CN201891142U - Improved structure of hydraulic system of loader - Google Patents
Improved structure of hydraulic system of loader Download PDFInfo
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- CN201891142U CN201891142U CN2010205630688U CN201020563068U CN201891142U CN 201891142 U CN201891142 U CN 201891142U CN 2010205630688 U CN2010205630688 U CN 2010205630688U CN 201020563068 U CN201020563068 U CN 201020563068U CN 201891142 U CN201891142 U CN 201891142U
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Abstract
The utility model relates to an improved structure of a hydraulic system of a loader, which comprises a steering hydraulic circulation loop and a working hydraulic circulation loop. The steering hydraulic circulation loop is used for driving front wheels of the loader to steer, and the working hydraulic circulation loop is used for driving a working device of the loader. The improved structure of the hydraulic system of the loader is characterized in that an output end of a priority valve is communicated with an output end of a working gear pump via a one-way valve, a steering gear pump and the working gear pump are medium and high pressure-resistant-level hydraulic gear pumps with pressure of 20MPa at least so as to increase work pressure of the hydraulic system, the diameter of a movable arm cylinder is reduced to 130mm to 145mm, the diameter of a rotating bucket cylinder is reduced to 100mm to 115mm, the diameter of a steering cylinder is reduced to 70mm to 85mm, and the hydraulic system is provided with a double-pump flow combination system of the priority valve, and simultaneously reduces displacement of oil pumps, thereby reducing total flow of the hydraulic system, decreasing hydraulic loss and being capable of realizing reduction of capacity of a hydraulic oil tank. The difference between the design and design with the abroad advanced level is reduced, reliability and work efficiency of the hydraulic system are increased, and cost of the hydraulic system is reduced effectively.
Description
Technical field
The utility model relates to technical field of engineering machinery, and a kind of specifically loader hydraulic system improves structure.
Background technology
5 tonnes of loaders that to have developed first hydraulic system pressure be 16MPa from 1985 are to modern, inquire about according to documents and materials, be subjected to the particularly restriction of gear oil pump withstand voltage properties and reliability of Hydraulic Elements, the metered dose hydraulic system pressure of 5 tonnes of loaders of China almost promotes again, and the hydraulic system pressure of external advanced person's corresponding type has risen to the 25MPa rank.Along with the raising of system pressure, make the ability of Hydraulic Elements transmitted power progressively increase, operating efficiency increases substantially, and under the identical condition of engine power, the efficient that old type produced can not be compared with new architecture.China's loader is compared with external mainly loader manufacturer ad eundem product, and hydraulic system pressure is also on the low side, and hydraulic system efficient is also lower.At present, main research concentrates in the application of trouble of loader diagnostic analysis and new-type element; On the research aspect the relevant raising loader hydraulic system operating pressure also rests on theory demonstration to feasibility, also there is not real specific embodiments to occur.
Summary of the invention
The purpose of this utility model is to provide a kind of loader hydraulic system to improve structure, and this hydraulic system is improved structure obviously shortens operating mechanism actuation time, has also improved the reliability of hydraulic system, helps reducing the hydraulic system cost simultaneously.
Of the present utility model being characterised in that: a kind of loader hydraulic system improves structure, comprise the working hydraulic pressure closed circuit that is used to drive the steering hydraulic closed circuit of loader front-wheel steer and is used to drive working device of loader, described steering hydraulic closed circuit comprises the tooth sector pump that input is communicated with fuel tank, with the pressure-gradient control valve that is linked in sequence with this tooth sector pump output terminal, coaxial flow amplifying and steering device, trimmer valve and turn to oil cylinder, described working hydraulic pressure closed circuit comprises the working gear pump that input is communicated with fuel tank, this working gear pump output terminal is connected with manual multiple-way valve, one of them output of described manual multiple-way valve is connected with boom cylinder, its another output is connected with rotary ink tank, it is characterized in that: an output of described pressure-gradient control valve is connected through one way valve and working gear pump output terminal, described tooth sector pump and working gear pump be pressure be not less than 20MPa in the hydraulic gear pump of high voltage withstand class, to improve the operating pressure of hydraulic system, the cylinder diameter of described boom cylinder is reduced into 130 ~ 145mm, the cylinder diameter of described rotary ink tank is reduced into 100 ~ 115mm, and the described cylinder diameter of oil cylinder that turns to is reduced into 70 ~ 85mm.
The rated discharge of above-mentioned tooth sector pump and working gear pump is 50 ~ 70ml/r.
The beneficial effects of the utility model: this hydraulic system adopts the double pump interflow system of configuration preference valve, be on the basis of 16MPa ZL50 type wheel loader, by dwindling the hydraulic cylinder cylinder diameter, improve the operating pressure of gear pump, finally make the zl50 loader hydraulic system working pressure reach 20MPa, reduce the discharge capacity of oil pump simultaneously, thereby reduce the hydraulic system total flow, reduce the hydraulic pressure loss, and can realize the hydraulic oil container volume reducing.This design has great importance, and has dwindled the gap with external advanced level, improves Hydraulic System Reliability and operating efficiency, effectively reduces the hydraulic system cost.
