CN103410804B - Hydraulic double-pump interflow control gear and full Terrain Cranes - Google Patents
Hydraulic double-pump interflow control gear and full Terrain Cranes Download PDFInfo
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- CN103410804B CN103410804B CN201310374704.0A CN201310374704A CN103410804B CN 103410804 B CN103410804 B CN 103410804B CN 201310374704 A CN201310374704 A CN 201310374704A CN 103410804 B CN103410804 B CN 103410804B
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Abstract
The present invention relates to a kind of hydraulic double-pump interflow control gear and full Terrain Cranes, hydraulic double-pump interflow control gear comprises interflow solenoid valve and main relief valve, the filler opening of main relief valve and oil outlet communicate with the second oil pump and fuel tank respectively, also comprise the interlocking structure that two guide's close type Pilot operated check valves are formed, carry out interflow by interflow solenoid valve and switch.Present invention employs the interlocking interflow control mode of guide's close type Pilot operated check valve and interflow solenoid valve combination control, during oil pump interflow, the fluid that second oil pump exports directly receives first oil pump connected junction of two streams in the mode that valve collaborates outward, and no longer need through interflow solenoid valve as existing hydraulic converging control system, thus make interflow solenoid valve only as the passage controlling fluid, compared to existing hydraulic converging control system, the flow of interflow solenoid valve can be reduced, and then make its spool latus rectum can do less, electromagnet volume also can be less, power consumption is less, reliability is higher.
Description
Technical field
The present invention relates to engineering machinery field, particularly relate to a kind of hydraulic double-pump interflow control gear and full Terrain Cranes.
Background technique
The control object that crane chassis support leg hydraulic system often adopts oil pump to realize cross cylinder and Vertical Cylinders, facts have proved that this application is feasible and simple and reliable.But along with the progressively increase of full Terrain Cranes tonnage, traditional H-shaped outrigger is adopted to require more and more higher to frame strength, therefore super-tonnage crane extensively adopts the less demanding radial outrigger of frame strength, this kind of supporting leg form, except needs cross cylinder and Vertical Cylinders action, need during work first supporting leg to be shown, therefore add oscillating oil cylinder, during traveling car load due to weight limits also need dismantle movable supporting legs, therefore turn increase the plugging pin oil cylinder of dismounting movable supporting legs, so, supporting leg pump just carries the work of multiple actuator.
Needed for each actuator, flow is variant, reduce the quantity of oil pump as far as possible simultaneously, adopt at present usually the control program that the larger A pump of discharge capacity and the less B pump of discharge capacity provide, wherein A pump provides hydraulic oil to cross cylinder and oscillating oil cylinder, B pump provides hydraulic oil for plugging pin oil cylinder, and owing to needing flow comparatively large during Vertical Cylinders operation, therefore adopt the form at A pump and B pump interflow.
In the supporting leg interflow of existing hydraulic control system of landing legs controls, two-bit triplet solenoid directional control valve is as interflow element.A pump is by one-way valve connection leg control valve (cross cylinder and Vertical Cylinders control valve) and oscillating oil cylinder control valve, and B pump is by one-way valve connecting bolt ram control valve.Operation when plugging pin oil cylinder is different from Vertical Cylinders, when plugging pin oil cylinder operation, B pump is by one-way valve and through the direct connecting bolt ram control valve of two-bit triplet solenoid directional control valve, and to realize plugging pin oil cylinder operation, now two-bit triplet solenoid directional control valve must not be electric; When the operation of needs Vertical Cylinders, two-bit triplet solenoid directional control valve obtains electric, and the work of right position, B pump leads to one-way valve, then realizes collaborating through the fluid of one-way valve through two-bit triplet solenoid directional control valve and A pump, is switched to supporting leg control valve.The object at A pump and B pump interflow when realizing Vertical Cylinders operation.
There is following shortcoming at present in this hydraulic converging control system:
1) collaborate solenoid valve size to restrict by flow: because solenoid valve adopts slide-valve structure, the flow of this kind of interflow mode B pump will first through the spool of two-bit triplet solenoid directional control valve.As everyone knows, the flow passed through is larger, and the size of spool will be larger, and this kind of mode still can use for small flow, if when B pump duty becomes large, spool will do greatly, because electromagnet is the power resources promoting spool, so electromagnet also will do greatly.Whole like this valve block will do greatly, seem that some is heavy, and electromagnet is large, controls power just large, and the electricity consuming car load power supply is just large.
