CN103410804A - Hydraulic double-pump confluence control device and all-terrain crane - Google Patents
Hydraulic double-pump confluence control device and all-terrain crane Download PDFInfo
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- CN103410804A CN103410804A CN2013103747040A CN201310374704A CN103410804A CN 103410804 A CN103410804 A CN 103410804A CN 2013103747040 A CN2013103747040 A CN 2013103747040A CN 201310374704 A CN201310374704 A CN 201310374704A CN 103410804 A CN103410804 A CN 103410804A
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Abstract
The invention relates to a hydraulic double-pump confluence control device and an all-terrain crane. The hydraulic double-pump confluence control device comprises a confluence solenoid valve, a main overflow valve and an interlocking structure, an oil inlet and an oil outlet of the main overflow valve are communicated with a second oil pump and an oil tank respectively, the interlocking structure is composed of two closed pilot operated check valves, and confluence switching is performed by the confluence solenoid valve. According to the hydraulic double-pump confluence control device, the interlocking confluence control mode that the closed pilot operated check valves and the confluence solenoid valve are combined for control is adopted, during confluence of oil pumps, and oil output by the second oil pump is directly connected to a confluence point connected with a first oil pump in an out-of-valve confluence mode rather than through the confluence solenoid valve in existing hydraulic confluence control systems, so that the confluence solenoid valve only serves as a channel for controlling the oil. Compared with existing hydraulic confluence control systems, the hydraulic double-pump confluence control device has the advantages that the flow of the confluence solenoid valve can be reduced, the spool diameter of the confluence solenoid valve can be reduced, the size of an electromagnet can be reduced, the power consumption is low, and the reliability is high.
Description
Technical field
The present invention relates to engineering machinery field, relate in particular to a kind of hydraulic double-pump interflow control gear and full Terrain Cranes.
Background technique
Crane chassis supporting leg hydraulic system often adopts an oil pump to realize the control purpose to cross cylinder and Vertical Cylinders, facts have proved that this application is feasible and simple and reliable.But the progressively increase along with full Terrain Cranes tonnage, adopt traditional H shape outrigger 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 supporting leg form, except needs cross cylinder and Vertical Cylinders action, during work, need first supporting leg to be shown, therefore increased oscillating oil cylinder, while travelling, car load is because weight limits also needs to dismantle movable supporting legs, therefore increased again the plugging pin oil cylinder of dismounting movable supporting legs, so, the supporting leg pump is just being born the work of a plurality of actuators.
Because the required flow of each actuator is variant, reduce as far as possible simultaneously the quantity of oil pump, usually the control program that the A pump that the employing discharge capacity is larger at present and the less B pump of discharge capacity provide, wherein the A pump provides hydraulic oil to cross cylinder and oscillating oil cylinder, the B pump provides hydraulic oil for plugging pin oil cylinder, and need flow larger during due to the 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 was controlled, the two-bit triplet solenoid directional control valve was as the interflow element.The 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 the B pump is by one-way valve connecting bolt oil cylinder control valve.Operation when plugging pin oil cylinder is different from Vertical Cylinders, when the plugging pin oil cylinder operation, the B pump is by one-way valve and through the direct connecting bolt oil cylinder of two-bit triplet solenoid directional control valve control valve, and to realize the plugging pin oil cylinder operation, now the two-bit triplet solenoid directional control valve must not be electric; When the operation of needs Vertical Cylinders, the two-bit triplet solenoid directional control valve obtains electric, the work of right position, and the B pump leads to one-way valve, then through the fluid of one-way valve, realizes interflow through two-bit triplet solenoid directional control valve and A pump, is switched to the supporting leg control valve.The purpose at A pump and B pump interflow while realizing the Vertical Cylinders operation.
