CN203500145U - Pressure compensation and automatic unloading hydraulic system of loader fixed displacement pump - Google Patents
Pressure compensation and automatic unloading hydraulic system of loader fixed displacement pump Download PDFInfo
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- CN203500145U CN203500145U CN201320651675.3U CN201320651675U CN203500145U CN 203500145 U CN203500145 U CN 203500145U CN 201320651675 U CN201320651675 U CN 201320651675U CN 203500145 U CN203500145 U CN 203500145U
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Abstract
The utility model discloses a pressure compensation and automatic unloading hydraulic system of a loader fixed displacement pump. An oil outlet of a multi-way valve of the system is connected with a lifting hydraulic cylinder, a bucket hydraulic cylinder and a second shuttle valve are connected between an oil inlet and the oil outlet of the multi-way valve, a longitudinal oil opening of the second shuttle valve is connected with a horizontal oil opening of a first shuttle valve, and the other horizontal oil opening of the first shuttle valve is connected with the oil outlet of the multi-way valve. A longitudinal oil opening of the first shuttle valve is connected with a left control oil opening of a pressure compensation valve, and an oil inlet of the pressure compensation valve, the oil inlet of the multi-way valve, an oil outlet of a work pump and an oil outlet of an unloading valve are connected. An oil return opening of the pressure compensation valve, an oil return opening of the multi-way valve, an oil inlet of an oil radiator and an oil return opening of the unloading valve are connected. The oil return opening of the multi-way valve is connected with a hydraulic oil tank through the oil radiator, and the oil inlet of the unloading valve is connected with an oil outlet of a steering pump through a conversion valve. Operation comfortableness of the whole machine is improved, more energy is saved, driving force of a transmission system is improved, throttling and spill losses of the system are reduced, and the utilization rate of energy is improved.
Description
Technical field
The utility model relates to a kind of hydraulic system of loader.
Background technique
Traditional loader adopts quantitative gear pump system, and utilizes the principle of throttle grverning to carry out speed control to the lift cylinder of loader hydraulic system of working and bucket cylinder.Because throttle grverning exists the inherent characteristic that depends on valve port area and valve port front and back pressure reduction by the flow of valve port, for loader, even in the constant situation of main valve opening, the fluid flow that enters oil hydraulic cylinder by valve core of main valve during different engine is different, this just there will be Joystick when same angle, during the high rotating speed of motor, cylinder action is fast, the slow unfavorable phenomenon of cylinder action during the motor slow-speed of revolution.Center of gravity in working device of loader movement process is also to change always, so the pressure producing in oil hydraulic cylinder is also changing, before and after so just causing main valve valve port, pressure reduction, not stopping variation, causes that the flow that enters oil hydraulic cylinder changes, and further causes operating cylinder motion speed to change.The angle of traditional working device of loader Joystick when starting is just relevant to the shovel dress weight of material and the size of engine speed in a word, causes the unstable of manipulation.
For traditional loader dual-pump combining system, when loader does not turn to, in steering hydraulic control system, the hydraulic oil of steering pump output all collaborates to the system in work system forcibly by hydrovalve.This mode can be dwindled work pump delivery.But distributing valve, in meta or when entering bucket, receiving the spading materials such as bucket in high pressure small flow, just has a large amount of fluid high-pressure overflows in loader working hydraulic pressure control system.Energy consumption has reduced the moment of torsion that loader walking drives when increasing.
The off-load technology relating on present stage loader product has two kinds, and a kind of is to utilize Pressure Control Technology, and when the working pressure of work system reaches setting value, unloading valve is opened, and the flow of steering pump is realized Low-pressure load discharge oil sump tank through leader unload valve.This technology loop can, with load variations automaitc shfit, still, when induced pressure approaches the set pressure of unloading valve, easily occur that speed is unstable.Another kind is to utilize pilot pressure control technique, only, when distributing valve excavates position in receiving bucket, the pressure of drawing from pioneer pump, controls leader unload valve automatically, make leader unload valve in on-state, the flow of steering pump is realized Low-pressure load discharge oil sump tank through leader unload valve.The function that this system circuit can be realized is, only in spading operating mode, realizes high-pressure low-flow, and distributing valve still exists restriction loss when meta, has equally one-sidedness, also easily occurs that speed is unstable.Biliographic data: lid military rank, about the analysis of loader dual-pump combining energy saving of system effect, engineering machinery, 2005(9) .54-55; Xu Xinyue, Jing Junqing, double pump closes the application of shunting, pilot pressure off-load and Flow amplification type steering system, building machinery, 2006(7): 92.