2) reliability is not high: in today of hydraulics development, along with the increase of flow, the enlarged diameter of spool, and then the active force promoting spool also increases, traditional electromagnetic valve has become difficulty, the control form of spool becomes hydraulic control form (by hydraulic pilot oil to promote spool, electrically only controlling switch and the size of guide oil) from pure electric magnet control gradually.Because adopting large magnet control, magnet control seems difficult, therefore the reliability of whole control is not high.
3) interchangeability is not strong: consider the requirement of interflow to two-bit triplet solenoid directional control valve, and this valve needs to adopt plug-in type or plate valve.And the valve application of this kind of function is less, when needing when breaking down to change, must select the valve-type that this kind of application is less, interchangeability is poor.
Summary of the invention
The object of the invention is to propose a kind of hydraulic double-pump interflow control gear and full Terrain Cranes, the hydraulic double-pump interflow that can realize flow larger with the control spool of reduced size and electromagnet controls.
For achieving the above object, the invention provides a kind of hydraulic double-pump interflow control gear, comprise interflow solenoid valve and main relief valve, filler opening and the oil outlet of described main relief valve communicate with the second oil pump and fuel tank respectively, wherein, also comprise first guide's close type Pilot operated check valve and second guide's close type Pilot operated check valve, the filler opening of described interflow solenoid valve and return opening communicate with described second oil pump and fuel tank respectively, two actuator ports of described interflow solenoid valve communicate with the pilot control hydraulic fluid port of described first guide's close type Pilot operated check valve and the pilot control hydraulic fluid port of second guide's close type Pilot operated check valve respectively, all the communicating with described second oil pump without spring terminal hydraulic fluid port without spring terminal hydraulic fluid port and second guide's close type Pilot operated check valve of described first guide's close type Pilot operated check valve, the spring terminal hydraulic fluid port of described second guide's close type Pilot operated check valve connects the load of non-interflow, the spring terminal hydraulic fluid port of described first guide's close type Pilot operated check valve and the first oil pump all be connected the junction of two streams of collaborating load and communicate.
Further, described first guide's close type Pilot operated check valve and second guide's close type Pilot operated check valve all adopt bevel-type spool.
Further, described interflow solenoid valve is conventional two-position four-way solenoid directional control valve, under described interflow solenoid valve is in the state be not energized, described second oil pump is communicated by the pilot control hydraulic fluid port of described interflow solenoid valve with described first guide's close type Pilot operated check valve, described fuel tank is communicated by the pilot control hydraulic fluid port of described interflow solenoid valve with described second guide's close type Pilot operated check valve, described second oil pump by described second guide's close type Pilot operated check valve directly to described non-interflow load fuel feeding.
Further, under the state that described interflow solenoid valve is in energising, described second oil pump is communicated by the pilot control hydraulic fluid port of described interflow solenoid valve with described second guide's close type Pilot operated check valve, described fuel tank is communicated by the pilot control hydraulic fluid port of described interflow solenoid valve with described first guide's close type Pilot operated check valve, the fuel feeding of described second oil pump is collaborated in described junction of two streams by the fuel feeding of described first guide's close type Pilot operated check valve and described first oil pump, and is supplied to the load of described interflow.
Further, also comprise multi-load pressure control device, be located in same valve body with described interflow solenoid valve, described main relief valve, described first guide's close type Pilot operated check valve and described second guide's close type Pilot operated check valve, described multi-load pressure control device can realize the Stress control that described first oil pump corresponds to different loads level.
Further, described multi-load pressure control device comprises plurality of electromagnetic selector valve and relief valve, and described plurality of electromagnetic selector valve and relief valve comprise the 3rd relief valve of the second relief valve of the first relief valve of the first solenoid directional control valve and corresponding induced pressure, the second solenoid directional control valve and corresponding induced pressure, the 3rd solenoid directional control valve and corresponding induced pressure and correspond to non-loaded pilot-type relief valve.