There is following shortcoming at present in this hydraulic converging control system:
1) interflow solenoid valve size is restricted by flow: because solenoid valve adopts slide-valve structure, the flow of this kind interflow mode B pump will first pass 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 mode still can be used for small flow, if when the B pump duty becomes large, spool will be done greatly, because of electromagnet, is the power resources that promote spool, so electromagnet also will be done greatly.Whole like this valve piece will be done greatly, some heaviness that seems, and also electromagnet is large, and power ratio control is just large, and the electric weight that consumes the car load power supply is just large.
2) reliability is not high: in today of hydraulics development, be accompanied by the increase of flow, the enlarged diameter of spool, and then the active force that promotes spool also increases, it is difficult that traditional electromagnetic valve has become, the control form of spool becomes hydraulic control form (promoting spool by hydraulic pilot oil, electric switch and the size of controlling guide oil) by pure electric magnet control gradually.Because adopting large magnet control, it is difficult that magnet control seems, therefore the reliability of whole control is not high.
3) interchangeability is not strong: consider the requirement of interflow to the two-bit triplet solenoid directional control valve, this valve need to adopt plug-in type or plate valve.And the application of the valve of this kind function is less, while when breaking down, needing to change, must select the less valve-type of this kind application, interchangeability is poor.
Summary of the invention
The objective of the invention is to propose a kind of hydraulic double-pump interflow control gear and full Terrain Cranes, can realize the hydraulic double-pump interflow control that flow is larger with control spool and the electromagnet of reduced size.
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, the filler opening of described main relief valve and oil outlet 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 the 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 the second oil pump without the 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 the bevel-type spool.
Further, described interflow solenoid valve is conventional two-position four-way solenoid directional control valve, at described interflow solenoid valve, be under the state of not energising, described the second oil pump communicates with the pilot control hydraulic fluid port of described first guide's close type Pilot operated check valve by described interflow solenoid valve, described fuel tank communicates with the pilot control hydraulic fluid port of described second guide's close type Pilot operated check valve by described interflow solenoid valve, described the second oil pump by described second guide's close type Pilot operated check valve directly to described non-interflow load fuel feeding.
Further, at described interflow solenoid valve, be under the state of energising, described the second oil pump communicates with the pilot control hydraulic fluid port of described second guide's close type Pilot operated check valve by described interflow solenoid valve, described fuel tank communicates with the pilot control hydraulic fluid port of described first guide's close type Pilot operated check valve by described interflow solenoid valve, the fuel feeding of described the second oil pump collaborates in described junction of two streams by the fuel feeding of described first guide's close type Pilot operated check valve and described the first oil pump, and is supplied to the load of described interflow.
Further, also comprise the multi-load pressure control device, 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, be located in same valve body, described multi-load pressure control device can be realized the pressure control of described the first oil pump corresponding to the different loads level.
Further, described multi-load pressure control device comprises plurality of electromagnetic selector valve and relief valve, described plurality of electromagnetic selector valve and relief valve comprise the first relief valve, the second solenoid directional control valve and the corresponding induced pressure of the first solenoid directional control valve and corresponding induced pressure the second relief valve, the 3rd solenoid directional control valve and corresponding induced pressure the 3rd relief valve and corresponding to non-loaded pilot-type relief valve.
Further, the filler opening of described pilot-type relief valve and return opening communicate with described the 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 the second solenoid directional control valve, an actuator port of described the second solenoid directional control valve communicates with the filler opening of described the 3rd solenoid directional control valve, an actuator port of described the 3rd solenoid directional control valve communicates with the filler opening of described the first solenoid directional control valve, the return opening of the actuator port of described the first solenoid directional control valve and described the second solenoid directional control valve and the 3rd solenoid directional control valve all communicates with described fuel tank, the filler opening of described the first relief valve and return opening communicate with pilot control hydraulic fluid port and the described fuel tank of described pilot-type relief valve respectively, the filler opening of described the second relief valve and return opening communicate with another actuator port and the described fuel tank of described the second solenoid directional control valve respectively, the filler opening of described the 3rd relief valve and return opening communicate with another actuator port and the described fuel tank of described the 3rd solenoid directional control valve respectively.
