amplitude oil cylinder rod chamber respectively is communicated with.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011203190796U CN202209447U (en) | 2011-08-29 | 2011-08-29 | Converging valve and crane hydraulic control system with converging valve |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011203190796U CN202209447U (en) | 2011-08-29 | 2011-08-29 | Converging valve and crane hydraulic control system with converging valve |
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| CN202209447U true CN202209447U (en) | 2012-05-02 |
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| CN2011203190796U Expired - Lifetime CN202209447U (en) | 2011-08-29 | 2011-08-29 | Converging valve and crane hydraulic control system with converging valve |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102345749A (en) * | 2011-08-29 | 2012-02-08 | 徐州重型机械有限公司 | Flow collecting valve and crane hydraulic control system with the same |
| CN104743457A (en) * | 2015-02-28 | 2015-07-01 | 徐州徐工随车起重机有限公司 | Double-cylinder amplitude-variable hydraulic control system for dual-side lateral crane |
| CN105443481A (en) * | 2014-12-09 | 2016-03-30 | 徐州重型机械有限公司 | Series-parallel crane multitandem valve and hydraulic system and crane |
| CN110848194A (en) * | 2019-11-21 | 2020-02-28 | 徐州天睿地机械有限公司 | Externally-connected converging valve for mobile hydraulic power station |
-
2011
- 2011-08-29 CN CN2011203190796U patent/CN202209447U/en not_active Expired - Lifetime
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102345749A (en) * | 2011-08-29 | 2012-02-08 | 徐州重型机械有限公司 | Flow collecting valve and crane hydraulic control system with the same |
| CN102345749B (en) * | 2011-08-29 | 2013-06-19 | 徐州重型机械有限公司 | Flow collecting valve and crane hydraulic control system with the same |
| CN105443481A (en) * | 2014-12-09 | 2016-03-30 | 徐州重型机械有限公司 | Series-parallel crane multitandem valve and hydraulic system and crane |
| CN105443481B (en) * | 2014-12-09 | 2018-01-12 | 徐州重型机械有限公司 | Series parallel type crane banked direction control valves, hydraulic system and crane |
| CN104743457A (en) * | 2015-02-28 | 2015-07-01 | 徐州徐工随车起重机有限公司 | Double-cylinder amplitude-variable hydraulic control system for dual-side lateral crane |
| CN110848194A (en) * | 2019-11-21 | 2020-02-28 | 徐州天睿地机械有限公司 | Externally-connected converging valve for mobile hydraulic power station |
| CN110848194B (en) * | 2019-11-21 | 2021-07-30 | 徐州天睿地机械有限公司 | Externally-connected converging valve for mobile hydraulic power station |
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