Further, the filler opening of described pilot-type relief valve and return opening communicate with described first oil pump and fuel tank respectively, the pilot control hydraulic fluid port of described pilot-type relief valve communicates with the filler opening of described second solenoid directional control valve, an actuator port of described second solenoid directional control valve communicates with the filler opening of described 3rd solenoid directional control valve, an actuator port of described 3rd solenoid directional control valve communicates with the filler opening of described first solenoid directional control valve, the actuator port of described first solenoid directional control valve and the return opening of described second solenoid directional control valve and the 3rd solenoid directional control valve all communicate with described fuel tank, the filler opening of described first relief valve and return opening communicate with the pilot control hydraulic fluid port of described pilot-type relief valve and described fuel tank respectively, the filler opening of described second relief valve and return opening communicate with another actuator port of described second solenoid directional control valve and described fuel tank respectively, the filler opening of described 3rd relief valve and return opening communicate with another actuator port of described 3rd solenoid directional control valve and described fuel tank respectively.
For achieving the above object, the invention provides a kind of full Terrain Cranes, comprise the first oil pump compared with large discharge, compared with the second oil pump of small flow, fuel tank, cross cylinder, Vertical Cylinders, oscillating oil cylinder and plugging pin oil cylinder, it is characterized in that, also comprise aforesaid hydraulic double-pump interflow control gear, the spring terminal hydraulic fluid port of second guide's close type Pilot operated check valve in the control gear of described hydraulic double-pump interflow connects described plugging pin oil cylinder, the spring terminal hydraulic fluid port of first guide's close type Pilot operated check valve in the control gear of described hydraulic double-pump interflow is connected described Vertical Cylinders with the junction of two streams of the first oil pump compared with large discharge.
Further, described first oil pump and the second oily delivery side of pump are equipped with one-way valve.
Further, described fuel tank is also provided with return filter and oil absorption filter.
Based on technique scheme, present invention employs the interlocking interflow control mode of guide's close type Pilot operated check valve and interflow solenoid valve combination control, when oil pump collaborates, the fluid that second oil pump exports directly receives first oil pump connected junction of two streams in the mode that valve collaborates outward, and no longer need through interflow solenoid valve as existing hydraulic converging control system, thus make interflow solenoid valve only as the passage controlling fluid, compared to existing hydraulic converging control system, the flow of interflow solenoid valve can be reduced, and then make its spool latus rectum can do less, electromagnet volume also can be less, power consumption is less, reliability is higher.
Accompanying drawing explanation
Accompanying drawing described herein is used to provide a further understanding of the present invention, and form a application's part, schematic description and description of the present invention, for explaining the present invention, does not form inappropriate limitation of the present invention.In the accompanying drawings:
Fig. 1 is the hydraulic principle schematic diagram of an embodiment of hydraulic double-pump of the present invention interflow control gear.
Fig. 2 is the hydraulic principle schematic diagram of the full Terrain Cranes embodiment that have employed Fig. 1 embodiment.
Fig. 3 is the hydraulic principle schematic diagram of another embodiment of the full Terrain Cranes of the present invention.
Embodiment
Below by drawings and Examples, technological scheme of the present invention is described in further detail.
As shown in Figure 1, be the hydraulic principle schematic diagram of an embodiment of hydraulic double-pump interflow of the present invention control gear.In the present embodiment, hydraulic double-pump interflow control gear comprises interflow solenoid valve 1, main relief valve 2, first guide's close type Pilot operated check valve 3 and second guide's close type Pilot operated check valve 4.These valve members can be arranged in same valve block, also can be arranged to combination valve block etc. as required.
The filler opening of main relief valve 2 and oil outlet lead to compared with the second oil pump B of small flow and fuel tank T-phase respectively by the P2 hydraulic fluid port on valve block in Fig. 1 and T hydraulic fluid port, are mainly used in the oil pressure of the pressure oil that control second oil pump B exports.The interflow filler opening of solenoid valve 1 and return opening also lead to the second oil pump B and fuel tank T-phase respectively by the P2 hydraulic fluid port on valve block and T hydraulic fluid port, and the pressure oil whether pressure oil being mainly used to control second oil pump B output exports with the first oil pump A collaborates.