Summary of the invention
In order to overcome known loader hydraulic system, handle the little defect of moment of torsion unstable, that energy consumption large, loader walking drives, the utility model provides a kind of loading machine quantitative pumping pressure compensation and automatic deloading hydraulic system, this loading machine quantitative pumping pressure compensation and automatic deloading hydraulic system can be stablized loader operation, and the moment of torsion that energy consumption is little, loader walking drives is large.
The technical solution adopted in the utility model is: this loading machine quantitative pumping pressure compensation and automatic deloading hydraulic system comprise multi-way valve, the oil outlet of multi-way valve is connected with lifting hydraulic cylinder, between the filler opening of multi-way valve and oil outlet, be connected with scraper bowl oil hydraulic cylinder and the second shuttle valve, longitudinal hydraulic fluid port of the second shuttle valve is connected with a horizontal hydraulic fluid port of the first shuttle valve, another horizontal hydraulic fluid port of the first shuttle valve is connected with the oil outlet of multi-way valve, longitudinal hydraulic fluid port of the first shuttle valve is connected with the left control port of pressure-compensated valve, the filler opening of pressure-compensated valve, the filler opening of multi-way valve, the oil outlet of working pump, the oil outlet of unloading valve is connected, the return opening of pressure-compensated valve, the return opening of multi-way valve, the filler opening that oil is loose, the return opening of unloading valve is connected, the return opening of multi-way valve falls apart and is connected with hydraulic oil container through oil, the oil outlet of working pump is connected with pressure relay, the filler opening of working pump is connected with hydraulic oil container by filter, the filler opening of unloading valve is connected with the oil outlet of steering pump by switching valve, the filler opening of steering pump passed through filtering mouth parts and was connected with hydraulic fluid tank, steering pump is connected with pioneer pump, pioneer pump filler opening is connected with hydraulic oil container through filter, the oil outlet of pioneer pump is connected with relief valve, the oil outlet of pioneer pump is connected with the control port of unloading valve by solenoid directional control valve.
The utility model is selected hydraulic system of working oil cylinder maximum load pressure and is passed to pressure-compensated valve, utilize the pressure difference of pressure-compensated valve to the compensation of low load connection they and maximum load, thereby before and after keeping each multi-way valve, pressure is induced pressure, the flow that finally makes to enter each executive component is only relevant with its multi-way valve spool aperture, finely solved the unlatching wild effect that control system is affected by load and engine speed to cause.
The mode that the utility model is used sensor to control solenoid valve break-make guide oil is opened Low-pressure load discharge valve, unloading valve adopts the structural type of cartridge valve to design, object is according to the conditions of demand of each system use traffic of loader, realization is shunted off-load from dynamic circuit connector, extend the time that unloading valve is opened simultaneously, reduce the compression shock and the noise that when unloading valve is opened, cause.Traffic requirement while both guaranteeing work, the return pressure loss while making meta is again as far as possible little.
Advantage of the present utility model: compared with the existing technology, by can make working device of loader starting and control stage and load irrelevant to the compensation of pressure before and after multi-way valve valve port, irrelevant with flow, improved the comfortable type of complete machine operation.By the seizure to work system pressure, utilize guide's mode to open the unloading valve of steering pump, make loader more energy-conservation and improve the driving force of power train in high-pressure low-flow demand.Throttling spill losses when improving and reducing hydraulic work system, reduces Hydraulic System Fever amount, improves capacity usage ratio.
Accompanying drawing explanation
Fig. 1 is an embodiment's of the utility model Hydraulic System Principle schematic diagram.
Fig. 2 is the structural representation of the pressure-compensated valve in Fig. 1.