For achieving the above object, the invention provides a kind of full Terrain Cranes, the first oil pump that comprises larger flow, the second oil pump than 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 junction of two streams of 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 and the first oil pump of larger flow is connected described Vertical Cylinders.
Further, the outlet of described the first oil pump and the second oil pump is equipped with one-way valve.
Further, on described fuel tank, also be provided with return filter and oil absorption filter.
Based on technique scheme, the interlocking interflow control mode that the present invention has adopted guide's close type Pilot operated check valve and interflow solenoid valve combination to control, when oil pump collaborates, the fluid of the second oil pump output is directly received the first oil pump connected junction of two streams in the mode at the outer interflow of valve, and no longer need to be through the interflow solenoid valve as existing hydraulic converging control system, thereby make to collaborate solenoid valve only as the passage of controlling fluid, than existing hydraulic converging control system, can reduce the flow of interflow solenoid valve, and then make its spool latus rectum can do littlely, the electromagnet volume also can be less, power consumption still less, reliability is higher.
The accompanying drawing explanation
Accompanying drawing described herein is used to provide a further understanding of the present invention, forms the application's a part, and schematic description and description of the present invention the present invention does not form inappropriate limitation of the present invention for explaining.In the accompanying drawings:
Fig. 1 is an embodiment's of hydraulic double-pump of the present invention interflow control gear hydraulic principle schematic diagram.
Fig. 2 is the hydraulic principle schematic diagram that has adopted Fig. 1 embodiment's full Terrain Cranes embodiment.
Fig. 3 is another embodiment's of the full Terrain Cranes of the present invention hydraulic principle schematic diagram.
Embodiment
Below by drawings and Examples, technological scheme of the present invention is described in further detail.
As shown in Figure 1, the hydraulic principle schematic diagram that collaborates an embodiment of control gear for hydraulic double-pump of the present invention.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 piece, also can be arranged to as required combination valve block etc.
The filler opening of main relief valve 2 and oil outlet communicate with the second oil pump B and fuel tank T than small flow by the P2 hydraulic fluid port on valve piece in Fig. 1 and T hydraulic fluid port respectively, are mainly used in controlling the oil pressure of the pressure oil that the second oil pump B exports.Filler opening and the return opening of interflow solenoid valve 1 also communicate with the second oil pump B and fuel tank T by the P2 hydraulic fluid port on the valve piece and T hydraulic fluid port respectively, and whether the pressure oil that is mainly used to control the second oil pump B output collaborates with the pressure oil that the first oil pump A exports.
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 the communicating with the second oil pump B by the P2 hydraulic fluid port on the valve piece without the 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 can directly connect the load of non-interflow by the L1 hydraulic fluid port on the valve piece, and the first oil pump A of the spring terminal hydraulic fluid port of first guide's close type Pilot operated check valve 3 and larger flow be connected the junction of two streams of collaborating load and communicate, in this junction of two streams, form interflow.
From the embodiment of Fig. 1, can see, the switching of interflow solenoid valve can realize the variation of oil pressure of the pilot control hydraulic fluid port of two guide's closed type Pilot operated check valves.Under the state of fuel feeding not, corresponding guide's closed type Pilot operated check valve is in closed condition, the fluid of the second oil pump B output can not pass through this guide's closed type Pilot operated check valve, and make the pilot control hydraulic fluid port of guide's closed type Pilot operated check valve possess certain oil pressure in case collaborate solenoid valve by switching, the fluid of the second oil pump B output just can pass through this guide's closed type Pilot operated check valve.
Different load that two guide's closed type Pilot operated check valves that arrange in the present embodiment are corresponding respectively, corresponding to the less situation of load, do not need to collaborate, directly by the second oil pump B, carrying out fuel feeding gets final product, and for the higher situation of load, need interflow, by the first oil pump A and the second oil pump B by collaborating to come common fuel feeding.