As seen from Figure 1, two actuator ports of interflow solenoid valve 1 communicate with the pilot control hydraulic fluid port of first guide's close type Pilot operated check valve 3 and the pilot control hydraulic fluid port of second guide's close type Pilot operated check valve 4 respectively, all being communicated with the second oil pump B by the P2 hydraulic fluid port on valve block without spring terminal hydraulic fluid port without spring terminal hydraulic fluid port and second guide's close type Pilot operated check valve 4 of first guide's close type Pilot operated check valve 3, the spring terminal hydraulic fluid port of second guide's close type Pilot operated check valve 4 directly can connect the load of non-interflow by the L1 hydraulic fluid port on valve block, and the spring terminal hydraulic fluid port of first guide's close type Pilot operated check valve 3 with compared with large discharge the first oil pump A be connected the junction of two streams of collaborating load and communicate, interflow is formed in this junction of two streams.
Can see from the embodiment of Fig. 1, the switching of interflow solenoid valve can realize the change of the oil pressure of the pilot control hydraulic fluid port of two guide's closed type Pilot operated check valves.Under the state of non-fuel feeding, corresponding guide's closed type Pilot operated check valve is in closed condition, the fluid that second oil pump B exports is not by this guide's closed type Pilot operated check valve, and once make the pilot control hydraulic fluid port of guide's closed type Pilot operated check valve possess certain oil pressure by switching interflow solenoid valve, then the fluid that the second oil pump B exports just can pass through this guide's closed type Pilot operated check valve.
Different load that two the guide's closed type Pilot operated check valves arranged in the present embodiment are corresponding respectively, corresponding to the situation that load is less, do not need to collaborate, directly carry out fuel feeding by the second oil pump B, and for the higher situation of load, then need interflow, by the first oil pump A and the second oil pump B by collaborating to come common fuel feeding.
Like this, when collaborating solenoid valve and being switched to different states, two guide's closed type Pilot operated check valves of two actuator ports being connected to interflow solenoid valve can be made to select the connection of, the second oil pump B is made to carry out the fuel feeding of non-interflow load by guide's closed type Pilot operated check valve of this connection or collaborate with the first oil pump A, for fuel feeding is carried out in interflow load.Can see, no matter be any switching state, the fuel feeding of the second oil pump B is all the conveying being carried out fluid by guide's closed type Pilot operated check valve of connection, and without the need to carrying through the oil circuit of solenoid valve inside, interflow, and the oil circuit collaborating solenoid valve inside is just used to provide enough for the Stress control of the pilot control hydraulic fluid port of guide's closed type Pilot operated check valve, the requirement of this function to oil mass is less, therefore without the need to needing larger latus rectum and electromagnet as the solenoid valve of existing interflow, it is less that the interflow solenoid valve of the present embodiment can make, adopt less electromagnet, this also makes cost reduce, control stability and reliability increase.
First guide's close type Pilot operated check valve and second guide's close type Pilot operated check valve preferably adopt bevel-type spool.When not collaborating, the fluid of the second oil pump arrives the pilot control hydraulic fluid port of first guide's close type Pilot operated check valve by interflow solenoid valve, with the spring acting in conjunction of first guide's close type Pilot operated check valve, and adopt bevel-type spool can realize zero leakage of flow very reliably, and when needing interflow, spool can be backed down easily and realize interflow, the interlocking structure of this guide's close type Pilot operated check valve structurally fairly simple that, be easy to realize, and also very reliable in application.
Selecting of interflow solenoid valve, preferred conventional two-position four-way solenoid directional control valve, under interflow solenoid valve is in the state be not energized, second oil pump is communicated with the pilot control hydraulic fluid port of first guide's close type Pilot operated check valve by interflow solenoid valve, fuel tank is communicated with the pilot control hydraulic fluid port of second guide's close type Pilot operated check valve by interflow solenoid valve, and the second oil pump passes through second guide's close type Pilot operated check valve directly to non-interflow load fuel feeding.
Further, under the state that interflow solenoid valve is in energising, second oil pump is communicated with the pilot control hydraulic fluid port of second guide's close type Pilot operated check valve by interflow solenoid valve, fuel tank is communicated with the pilot control hydraulic fluid port of first guide's close type Pilot operated check valve by interflow solenoid valve, the fuel feeding of the second oil pump is collaborated in junction of two streams by the fuel feeding of first guide's close type Pilot operated check valve and the first oil pump, and is supplied to interflow load.