In figure: 1, pressure-compensated valve, the 2, first shuttle valve, the 3, second shuttle valve, 4, scraper bowl oil hydraulic cylinder, 5, lifting hydraulic cylinder, 6, multi-way valve, 7, pressure relay, 8, working pump, 9, unloading valve, 10, switching valve, 11, solenoid directional control valve, 12, relief valve, 13, pioneer pump, 14, steering pump, 15, hydraulic oil container, 16, cartridge valve, 17, pilot relief valve, 18, one-way valve, 19, oil suction filter, 20, oil is loose; 21, valve body, 22, valve pocket, 23, valve is stifled, 24, spring, 25, spool, 26, Sealing.
Embodiment
Below in conjunction with drawings and Examples, the utility model is described.
In Fig. 1, this loading machine quantitative pumping pressure compensation and automatic deloading hydraulic system comprise multi-way valve 6, the oil outlet of multi-way valve 6 is connected with lifting hydraulic cylinder 5, between the filler opening of multi-way valve 6 and oil outlet, be connected with scraper bowl oil hydraulic cylinder 4 and the second shuttle valve 3, longitudinal hydraulic fluid port of the second shuttle valve 3 is connected with a horizontal hydraulic fluid port of the first shuttle valve 2, another horizontal hydraulic fluid port of the first shuttle valve 2 is connected with the oil outlet of multi-way valve 6, longitudinal hydraulic fluid port of the first shuttle valve 2 is connected with the left control port (II) of pressure-compensated valve 1, the filler opening of pressure-compensated valve 1 (I), the filler opening of multi-way valve 6, the oil outlet of working pump 8, the oil outlet of unloading valve 9 is connected, the return opening of pressure-compensated valve 1 (III), the return opening of multi-way valve 6, the filler opening of oil loose 20, the return opening of unloading valve 9 is connected, the return opening of multi-way valve 6 is connected with hydraulic oil container 15 through oil loose 20, the oil outlet of working pump 8 is connected with pressure relay 7, the filler opening of working pump 8 is connected with hydraulic oil container 15 by filter 19, the filler opening of unloading valve 9 is connected with the oil outlet of steering pump 14 by switching valve 10, the filler opening of steering pump 14 passed through filtering mouth parts and was connected with hydraulic fluid tank 15, steering pump 14 is connected with pioneer pump 13, pioneer pump 13 filler openings are connected with hydraulic oil container 15 through filter, the oil outlet of pioneer pump 13 is connected with relief valve 12, the oil outlet of pioneer pump 13 is connected with the control port of unloading valve 9 by solenoid directional control valve 11.
The load-transducing pressure of drawing from scraper bowl oil hydraulic cylinder 4 enters shuttle valve 3, the load-transducing pressure of drawing from lifting hydraulic cylinder 5 enters shuttle valve 2, by selecting maximum load pressure, pass to pressure-compensated valve 1, with pressure-compensated valve 1, guarantee that multi-way valve 6 inlet outlet pressure differentials maintain 15bar, the flow that consequently enters scraper bowl oil hydraulic cylinder 4 and lifting hydraulic cylinder 5 is only relevant with its selector valve aperture, has avoided causing each executive component phase mutual interference because load difference or engine speed change.Meanwhile, from shuttle valve 2 maximum load pressure and oil hydraulic pump delivery pressure out, act on pressure-compensated valve 1 simultaneously.When multi-way valve 6 valve core opening areas change, multi-way valve 6 spool inlet outlet pressure differentials can change, cause the balance of pressure-compensated valve 1 spool to be broken, according to Newton's third law pressure-compensated valve 1 spool, can come the pressure at the variation of control pump outlet pressure and then pilot pressure recuperation valve 1 spool two ends finally to make spool again to stablize by mobile draining, make multi-way valve 6 spool inlet outlet pressure differentials keep constant, the flow that past scraper bowl oil hydraulic cylinder 4 or lifting hydraulic cylinder 5 go and the proportional relation of opening amount of main valve plug.This has just realized working pump 8 and steering pump 14 output flows adapt to loader operation needs.Working pump 8 and steering pump 14 delivery pressures are followed all the time induced pressure and are changed, and slightly exceed a less force value than induced pressure.The spring pressure of pressure-compensated valve 1 is set and is slightly larger than that multi-way valve 6 spools are opened entirely and inlet pressure and shuttle valve 2 are selected maximum load pressure during full flow pressure difference.
