CN103883571A - Electrohydraulic control multi-pump quantitive confluence hydraulic system for loading machines - Google Patents
Electrohydraulic control multi-pump quantitive confluence hydraulic system for loading machines Download PDFInfo
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- CN103883571A CN103883571A CN201310693873.0A CN201310693873A CN103883571A CN 103883571 A CN103883571 A CN 103883571A CN 201310693873 A CN201310693873 A CN 201310693873A CN 103883571 A CN103883571 A CN 103883571A
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Abstract
Disclosed is an electrohydraulic control multi-pump quantitive confluence hydraulic system for loading machines. A steering system is provided with a first auxiliary pump. A first control valve group used for controlling the oil supplying direction of the first auxiliary pump is arranged between the first auxiliary pump and a steering system main oilway. In the low speed segment of an engine, the first control valve group controls the first auxiliary pump to supply oil to the steering system; in the high speed segment of the engine, the first control valve group controls the first auxiliary pump to supply oil to an operating system. The operating system is provided with a second auxiliary pump. In the low speed segment of the engine, a second control valve group controls the second auxiliary pump to supply oil to the steering system; in the high speed segment of the engine, the second control valve group controls the second auxiliary pump to supply oil to the operating system. The electrohydraulic control multi-pump quantitive confluence hydraulic system has the advantages that combination of the multi-pump technology and electric-control technology is adopted, energy saving is realized effectively, and the flow of the steering system can be controlled in a flow targeted value no matter what state the engine speed is in.
Description
Technical field
The present invention relates to the hydraulic system of loader, particularly the quantitatively hydraulic system at interflow of the many pumps of a kind of loader electrichydraulic control.
Background technique
The hydraulic system of existing loader is generally made up of hydraulic system of working, steering hydraulic system and hydraulic braking system etc., hydraulic system of working is often made up of elements such as working pump, distributing valve, pilot valve, boom cylinder, rotary ink tanks, steering hydraulic system is often made up of elements such as steering pump, pressure-gradient control valve, commutator (flux amplification valve), steering cylinders, and hydraulic braking system is often made up of elements such as brake pump, liquid-filling valve, brake valve, accumulators.At present, loaders most on market still adopt fixed dilivery hydraulic system, and loader as domestic in Liu work, casual labourer, imperial work, Xia Gong etc. is manufactured business, and more than 90% loader is all to have adopted quantitative system; Also have quantitatively and the mutually combine situation of use of variable delivery hydraulic system, as CAT938G, Liu work are determined variable delivery hydraulic system, tall building work is determined variable delivery hydraulic system etc.; In high-end loader, almost adopt entire variable hydraulic system, as blocked the current main products of international renowned company such as the later product of special H series, Volvo, little Song.Fixed dilivery hydraulic system is than variable delivery hydraulic system, it is high that it has ripe degree, good reliability, resistance tocrocking is strong, cost performance advantages of higher, and fixed dilivery hydraulic system can meet the normal operation requirement of loader completely, but fixed dilivery hydraulic system is also deposited deficiency in many aspects, the shortcoming such as controllability as serious in energy loss, that can not carry out composite move operation, system is bad, hydraulic shock is large.Adopt hydraulic system of working and the separate scheme of steering hydraulic system, this scheme requires working pump and steering pump all to need to have enough large discharge capacity just can make the normal operation of machine, take 5 tons of transloaders as example, generally, the working pump discharge capacity of this system is often selected 160cc left and right, be often about 80cc and turn to pump delivery, the total discharge capacity of system is in 240cc left and right.The shortcoming of this system has: 1. energy loss is serious; 2. action engine is easily flame-out simultaneously under high capacity for work system and steering system; 3 steering system turn to easily unstable in the time of high engine speeds, and when low speed, oil mass is inadequate; 4. the hydraulic shock of oil cylinder stroke terminal is large; 5. system heating is serious etc.