Can see, adopt conventional two-position four-way solenoid directional control valve can realize the interflow requirement of the large discharge that the present invention will realize completely, and this solenoid directional control valve does not need to adopt plug-in type or plate valve, therefore interchangeability is better.
As shown in Figure 2, for have employed the hydraulic principle schematic diagram of the full Terrain Cranes embodiment of Fig. 1 embodiment.Can see in fig. 2, full Terrain Cranes comprises the A oil pump 5 compared with large discharge, the B oil pump 6 compared with small flow, fuel tank 7, cross cylinder, Vertical Cylinders, oscillating oil cylinder and plugging pin oil cylinder.Full Terrain Cranes also comprises the hydraulic double-pump interflow control gear shown in Fig. 1, the spring terminal hydraulic fluid port of second guide's close type Pilot operated check valve 4 in the control gear of hydraulic double-pump interflow is by the L1 hydraulic fluid port connecting bolt oil cylinder on valve block, and the spring terminal hydraulic fluid port of first guide's close type Pilot operated check valve 3 in the control gear of hydraulic double-pump interflow is connected Vertical Cylinders with the junction of two streams L2 of A oil pump.
Flow required during plugging pin oil cylinder operation is less, the fluid provided compared with the B oil pump 6 of small flow can meet the needs of plugging pin oil cylinder, therefore without the need to collaborating, and flow required during Vertical Cylinders operation is comparatively large, therefore needs B oil pump 6 and A oil pump 5 interflow to carry out fuel feeding.
In fig. 2, one-way valve 11,10 can also be set in the outlet of A oil pump 5 and B oil pump 6, be used for preventing fluid from flowing backwards, to protect oil pump.Further, the return filter 9 that filters the fluid returning fuel tank can also be set on fuel tank 7 and to the oil absorption filter 8 being input to the fluid in oil pump from fuel tank and filtering.These two kinds of filters can realize the protection of oil pump and other hydraulic element.
Hydraulic double-pump interflow of the present invention control gear can also realize the Stress control of multi-load further, to be applicable to the unequally loaded needs such as cross cylinder, oscillating oil cylinder of full Terrain Cranes.As shown in Figure 3, be the hydraulic principle schematic diagram of another embodiment of the full Terrain Cranes of the present invention.Compared with preceding embodiment, hydraulic double-pump interflow control gear in the present embodiment also comprises multi-load pressure control device, be located in same valve body with interflow solenoid valve 1, main relief valve 2, first guide's close type Pilot operated check valve 3 and second guide's close type Pilot operated check valve 4, multi-load pressure control device can realize the Stress control that A oil pump corresponds to different loads level.
Composition graphs 3 can be seen, multi-load pressure control device comprises plurality of electromagnetic selector valve and relief valve, comprising the second relief valve 15 of the first relief valve 13, second solenoid directional control valve 14 of the first solenoid directional control valve 18 and corresponding induced pressure (pressure I) and corresponding induced pressure (pressure II), the 3rd solenoid directional control valve 16 and corresponding induced pressure (pressure III) the 3rd relief valve 17 and correspond to non-loaded pilot-type relief valve 12.
In annexation, the filler opening of pilot-type relief valve 12 and return opening communicate with A oil pump 5 and fuel tank 7 respectively, the pilot control hydraulic fluid port of pilot-type relief valve 12 communicates with the filler opening of the second solenoid directional control valve 14, an actuator port of the second solenoid directional control valve 14 communicates with the filler opening of the 3rd solenoid directional control valve 16, an actuator port of the 3rd solenoid directional control valve 16 communicates with the filler opening of the first solenoid directional control valve 18, the actuator port of the first solenoid directional control valve 18 and the return opening of the second solenoid directional control valve 14 and the 3rd solenoid directional control valve 16 all communicate with fuel tank 7, the filler opening of the first relief valve 13 and return opening communicate with the pilot control hydraulic fluid port of pilot-type relief valve 12 and fuel tank 7 respectively, the filler opening of the second relief valve 15 and return opening communicate with another actuator port of the second solenoid directional control valve 14 and fuel tank 7 respectively, the filler opening of the 3rd relief valve 17 and return opening communicate with another actuator port of the 3rd solenoid directional control valve 16 and fuel tank 7 respectively.