Like this, when the interflow solenoid valve is switched to different states, can make two guide's closed type Pilot operated check valves of two actuator ports that are connected to the interflow solenoid valve select one connection, make the second oil pump B carry out the fuel feeding of non-interflow load or collaborate with the first oil pump A by guide's closed type Pilot operated check valve of this connection, for fuel feeding is carried out in the interflow load.Can see, no matter be any switching state, the fuel feeding of the second oil pump B is all to carry out the conveying of fluid by guide's closed type Pilot operated check valve of connecting, and carry without the oil circuit through solenoid valve inside, interflow, and the oil circuit of solenoid valve inside, interflow just is used to provide the pressure control of the pilot control hydraulic fluid port that enough supplies guide's closed type Pilot operated check valve, this function is less to the requirement of oil mass, therefore without as the solenoid valve of existing interflow, needing larger latus rectum and electromagnet, it is less that the interflow solenoid valve of the present embodiment can be made, adopt less electromagnet, this also makes cost, 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 the 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 the interflow solenoid valve, spring acting in conjunction with first guide's close type Pilot operated check valve, and adopt the bevel-type spool can realize very reliably zero leakage of flow, and while needing interflow, can back down spool 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, at the interflow solenoid valve, be under the state of not energising, the second oil pump communicates with the pilot control hydraulic fluid port of first guide's close type Pilot operated check valve by the interflow solenoid valve, fuel tank communicates with the pilot control hydraulic fluid port of second guide's close type Pilot operated check valve by the 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, solenoid valve is under the state of energising at interflow, the second oil pump communicates with the pilot control hydraulic fluid port of second guide's close type Pilot operated check valve by the interflow solenoid valve, fuel tank communicates with the pilot control hydraulic fluid port of first guide's close type Pilot operated check valve by the interflow solenoid valve, the fuel feeding of the second oil pump collaborates 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 the interflow load.
Can see, adopt conventional two-position four-way solenoid directional control valve can realize the interflow requirement of the large flow that the present invention will realize fully, and this solenoid directional control valve do not need to adopt plug-in type or plate valve, so interchangeability is better.
As shown in Figure 2, be the full Terrain Cranes embodiment's that adopted Fig. 1 embodiment hydraulic principle schematic diagram.In Fig. 2, can see, full Terrain Cranes comprises the A oil pump 5 of larger flow, than the B oil pump 6 of small flow, fuel tank 7, cross cylinder, Vertical Cylinders, oscillating oil cylinder and plugging pin oil cylinder.Full Terrain Cranes also comprises hydraulic double-pump interflow control gear shown in Figure 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 the valve piece, 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 the plugging pin oil cylinder operation is less, the fluid provided than the B oil pump 6 of small flow can meet the needs of plugging pin oil cylinder, therefore without collaborating, and required flow is larger during the Vertical Cylinders operation, therefore needs B oil pump 6 and A oil pump 5 interflow to carry out fuel feeding.
In Fig. 2, can also one- way valve 11,10 be set in the outlet of A oil pump 5 and B oil pump 6, be used for preventing that fluid from flowing backwards, with the protection oil pump.Further, the return filter 9 that the fluid that returns to fuel tank is filtered and the oil absorption filter 8 filtered be input to the fluid oil pump from fuel tank can also be set on fuel tank 7.These two kinds of filters can be realized the protection of oil pump and other hydraulic element.
Hydraulic double-pump of the present invention interflow control gear can also realize further that the pressure of multi-load controls, with unequally loaded needs such as the cross cylinder that is applicable to full Terrain Cranes, oscillating oil cylinders.As shown in Figure 3, be another embodiment's of the full Terrain Cranes of the present invention hydraulic principle schematic diagram.Embodiment compares with front, hydraulic double-pump interflow control gear in the present embodiment also comprises the multi-load pressure control device, 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, be located in same valve body, the multi-load pressure control device can be realized the pressure control of A oil pump corresponding to the different loads level.