In order to reduce working pump discharge capacity and to prevent motor easy flame-out problem under hydraulic system high capacity, use Dual-pump flow-converging technology.Turn to preferential, in the time that steering system turns to demand, the fluid of steering pump is preferentially supplied with steering system, unnecessary fluid collaborates work system, and in the time not turning to, all fluid of steering pump all collaborate in the middle of work system, it is in the time that the pressure of work system reaches certain value that system is provided with unloading valve, by the fluid off-load of steering pump, reduce engine load by force, avoid flame-out.The shortcoming of this system has: 1. energy loss makes moderate progress compared with autonomous system, but steering pump cross the loss of pressure-gradient control valve and exist always, the pressure-gradient control valve of producing is both at home and abroad when by 140L/min flow, most is lost within the scope of 1-2MPa; 2. owing to turning to pump delivery not diminish, therefore steering system same existence in the time of high engine speeds turns to easily unstablely, and when low speed, oil mass is inadequate; 3. the hydraulic shock of oil cylinder stroke terminal is large; 4. system heating is serious etc.
In order to improve steering system bad problem of steering operation when the high low speed of motor, use three pump system, in the time of low engine speed state, there are two pumps simultaneously to steering system fuel feeding, steering system while having solved low speed is for shortage of oil problem, in the time of high engine speeds state, only have a pump to steering system fuel feeding, solve the unstable problem of high speed steering.The shortcoming that this system exists is: 1. in the time not turning to, because the fluid of steering pump flows back to fuel tank through signal control valve, pressure-gradient control valve and commutator meta, energy loss herein has 3-4MPa left and right, and energy loss is more serious; 2. do not use unloading valve, when high load, motor is easily flame-out; 3. work pump delivery can not reduce too much, and the Energy Intensity Reduction of work system is not obvious; 4. when work system works independently, pump total displacement is in 160cc left and right, and the impact of oil cylinder stroke terminal is serious etc.
Object of the present invention is just to provide a kind of application of many pumps technology in conjunction with electronic control technology that adopt, automatically distribute pump delivery according to the state of system, can effectively realize energy-conservation, electrichydraulic control combines, can reduce the complexity of hydraulic pipe line, reduce hydraulic leak point, and electric line is easy to arrange, three sections of flow modes of speed regulation of steering system, no matter engine speed is at what state, can be by the flow control of steering system within the scope of flow target value, guarantee the stability of steering system, low speed three oil pump feeds, middling speed double pump fuel feeding, the single oil pump feed of high speed, the many pumps of the significant loader electrichydraulic control of energy-saving effect are the hydraulic system at interflow quantitatively.
Solution of the present invention is such:
The present invention mainly contains steering system and work system, and wherein steering system comprises steering pump and steering cylinder, and work system comprises working pump and rotary ink tank, boom cylinder, it is characterized in that:
(1), described steering system is provided with the first service pump, between the first service pump and steering system working connection, be provided with the first control valve group of controlling the first service pump fuel feeding direction, low speed segment in motor, by the first control valve group control by the first service pump to steering system fuel feeding, in high engine speeds section, by the first control valve group control by the first service pump to work system fuel feeding;
(2), described work system is provided with the second service pump, between the second service pump and work system working connection, be provided with the second control valve group of controlling the second service pump fuel feeding direction, in low engine speed section, by the second control valve group control by the second service pump to steering system fuel feeding, in motor high speed section, by the second control valve group control by the second service pump to work system fuel feeding;
(3), in steering system working connection, be provided with flux amplification valve, the preferential valve port of described flux amplification valve is received work system working connection by automatically controlled unloading valve, for in loader working procedure, by remaining steering system fluid through the pressure-gradient control valve of flux amplification valve and automatically controlled unloading valve to work system fuel feeding.
Technological scheme also comprises more specifically: described the first control valve group comprises the first solenoid directional control valve, the second solenoid directional control valve; The turn signal that described the first solenoid directional control valve detects by pressure switch is controlled, and described the second solenoid directional control valve is controlled by the signal that detects engine speed.
Further: described the second control valve group comprises the 3rd solenoid directional control valve, the 4th solenoid directional control valve, the turn signal that described the 4th solenoid directional control valve detects by pressure switch is controlled, and described the 3rd solenoid directional control valve is controlled by detecting engine speed.
Further: to be parallel with electromagnetic relief valve at described work delivery side of pump, for when the cylinder movement of work system is when approaching stroke end, by detecting the displacement signal of oil cylinder, directly the fluid of working pump to be unloaded to oil sump tank.
Further: described engine speed is divided into low speed segment, middling speed section, high regime, described low speed segment is idling-1150rpm; Described middling speed section is 1150-1600rpm; Described high regime is 1600-2200rpm.