Description of drawings
Fig. 1 is a hydraulic system principle figure.
Fig. 2 is the correction data table of hydraulic cylinder size before and after the zl50 loader boost in pressure.
Fig. 3 is oil cylinder displacement curve figure before and after the boost in pressure.
Fig. 4 is boom cylinder oil pocket pressure time curve figure before and after the boost in pressure.
Fig. 5 is rotary ink tank oil pocket pressure time curve figure before and after the boost in pressure.
Fig. 6 rises to 20MPa performance test contrast table for ZL50 type loader hydraulic system from 16MPa.
Fig. 7 is zl50 loader turnaround time mensuration table.
Among Fig. 1: 1. fuel tank 2. oil filters 3. tooth sector pumps 4. pressure-gradient control valves 5. coaxial flow amplifying and steering device 6. trimmer valves 7. turn to oil cylinder 8. one way valves 9. boom cylinders 10. rotary ink tanks 11. manual multiple-way valves 12. working gear pumps 13. radiators.
Among Fig. 4 and Fig. 5: the little cavity pressure of the big cavity pressure 2.20MPa of 1.20MPa boom cylinder boom cylinder loculus pressure 3.16MPa boom cylinder big cavity pressure 4.16MPa boom cylinder.
The specific embodiment
The utility model will be further described below in conjunction with accompanying drawing.
With reference to the accompanying drawings 1, loader hydraulic system of the present utility model improves structure, comprise the working hydraulic pressure closed circuit that is used to drive the steering hydraulic closed circuit of loader front-wheel steer and is used to drive working device of loader, described steering hydraulic closed circuit comprises the tooth sector pump 3 that input is communicated with fuel tank 1, with the pressure-gradient control valve 4 that is linked in sequence with these tooth sector pump 3 outputs, coaxial flow amplifying and steering device 5, trimmer valve 6 and turn to oil cylinder 7, described working hydraulic pressure closed circuit comprises the working gear pump 12 that input is communicated with fuel tank 1, these working gear pump 12 outputs are connected with manual multiple-way valve 11, one of them output of described manual multiple-way valve 11 is connected with boom cylinder 9, its another output is connected with rotary ink tank 10, it is characterized in that: an output of described pressure-gradient control valve 4 is connected through one way valve 8 and working gear pump 12 outputs, described tooth sector pump 3 and working gear pump 12 for pressure be not less than 20MPa in the hydraulic gear pump of high voltage withstand class, to improve the operating pressure of hydraulic system, the cylinder diameter of described boom cylinder 9 is reduced into 130 ~ 145mm, the cylinder diameter of described rotary ink tank 10 is reduced into 100 ~ 115mm, and the described cylinder diameter of oil cylinder 7 that turns to is reduced into 70 ~ 85mm.
The rated discharge of above-mentioned described tooth sector pump 3 and working gear pump 12 is 50 ~ 70ml/r.
Embodiment is as follows more specifically:
What this hydraulic system adopted is the double pump interflow system of configuration preference valve, and referring to accompanying drawing 1, tooth sector pump 3 guarantees preferentially that by pressure-gradient control valve 4 controls the steering hydraulic closed circuit is with oily; Under the situation that the steering hydraulic closed circuit is failure to actuate, the pressure oil of tooth sector pump is through pressure-gradient control valve and working hydraulic pressure closed circuit interflow, and working solution press pump and tooth sector pump are all bearing same pressure.When the pressure of working hydraulic pressure closed circuit reaches opening pressure of safety valve, this moment two operating pressures that hydraulic pump all will bear 20MPa.
5 tonnes of loaders of 20MPa of exploitation are to improve acquisition on system pressure is the basis of 5 tonnes of loaders of 16MPa, by adopting pressure to be not less than the hydraulic gear pump of high voltage withstand class among the 20MPa, with the operating pressure that improves hydraulic system, dwindle the hydraulic cylinder cylinder diameter and reduce oil pump capacity and realize.Improve pressure and power remains unchanged substantially or improve little, flow just can obviously reduce so, this moment element discharge capacity or latus rectum is just optional must be less.Table 1 is the correction data for hydraulic cylinder size before and after the zl50 loader boost in pressure.
The utility model can improve Hydraulic System Reliability and operating efficiency, reduces the hydraulic system cost, has dwindled the gap with external advanced level, is significant.
The utility model does not limit to above-mentioned preferred forms, and anyone can draw other various forms of engineening goods under enlightenment of the present utility model.All equalizations of being done according to the utility model claim change and modify, and all should belong to covering scope of the present utility model.