On concrete control, when needing the oil pressure of A oil pump 5 delivery pressure I grade, the first solenoid directional control valve 18 is made to obtain electric, now the first solenoid directional control valve 18 is switched to right position, and the second solenoid directional control valve 14 and the 3rd solenoid directional control valve 16 not electric and be in left position, then the pressure I now set by the first relief valve 13 works; When needing the oil pressure of A oil pump 5 delivery pressure II grade, the second solenoid directional control valve 14 is made to obtain electric, now the second solenoid directional control valve 14 is switched to right position, and the first solenoid directional control valve 18 and the 3rd solenoid directional control valve 16 not electric and be in left position, then the pressure II now set by the second relief valve 15 works; When needing the oil pressure of A oil pump 5 delivery pressure III grade, the 3rd solenoid directional control valve 16 is made to obtain electric, now the 3rd solenoid directional control valve 16 is switched to right position, and the first solenoid directional control valve 18 and the second solenoid directional control valve 14 not electric and be in left position, then the pressure III now set by the 3rd relief valve 17 works.
When there is no load operation, all solenoid directional control valves in multi-load pressure control device all must not be electric, now guide's hydraulic fluid port of pilot-type relief valve 12 directly lead to fuel tank 7, A oil pump 5 export fluid directly flow back to fuel tank 7 by this pilot-type relief valve 12 with very little pressure.
Finally should be noted that: above embodiment is only in order to illustrate that technological scheme of the present invention is not intended to limit; Although with reference to preferred embodiment to invention has been detailed description, those of ordinary skill in the field are to be understood that: still can modify to the specific embodiment of the present invention or carry out equivalent replacement to portion of techniques feature; And not departing from the spirit of technical solution of the present invention, it all should be encompassed in the middle of the technological scheme scope of request of the present invention protection.
Claims (10)
1. a hydraulic double-pump interflow control gear, comprise interflow solenoid valve and main relief valve, filler opening and the oil outlet of described main relief valve communicate with the second oil pump and fuel tank respectively, it is characterized in that, also comprise first guide's close type Pilot operated check valve and second guide's close type Pilot operated check valve, the filler opening of described interflow solenoid valve and return opening communicate with described second oil pump and fuel tank respectively, two actuator ports of described interflow solenoid valve communicate with the pilot control hydraulic fluid port of described first guide's close type Pilot operated check valve and the pilot control hydraulic fluid port of second guide's close type Pilot operated check valve respectively, all the communicating with described second oil pump without spring terminal hydraulic fluid port without spring terminal hydraulic fluid port and second guide's close type Pilot operated check valve of described first guide's close type Pilot operated check valve, the spring terminal hydraulic fluid port of described second guide's close type Pilot operated check valve connects the load of non-interflow, the spring terminal hydraulic fluid port of described first guide's close type Pilot operated check valve and the first oil pump all be connected the junction of two streams of collaborating load and communicate.
2. hydraulic double-pump interflow according to claim 1 control gear, it is characterized in that, described first guide's close type Pilot operated check valve and second guide's close type Pilot operated check valve all adopt bevel-type spool.
3. hydraulic double-pump interflow according to claim 1 control gear, it is characterized in that, described interflow solenoid valve is conventional two-position four-way solenoid directional control valve, under described interflow solenoid valve is in the state be not energized, described second oil pump is communicated by the pilot control hydraulic fluid port of described interflow solenoid valve with described first guide's close type Pilot operated check valve, described fuel tank is communicated by the pilot control hydraulic fluid port of described interflow solenoid valve with described second guide's close type Pilot operated check valve, described second oil pump by described second guide's close type Pilot operated check valve directly to described non-interflow load fuel feeding.
4. hydraulic double-pump interflow according to claim 3 control gear, it is characterized in that, under the state that described interflow solenoid valve is in energising, described second oil pump is communicated by the pilot control hydraulic fluid port of described interflow solenoid valve with described second guide's close type Pilot operated check valve, described fuel tank is communicated by the pilot control hydraulic fluid port of described interflow solenoid valve with described first guide's close type Pilot operated check valve, the fuel feeding of described second oil pump is collaborated in described junction of two streams by the fuel feeding of described first guide's close type Pilot operated check valve and described first oil pump, and be supplied to the load of described interflow.