At switching valve 10 to multi-way valve 6 these pipelines, working pressure unloading valve 9, pressure signal is taken from the filler opening of multi-way valve 6, when reaching predefined pressure unloading 13MPa, pressure relay 7 sends electrical signal, and solenoid directional control valve is opened, and the pressure oil of now pioneer pump 13 outputs can back down pilot relief valve 17, the main valve plug of cartridge valve 16 can be opened because of the pressure of steering pump 14 delivery outlets like this, realizes the Low-pressure load discharge function of steering pump 14.Now the pressure oil of working pump 8 can keep because of the effect of one-way valve 18, and scraper bowl oil hydraulic cylinder 4 and lifting hydraulic cylinder 5 are normally worked.The pressure maximum when pressure setting of pressure relay 7 should be slightly larger than boom cylinder normal hoisting load rating, to guarantee not to three of loader and to impact.
In Fig. 2, the utility model has comprised a kind of pressure-compensated valve.Spool 25 is issued to balance in the effect of filler opening I pressure, left control port II pressure and spring 24 power.Suppose in situation that the valve core opening of distributing valve 6 in Fig. 1 is constant, scraper bowl oil hydraulic cylinder 4 in Fig. 1 or the load of lifting hydraulic cylinder 5 strengthen moment suddenly, that in Fig. 2, the pressure of filler opening I does not come and change, spool 25 disequilibrium positions and moving to left in Fig. 2, the area that overlaps with hydraulic fluid port on valve pocket 22 of the hydraulic fluid port on spool 25 makes hydraulic fluid port filler opening I have enough pressure to raise to tackle the increase of load by reducing so.Final spool 25 can be again in state of equilibrium, and because of the displacement that spool moves less, so can think that the pressure difference value of filler opening I and left control port II still equals the setting pressure of spring, this has just guaranteed that in Fig. 1, multi-way valve 6 spool oil inlet and outlet pressure difference values are constant, and then has guaranteed that flow that working pump 8 in Fig. 1 exports hydraulic cylinder for working to is not subject to the control of load.
The valve core opening of supposing multi-way valve 6 in Fig. 1 remains unchanged, the moment that the rotating speed of working pump 8 strengthens suddenly in Fig. 1, in Fig. 2, the pressure of left control port II does not also have enough time to become, but the pressure of filler opening I can become greatly, and in Fig. 2, spool 25 will move to right until rebalancing like this.Guaranteed that like this working pump 8 in Fig. 1 supplies with under the prerequisite of the fluid stable of scraper bowl oil hydraulic cylinder and lifting hydraulic cylinder in Fig. 1, in the opening that unnecessary fluid spool 25 and valve pocket 22 from Fig. 2 increase, flowed out.
Pressure-compensated valve 1 is chosen maximum output pressure signal by shuttle valve 3 and through pressure-compensated valve 1, is controlled the pressure input signal of distributing valve 6, realizes the object of essence control work system.