Result of study is analyzed and experimental verification
It is as follows to obtain a result by theory analysis:
Fig. 3 is an oil cylinder displacement curve comparison diagram before and after the boost in pressure, wherein 16MPaXG951 III type wheel loader operating mechanism run duration is identical actuation time with 20MPaXG951 III type wheel loader operating mechanism, can visually see in identical run duration, the displacement of the operating mechanism of 16MPaXG951 III type wheel loader compare with 20MPaXG951 III type wheel loader obviously little many.
From Fig. 4 and Fig. 5 as can be seen because the suffered active force of oil cylinder is identical, and make 20MPaXG951 III type wheel loader oil cylinder working-pressure apparently higher than 16MPaXG951 III type wheel loader oil cylinder working-pressure because boost in pressure front and back cylinder diameter dwindles, and each the oil pocket pressure history trend before and after the boost in pressure conform to.
Reduced pressure promotes fore and aft stowage machine performance curve, and after the demonstration boost in pressure, operating mechanism obviously shortens actuation time, and cylinder force is constant, and oil pocket pressure is higher than the oil pocket pressure before the boost in pressure.
By 1000 hours examination of overall test and working site experiment, draw the performance comparison that hydraulic system pressure promotes front and back, see Fig. 6 and shown in Figure 7 in detail.
Claims (1)
1. a loader hydraulic system improves structure, comprise the working hydraulic pressure closed circuit that is used to drive the steering hydraulic closed circuit of loader front-wheel steer and is used to drive working device of loader, described steering hydraulic closed circuit comprises the tooth sector pump that input is communicated with fuel tank, with the pressure-gradient control valve that is linked in sequence with this tooth sector pump output terminal, coaxial flow amplifying and steering device, trimmer valve and turn to oil cylinder, described working hydraulic pressure closed circuit comprises the working gear pump that input is communicated with fuel tank, this working gear pump output terminal is connected with manual multiple-way valve, one of them output of described manual multiple-way valve is connected with boom cylinder, its another output is connected with rotary ink tank, it is characterized in that: an output of described pressure-gradient control valve is connected through one way valve and working gear pump output terminal, described tooth sector pump and working gear pump be pressure be not less than 20MPa in the hydraulic gear pump of high voltage withstand class, to improve the operating pressure of hydraulic system, the cylinder diameter of described boom cylinder is reduced into 130 ~ 145mm, the cylinder diameter of described rotary ink tank is reduced into 100 ~ 115mm, and the described cylinder diameter of oil cylinder that turns to is reduced into 70 ~ 85mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010205630688U CN201891142U (en) | 2010-10-16 | 2010-10-16 | Improved structure of hydraulic system of loader |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010205630688U CN201891142U (en) | 2010-10-16 | 2010-10-16 | Improved structure of hydraulic system of loader |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201891142U true CN201891142U (en) | 2011-07-06 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010205630688U Expired - Fee Related CN201891142U (en) | 2010-10-16 | 2010-10-16 | Improved structure of hydraulic system of loader |
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| Country | Link |
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| CN (1) | CN201891142U (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2013033884A1 (en) * | 2011-09-05 | 2013-03-14 | 长沙中联重工科技发展股份有限公司 | Concrete pumping equipment and hydraulic system thereof |
| CN103388598A (en) * | 2013-08-06 | 2013-11-13 | 中联重科股份有限公司 | Lazy arm telescopic mechanism and hydraulic control system, hydraulic control method and crane thereof |
| CN104728199A (en) * | 2013-12-18 | 2015-06-24 | 北汽福田汽车股份有限公司 | Multi-way valve, multi-way valve system and engineering machinery |
| CN105937511A (en) * | 2016-06-22 | 2016-09-14 | 河南瑞创通用机械制造有限公司 | Hydraulic system assembly and tractor |
-
2010
- 2010-10-16 CN CN2010205630688U patent/CN201891142U/en not_active Expired - Fee Related
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2013033884A1 (en) * | 2011-09-05 | 2013-03-14 | 长沙中联重工科技发展股份有限公司 | Concrete pumping equipment and hydraulic system thereof |
| CN103388598A (en) * | 2013-08-06 | 2013-11-13 | 中联重科股份有限公司 | Lazy arm telescopic mechanism and hydraulic control system, hydraulic control method and crane thereof |
| CN104728199A (en) * | 2013-12-18 | 2015-06-24 | 北汽福田汽车股份有限公司 | Multi-way valve, multi-way valve system and engineering machinery |
| CN105937511A (en) * | 2016-06-22 | 2016-09-14 | 河南瑞创通用机械制造有限公司 | Hydraulic system assembly and tractor |
| CN105937511B (en) * | 2016-06-22 | 2019-02-19 | 河南瑞创通用机械制造有限公司 | Hydraulic system assembly and tractor |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| 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: 20110706 Termination date: 20181016 |