Advantage of the present invention is to adopt the application of many pumps technology in conjunction with electronic control technology, automatically distribute pump delivery according to the state of system, can effectively realize energy-conservation, electrichydraulic control combines, can reduce the complexity of hydraulic pipe line, reduce hydraulic leak point, and electric line is easy to arrange, three sections of flow modes of speed regulation of steering system, no matter engine speed is at what state, can be by the flow control of steering system within the scope of flow target value, guarantee the stability of steering system, low speed three oil pump feeds, middling speed double pump fuel feeding, the single oil pump feed of high speed, energy-saving effect is remarkable.
Accompanying drawing explanation
Fig. 1 is embodiments of the invention.
Fig. 2 is near principle enlarged diagram Fig. 1 working pump.
Fig. 3 is near principle enlarged diagram Fig. 1 steering pump.
Fig. 4 is the automatically controlled unloading valve principle schematic of the present invention.
Fig. 5 is engine speed of the present invention and the graph of a relation that enters steering system flow.
Accompanying drawing explanation
In figure, 1-shuttle valve 2-pressure switch 3-commutator 4-reduction valve 5-second solenoid directional control valve 6-first solenoid directional control valve 7-steering pump 8-hydraulic oil container 9-first service pump 10-relief valve 11-radiator 12-the second service pump 13-working pump 14-electromagnetic relief valve 15-the 3rd solenoid directional control valve 16-the 4th solenoid directional control valve 17-pressure switch 18-unloading electromagnetic valve 19-distributing valve 20-rotary ink tank 21-boom cylinder 22-steering cylinder 23-flux amplification valve.
Embodiment
The present invention as shown in Figure 1, mainly contain steering system and work system, wherein steering system comprises steering pump 7 and steering cylinder 22, work system comprises working pump 13 and rotary ink tank 20, boom cylinder 21, described steering system is provided with the first service pump 9, between the first service pump 9 and steering system working connection, be provided with the first control valve group of controlling the first service pump fuel feeding direction, low speed segment in motor, by the first control valve group control by the first service pump to steering system fuel feeding, in high engine speeds section, by the first control valve group control by the first service pump to work system fuel feeding,
Described work system is provided with the second service pump, between the second service pump and work system working connection, be provided with the second control valve group of controlling the second service pump fuel feeding direction, in low engine speed section, by the second control valve group control by the second service pump to steering system fuel feeding, in motor high speed section, by the second control valve group control by the second service pump to work system fuel feeding;
In steering system working connection, be provided with flux amplification valve 23, the preferential valve port of described flux amplification valve 23 is received work system working connection by automatically controlled unloading valve 18, for in loader working procedure, by remaining steering system fluid through the pressure-gradient control valve of flux amplification valve 23 and automatically controlled unloading valve 18 to work system fuel feeding.
Described the first control valve group comprises the first solenoid directional control valve 6, the second solenoid directional control valve 5; The turn signal that described the first solenoid directional control valve 6 detects by pressure switch is controlled, and described the second solenoid directional control valve 5 is controlled by the signal that detects engine speed.
Described the second control valve group comprises the 3rd solenoid directional control valve 15, the 4th solenoid directional control valve 16, and the turn signal that described the 4th solenoid directional control valve 16 detects by pressure switch is controlled, and described the 3rd solenoid directional control valve 15 is controlled by detecting engine speed.
Take 5 tons of transloaders as example, the optional 60cc of work pump delivery left and right, turns to the optional 50cc of pump delivery left and right, the optional 20cc of the first service pump discharge capacity left and right, and the optional 30cc of the second auxiliary pump delivery left and right, the total discharge capacity of system maintains 160cc left and right.