Claims (1)
1. a loading machine quantitative pumping pressure compensates and automatic deloading hydraulic system, this loading machine quantitative pumping pressure compensation and automatic deloading hydraulic system comprise multi-way valve, it is characterized in that: the oil outlet of multi-way valve is connected with lifting hydraulic cylinder, between the filler opening of multi-way valve and oil outlet, be connected with scraper bowl oil hydraulic cylinder and the second shuttle valve, longitudinal hydraulic fluid port of the second shuttle valve is connected with a horizontal hydraulic fluid port of the first shuttle valve, another horizontal hydraulic fluid port of the first shuttle valve is connected with the oil outlet of multi-way valve, longitudinal hydraulic fluid port of the first shuttle valve is connected with the left control port of pressure-compensated valve, the filler opening of pressure-compensated valve, the filler opening of multi-way valve, the oil outlet of working pump, the oil outlet of unloading valve is connected, the return opening of pressure-compensated valve, the return opening of multi-way valve, the filler opening that oil is loose, the return opening of unloading valve is connected, the return opening of multi-way valve falls apart and is connected with hydraulic oil container through oil, the oil outlet of working pump is connected with pressure relay, the filler opening of working pump is connected with hydraulic oil container by filter, the filler opening of unloading valve is connected with the oil outlet of steering pump by switching valve, the filler opening of steering pump passed through filtering mouth parts and was connected with hydraulic fluid tank, steering pump is connected with pioneer pump, pioneer pump filler opening is connected with hydraulic oil container through filter, the oil outlet of pioneer pump is connected with relief valve, the oil outlet of pioneer pump is connected with the control port of unloading valve by solenoid directional control valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320651675.3U CN203500145U (en) | 2013-10-22 | 2013-10-22 | Pressure compensation and automatic unloading hydraulic system of loader fixed displacement pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320651675.3U CN203500145U (en) | 2013-10-22 | 2013-10-22 | Pressure compensation and automatic unloading hydraulic system of loader fixed displacement pump |
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| CN203500145U true CN203500145U (en) | 2014-03-26 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201320651675.3U Expired - Fee Related CN203500145U (en) | 2013-10-22 | 2013-10-22 | Pressure compensation and automatic unloading hydraulic system of loader fixed displacement pump |
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| CN (1) | CN203500145U (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103591062A (en) * | 2013-10-22 | 2014-02-19 | 徐工集团工程机械股份有限公司科技分公司 | Metering pump pressure compensation and automatic-unloading hydraulic system of loader |
| CN105155611A (en) * | 2015-08-27 | 2015-12-16 | 徐工集团工程机械股份有限公司科技分公司 | Intelligent control system of fixed-displacement hydraulic system for loader |
| CN105715590A (en) * | 2016-03-18 | 2016-06-29 | 广西柳工机械股份有限公司 | Unloading valve and loader variable speed hydraulic system |
| CN110118209A (en) * | 2019-05-23 | 2019-08-13 | 福州大学 | Guarantee the commutation control circuit system of HB concrete pump machine steady operation |
| CN111156209A (en) * | 2020-02-28 | 2020-05-15 | 雷沃工程机械集团有限公司 | Loader hydraulic steering system and loader |
| CN114810728A (en) * | 2022-04-13 | 2022-07-29 | 山重建机有限公司 | Multi-way valve digital twin model and modeling method thereof |
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2013
- 2013-10-22 CN CN201320651675.3U patent/CN203500145U/en not_active Expired - Fee Related
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103591062A (en) * | 2013-10-22 | 2014-02-19 | 徐工集团工程机械股份有限公司科技分公司 | Metering pump pressure compensation and automatic-unloading hydraulic system of loader |
| CN103591062B (en) * | 2013-10-22 | 2016-09-21 | 徐工集团工程机械股份有限公司科技分公司 | Loading machine quantitative pump pressure compensates and automatic deloading hydraulic system |
| CN105155611A (en) * | 2015-08-27 | 2015-12-16 | 徐工集团工程机械股份有限公司科技分公司 | Intelligent control system of fixed-displacement hydraulic system for loader |
| CN105155611B (en) * | 2015-08-27 | 2018-02-02 | 徐工集团工程机械股份有限公司科技分公司 | A kind of loading machine paced work hydraulic system Intelligent control system |
| CN105715590A (en) * | 2016-03-18 | 2016-06-29 | 广西柳工机械股份有限公司 | Unloading valve and loader variable speed hydraulic system |
| CN110118209A (en) * | 2019-05-23 | 2019-08-13 | 福州大学 | Guarantee the commutation control circuit system of HB concrete pump machine steady operation |
| CN110118209B (en) * | 2019-05-23 | 2023-10-20 | 福州大学 | Reversing control loop system for ensuring stable operation of HB concrete pump |
| CN111156209A (en) * | 2020-02-28 | 2020-05-15 | 雷沃工程机械集团有限公司 | Loader hydraulic steering system and loader |
| CN111156209B (en) * | 2020-02-28 | 2022-03-01 | 雷沃工程机械集团有限公司 | Loader hydraulic steering system and loader |
| CN114810728A (en) * | 2022-04-13 | 2022-07-29 | 山重建机有限公司 | Multi-way valve digital twin model and modeling method thereof |
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| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20140326 Termination date: 20171022 |