5. hydraulic double-pump interflow according to claim 1 control gear, it is characterized in that, also comprise multi-load pressure control device, be located in same valve body with described interflow solenoid valve, described main relief valve, described first guide's close type Pilot operated check valve and described second guide's close type Pilot operated check valve, described multi-load pressure control device can realize the Stress control that described first oil pump corresponds to different loads level.
6. hydraulic double-pump interflow according to claim 5 control gear, it is characterized in that, described multi-load pressure control device comprises plurality of electromagnetic selector valve and relief valve, and described plurality of electromagnetic selector valve and relief valve comprise the 3rd relief valve of the second relief valve of the first relief valve of the first solenoid directional control valve and corresponding induced pressure, the second solenoid directional control valve and corresponding induced pressure, the 3rd solenoid directional control valve and corresponding induced pressure and correspond to non-loaded pilot-type relief valve.
7. hydraulic double-pump interflow according to claim 6 control gear, it is characterized in that, the filler opening of described pilot-type relief valve and return opening communicate with described first oil pump and fuel tank respectively, the pilot control hydraulic fluid port of described pilot-type relief valve communicates with the filler opening of described second solenoid directional control valve, an actuator port of described second solenoid directional control valve communicates with the filler opening of described 3rd solenoid directional control valve, an actuator port of described 3rd solenoid directional control valve communicates with the filler opening of described first solenoid directional control valve, the actuator port of described first solenoid directional control valve and the return opening of described second solenoid directional control valve and the 3rd solenoid directional control valve all communicate with described fuel tank, the filler opening of described first relief valve and return opening communicate with the pilot control hydraulic fluid port of described pilot-type relief valve and described fuel tank respectively, the filler opening of described second relief valve and return opening communicate with another actuator port of described second solenoid directional control valve and described fuel tank respectively, the filler opening of described 3rd relief valve and return opening communicate with another actuator port of described 3rd solenoid directional control valve and described fuel tank respectively.
8. a full Terrain Cranes, comprise the first oil pump compared with large discharge, compared with the second oil pump of small flow, fuel tank, cross cylinder, Vertical Cylinders, oscillating oil cylinder and plugging pin oil cylinder, it is characterized in that, also comprise claim 1 ~ 7 arbitrary described hydraulic double-pump interflow control gear, the spring terminal hydraulic fluid port of second guide's close type Pilot operated check valve in the control gear of described hydraulic double-pump interflow connects described plugging pin oil cylinder, the spring terminal hydraulic fluid port of first guide's close type Pilot operated check valve in the control gear of described hydraulic double-pump interflow is connected described Vertical Cylinders with the junction of two streams of the first oil pump compared with large discharge.
9. full Terrain Cranes according to claim 8, is characterized in that, described first oil pump and the second oily delivery side of pump are equipped with one-way valve.
10. full Terrain Cranes according to claim 8, is characterized in that, described fuel tank is also provided with return filter and oil absorption filter.
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| CN103790883B (en) * | 2014-01-25 | 2016-04-13 | 中国北方车辆研究所 | A kind of double pump assignment of traffic control valve |
| CN114294303A (en) * | 2022-01-05 | 2022-04-08 | 三一汽车起重机械有限公司 | Power-adjustable hydraulic system, power-adjustable hydraulic method and working machine |
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| US4686828A (en) * | 1984-01-13 | 1987-08-18 | Dynamic Hydraulic Systems, Inc. | Hydraulically operated clamshell device |
| CN102094861A (en) * | 2010-12-02 | 2011-06-15 | 徐州重型机械有限公司 | Multi-pump concurrent flow hydraulic system for crane and concurrent valve bank |
| CN202369268U (en) * | 2011-12-19 | 2012-08-08 | 中联重科股份有限公司 | Crane and hydraulic system for controlling tensile force of steel wire rope |
| CN203488467U (en) * | 2013-08-26 | 2014-03-19 | 徐州重型机械有限公司 | Hydraulic dual-pump converging control device and all-terrain crane |
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