The flow of steering system divides three sections of controls, at low engine speed section (idling-1150rpm), by detect engine rotational speed signal, make the electromagnet 4YA of the second solenoid directional control valve 5 and the electromagnet 3YA of the 4th solenoid directional control valve 16 simultaneously electric; By the turn signal of detected pressures switch 2, make the electromagnet 4YA of the first solenoid directional control valve 6 and the electromagnet 2YA of the 3rd solenoid directional control valve 15 simultaneously electric, now by steering pump 7, the first service pump 9 together with the second service pump 12 give steering system fuel feeding.At medium engine speed section (1150-1600rpm), by detecting engine rotational speed signal, the electromagnet 4YA of the second solenoid directional control valve 5 is obtained electric, make the electromagnet 3YA dead electricity of the 4th solenoid directional control valve 16; By the turn signal of detected pressures switch 2, make the electromagnet 4YA of the first solenoid directional control valve 6 and the electromagnet 2YA of the 3rd solenoid directional control valve 15 simultaneously electric, now preferentially give together steering system fuel feeding by steering pump 7, the first service pump 9, pressure-gradient control valve and the automatically controlled unloading valve 18 of all the other fluid in flux amplification valve 23 flows in the middle of hydraulic system of working, gives work system fuel feeding with working pump 13 together with the second service pump 9.At high engine speeds section (1600-2200rpm), by detecting engine rotational speed signal, make the electromagnet 4YA of the second solenoid directional control valve 5 and the electromagnet 3YA of the 4th solenoid directional control valve 16 dead electricity simultaneously; By the turn signal of detected pressures switch 2, make the electromagnet 4YA of the first solenoid directional control valve 6 and the electromagnet 2YA of the 3rd solenoid directional control valve 15 simultaneously electric, now only by steering pump 7 separately to steering system fuel feeding, the fluid of the first service pump flows into hydraulic system of working through the left position PW mouth of the right position of the first solenoid directional control valve 6 P8 mouth to the second solenoid directional control valve 5 through automatically controlled unloading valve 18, and the fluid of the second service pump flows into hydraulic system of working through the left position P5 mouth of the right position of the 3rd solenoid directional control valve 15 P2 mouth to the four solenoid directional control valves 16.As long as electromagnet 4YA and electromagnet 2YA have turn signal at once to respond electricly, the response condition of electromagnet 5YA be engine speed lower than 1600rpm, the response condition of electromagnet 3YA is that engine speed is lower than 1150rpm.By these three sections of flow controls, according to above-mentioned selected pump displacement, be that 80-115L/min(idling speed is 800rpm at the flow of low speed segment steering system); The flow of middling speed section steering system is 80.5-112L/min; The flow of high regime steering system is the high speed 2200rpm of 80-110L/min(motor), as shown in drawings, no matter motor is in which type of rotating speed state, the flow that can guarantee to supply with steering system, within the little scope of fluctuation, is realized and is turned to requirement stably.
In system, use automatically controlled unloading valve 18, electromagnetic switch valve 25 effects are in the time that the pressure of work system reaches the setting value of pressure switch 17, electromagnet 8YA is obtained electric, the flow off-load of steering pump 7, the first service pump 9 and second service pump 12 of the automatically controlled unloading valve 18 of process, can effectively guarantee that like this motor can not stop working, and reduce unnecessary high-pressure high-flow spill losses.The effect of electromagnetic switch valve 27 is to move to while approaching stroke end when the boom cylinder 21 of work system or rotary ink tank 20, by detecting the displacement signal of oil cylinder, make electromagnet 6YA obtain the electric pump duty off-load of controlling the automatically controlled unloading valve of flowing through, in reducing the impact of oil cylinder stroke terminal, avoid unnecessary high-pressure high-flow spill losses.Boom cylinder 21 or rotary ink tank 20 are in the time of limit position, due to oil cylinder displacement transducer, to have signal that electromagnet 6YA is obtained electric, the fluid of the spring chamber of external control unloading valve 24 can flow back to T mouth and the fluid off-load of this unloading valve that makes to flow through, while now handling an other group oil cylinder, because the flow through automatically controlled unloading valve 18 is laid down, cause underfed, the effect that electromagnetic switch valve 26 is set is exactly under these limited conditionss, do not allow the fluid of unloading valve 24 spring chambers unload oil sump tank through electromagnetic valve switch valve 27, electromagnet 7YA starts shooting and obtains electric, 7YA dead electricity while there is limited conditions, automatically controlled unloading valve 18 does not have Unloading Effect.
At an outlet electromagnetic relief valve 14 in parallel of working pump 13, its effect is when the cylinder movement of work system is when approaching stroke end, by detecting the displacement signal of oil cylinder, electromagnet 1YA is obtained electric, directly the fluid of working pump 13 is unloaded to oil sump tank 8, now 6YA also simultaneously electric, like this in the time that oil cylinder approaches stroke end, only have the second service pump 12 to work system fuel feeding, in greatly reducing the impact of oil cylinder stroke terminal, avoided high-pressure high-flow overflow.In engine speed in low speed segment, due to 2YA and 3YA all obtain electric, in order to guarantee the work of work system, when low speed segment 1YA can not obtain electric, utilize 3YA electricly pin that not allow 1YA obtain electric.