In conjunction with Fig. 3, can see, the multi-load pressure control device comprises plurality of electromagnetic selector valve and relief valve, comprising the 3rd relief valve 17 of the second relief valve 15, the 3rd solenoid directional control valve 16 and the corresponding induced pressure (pressure III) of the first relief valve 13, the second solenoid directional control valve 14 and the corresponding induced pressure (pressure II) of the first solenoid directional control valve 18 and corresponding induced pressure (pressure I) with corresponding to non-loaded pilot-type relief valve 12.
On 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 return opening of the actuator port of the first solenoid directional control valve 18 and the second solenoid directional control valve 14 and the 3rd solenoid directional control valve 16 all communicates with fuel tank 7, the filler opening of the first relief valve 13 and return opening communicate with pilot control hydraulic fluid port and the fuel tank 7 of pilot-type relief valve 12 respectively, the filler opening of the second relief valve 15 and return opening communicate with another actuator port and the fuel tank 7 of the second solenoid directional control valve 14 respectively, the filler opening of the 3rd relief valve 17 and return opening communicate with another actuator port and the fuel tank 7 of the 3rd solenoid directional control valve 16 respectively.
On concrete control, when needing the oil pressure of A oil pump 5 delivery pressure I grades, make the first solenoid directional control valve 18 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, now the pressure I that sets of the first relief valve 13 works; When needing the oil pressure of A oil pump 5 delivery pressure II grades, make the second solenoid directional control valve 14 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, now the pressure II that sets of the second relief valve 15 works; When needing the oil pressure of A oil pump 5 delivery pressure III grades, make the 3rd solenoid directional control valve 16 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, now the pressure III that sets of the 3rd relief valve 17 works.
When there is no the load operation, all solenoid directional control valves in the multi-load pressure control device all must not be electric, now guide's hydraulic fluid port of pilot-type relief valve 12 directly leads to fuel tank 7, and the fluid of A oil pump 5 outputs directly flows 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, the present invention is had been described in detail, those of ordinary skill in the field are to be understood that: still can modify or the part technical characteristics is equal to replacement the specific embodiment of the present invention; And not breaking away from the spirit of technical solution of the present invention, it all should be encompassed in the middle of the technological scheme scope that the present invention asks for protection.
Claims (10)
1. a hydraulic double-pump collaborates control gear, comprise interflow solenoid valve and main relief valve, the filler opening of described main relief valve and oil outlet 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 the 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 the second oil pump without the 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 according to claim 1 interflow control gear, 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 the bevel-type spool.
3. hydraulic double-pump according to claim 1 collaborates control gear, it is characterized in that, described interflow solenoid valve is conventional two-position four-way solenoid directional control valve, at described interflow solenoid valve, be under the state of not energising, described the second oil pump communicates with the pilot control hydraulic fluid port of described first guide's close type Pilot operated check valve by described interflow solenoid valve, described fuel tank communicates with the pilot control hydraulic fluid port of described second guide's close type Pilot operated check valve by described interflow solenoid valve, described the 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 according to claim 3 collaborates control gear, it is characterized in that, at described interflow solenoid valve, be under the state of energising, described the second oil pump communicates with the pilot control hydraulic fluid port of described second guide's close type Pilot operated check valve by described interflow solenoid valve, described fuel tank communicates with the pilot control hydraulic fluid port of described first guide's close type Pilot operated check valve by described interflow solenoid valve, the fuel feeding of described the second oil pump collaborates in described junction of two streams by the fuel feeding of described first guide's close type Pilot operated check valve and described the first oil pump, and be supplied to the load of described interflow.
5. hydraulic double-pump according to claim 1 collaborates control gear, it is characterized in that, also comprise the multi-load pressure control device, 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, be located in same valve body, described multi-load pressure control device can be realized the pressure control of described the first oil pump corresponding to the different loads level.
6. hydraulic double-pump according to claim 5 collaborates control gear, it is characterized in that, described multi-load pressure control device comprises plurality of electromagnetic selector valve and relief valve, described plurality of electromagnetic selector valve and relief valve comprise the first relief valve, the second solenoid directional control valve and the corresponding induced pressure of the first solenoid directional control valve and corresponding induced pressure the second relief valve, the 3rd solenoid directional control valve and corresponding induced pressure the 3rd relief valve and corresponding to non-loaded pilot-type relief valve.
7. hydraulic double-pump according to claim 6 collaborates control gear, it is characterized in that, the filler opening of described pilot-type relief valve and return opening communicate with described the 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 the second solenoid directional control valve, an actuator port of described the second solenoid directional control valve communicates with the filler opening of described the 3rd solenoid directional control valve, an actuator port of described the 3rd solenoid directional control valve communicates with the filler opening of described the first solenoid directional control valve, the return opening of the actuator port of described the first solenoid directional control valve and described the second solenoid directional control valve and the 3rd solenoid directional control valve all communicates with described fuel tank, the filler opening of described the first relief valve and return opening communicate with pilot control hydraulic fluid port and the described fuel tank of described pilot-type relief valve respectively, the filler opening of described the second relief valve and return opening communicate with another actuator port and the described fuel tank of described the second solenoid directional control valve respectively, the filler opening of described the 3rd relief valve and return opening communicate with another actuator port and the described fuel tank of described the 3rd solenoid directional control valve respectively.
8. full Terrain Cranes, the first oil pump that comprises larger flow, the second oil pump than small flow, fuel tank, cross cylinder, Vertical Cylinders, oscillating oil cylinder and plugging pin oil cylinder, it is characterized in that, also comprise the arbitrary described hydraulic double-pump of claim 1～7 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 junction of two streams of 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 and the first oil pump of larger flow is connected described Vertical Cylinders.
9. full Terrain Cranes according to claim 8, is characterized in that, the outlet of described the first oil pump and the second oil pump is equipped with one-way valve.
10. full Terrain Cranes according to claim 8, is characterized in that, on described fuel tank, also is provided with return filter and oil absorption filter.
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103790883A (en) * | 2014-01-25 | 2014-05-14 | 中国北方车辆研究所 | Double-pump flow dividing control valve |
| WO2023130627A1 (en) * | 2022-01-05 | 2023-07-13 | 三一汽车起重机械有限公司 | Hydraulic system with adjustable power, adjusting method and work machine |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4686828A (en) * | 1984-01-13 | 1987-08-18 | Dynamic Hydraulic Systems, Inc. | Hydraulically operated clamshell device |
| JP2005121043A (en) * | 2003-10-14 | 2005-05-12 | Nabtesco Corp | Hydraulic circuit and confluence valve in the circuit |
| 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 |
-
2013
- 2013-08-26 CN CN201310374704.0A patent/CN103410804B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4686828A (en) * | 1984-01-13 | 1987-08-18 | Dynamic Hydraulic Systems, Inc. | Hydraulically operated clamshell device |
| JP2005121043A (en) * | 2003-10-14 | 2005-05-12 | Nabtesco Corp | Hydraulic circuit and confluence valve in the circuit |
| 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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| CN103790883A (en) * | 2014-01-25 | 2014-05-14 | 中国北方车辆研究所 | Double-pump flow dividing control valve |
| 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 |
| WO2023130627A1 (en) * | 2022-01-05 | 2023-07-13 | 三一汽车起重机械有限公司 | Hydraulic system with adjustable power, adjusting method and work machine |
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Address after: 221000 68 Gaoxin Road, Xuzhou economic and Technological Development Zone, Jiangsu Patentee after: Xuzhou Heavy Machinery Co., Ltd. Address before: No. 165, Tongshan Road, Xuzhou, Jiangsu Province Patentee before: Xuzhou Heavy Machinery Co., Ltd. |