Claims (5)
1. the quantitatively hydraulic system at interflow of the many pumps of loader electrichydraulic control, mainly contains steering system and work system, and wherein steering system comprises steering pump and steering cylinder, and work system comprises working pump and rotary ink tank, boom cylinder, it is characterized in that:
(1), described steering system is provided with the first service pump, between the first service pump and steering system working connection, be provided with the first control valve group of controlling the first service pump fuel feeding direction, low speed segment in motor, by the first control valve group control by the first service pump to steering system fuel feeding, in high engine speeds section, by the first control valve group control by the first service pump to work system fuel feeding;
(2), described work system is provided with the second service pump, between the second service pump and work system working connection, be provided with the second control valve group of controlling the second service pump fuel feeding direction, in low engine speed section, by the second control valve group control by the second service pump to steering system fuel feeding, in motor high speed section, by the second control valve group control by the second service pump to work system fuel feeding;
(3), in steering system working connection, be provided with flux amplification valve, the preferential valve port of described flux amplification valve is received work system working connection by automatically controlled unloading valve, for in loader working procedure, by remaining steering system fluid through the pressure-gradient control valve of flux amplification valve and automatically controlled unloading valve to work system fuel feeding.
2. the quantitatively hydraulic system at interflow of the many pumps of loader electrichydraulic control according to claim 1, is characterized in that: described the first control valve group comprises the first solenoid directional control valve, the second solenoid directional control valve; The turn signal that described the first solenoid directional control valve detects by pressure switch is controlled, and described the second solenoid directional control valve is controlled by the signal that detects engine speed.
3. the quantitatively hydraulic system at interflow of the many pumps of loader electrichydraulic control according to claim 1, it is characterized in that: described the second control valve group comprises the 3rd solenoid directional control valve, the 4th solenoid directional control valve, the turn signal that described the 4th solenoid directional control valve detects by pressure switch is controlled, and described the 3rd solenoid directional control valve is controlled by detecting engine speed.
4. the quantitatively hydraulic system at interflow of the many pumps of loader electrichydraulic control according to claim 1, it is characterized in that: be parallel with electromagnetic relief valve at described work delivery side of pump, for when the cylinder movement of work system is when approaching stroke end, by detecting the displacement signal of oil cylinder, directly the fluid of working pump is unloaded to oil sump tank.
5. according to the quantitatively hydraulic system at interflow of the many pumps of loader electrichydraulic control described in claim 2 or 3, it is characterized in that: described engine speed is divided into low speed segment, middling speed section, high regime, described low speed segment is idling-1150rpm; Described middling speed section is 1150-1600rpm; Described high regime is 1600-2200rpm.
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| CN201310693873.0A CN103883571B (en) | 2013-12-18 | 2013-12-18 | The many pumps of loading machine electrichydraulic control are the hydraulic system at interflow quantitatively |
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| CN201310693873.0A CN103883571B (en) | 2013-12-18 | 2013-12-18 | The many pumps of loading machine electrichydraulic control are the hydraulic system at interflow quantitatively |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104806588A (en) * | 2015-04-01 | 2015-07-29 | 广西柳工机械股份有限公司 | Two-pump confluence hydraulic control system |
| CN105298954A (en) * | 2015-11-25 | 2016-02-03 | 上海电气液压气动有限公司 | Hydraulic station system |
| CN108657271A (en) * | 2018-07-09 | 2018-10-16 | 雷沃重工股份有限公司 | tractor hydraulic system and tractor |
| CN109533018A (en) * | 2018-11-26 | 2019-03-29 | 雷沃重工股份有限公司 | Farm equipment hydraulic system and farm equipment |
| CN113606207A (en) * | 2021-06-28 | 2021-11-05 | 徐工集团工程机械股份有限公司科技分公司 | Loader hydraulic system and loader |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN104806588A (en) * | 2015-04-01 | 2015-07-29 | 广西柳工机械股份有限公司 | Two-pump confluence hydraulic control system |
| CN105298954A (en) * | 2015-11-25 | 2016-02-03 | 上海电气液压气动有限公司 | Hydraulic station system |
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| CN113606207A (en) * | 2021-06-28 | 2021-11-05 | 徐工集团工程机械股份有限公司科技分公司 | Loader hydraulic system and loader |
| CN113606207B (en) * | 2021-06-28 | 2022-07-05 | 徐工集团工程机械股份有限公司科技分公司 | Loader hydraulic system and loader |
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