CN201437601U - Loading machine quantitative hydraulic load sensing device - Google Patents
Loading machine quantitative hydraulic load sensing device Download PDFInfo
- Publication number
- CN201437601U CN201437601U CN2009203021485U CN200920302148U CN201437601U CN 201437601 U CN201437601 U CN 201437601U CN 2009203021485 U CN2009203021485 U CN 2009203021485U CN 200920302148 U CN200920302148 U CN 200920302148U CN 201437601 U CN201437601 U CN 201437601U
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- way pressure
- pressure compensator
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Abstract
The utility model discloses a loading machine quantitative hydraulic load sensing device. The device is characterized in that the device is provided with a three-way pressure compensator and a two-way pressure compensator, wherein, an Ls port of the three-way pressure compensator is communicated with the Ls port of the two-way pressure compensator; and the oil inlet end of the two-way pressure compensator is communicated with the E end of a reversing valve, and the oil outlet end thereof is communicated with the F end of the reversing valve. The device has the advantages that the device adopts the loading feedback and the loading sensing device with dosing pump oil supply and a closing bit loading sensing valve, the system only provides the required flow rate to a performing element, and the superfluous flow rate inflows an overfall oil sump tank opened by the required pressure of the actual load overcome by the system through the three-way pressure compensator, so that the loss of pressure produced by the system is lower, the heat generation of the system is lower, and the energy-saving effect of the loading machine hydraulic system is evidently increased.
Description
Technical field
The utility model relates to a kind of quantitative hydraulic pressure load sensing of loader device that is used for loader hydraulic system.
Background technology
At present, the hydraulic system that loader usually adopts is out that all the meta multiple directional control valve controls each action, sees Fig. 2.Be characterized in: realized actions such as loading arm lifting, scraper bowl revolution,, can not realize the coordination of composite move because each loop connection in series-parallel can only be operated individual part; And determine by overcoming the required pressure of maximum load because of system pressure this moment, hour can cause main safety valve to open in banked direction control valves valve rod aperture efficiency and overflow back fuel tank by rated pressure, it is bigger that system produces the pressure loss, causes system's heating and cause energy loss.
The utility model content
The purpose of this utility model just provides a kind of load sensing device that adopts the constant displacement pump fuel feeding, closes the meta load-sensing valve, system only offers the required flow of executive component, unnecessary flow overcomes the required pressure of actual loading by the three-way pressure compensating device by system and opens and overflow back fuel tank, system's generation pressure loss is smaller, system's heating is just smaller, has strengthened the quantitative hydraulic pressure load sensing of the loader device of the energy-saving effect of loader hydraulic system very significantly.
Solution of the present utility model is such: have three-way pressure compensating device and two logical pressure compensators, wherein the Ls mouth of three-way pressure compensating device is communicated with the Ls1 mouth of two logical pressure compensators; The oil inlet end of two logical pressure compensators is communicated with the E of reversal valve end, oil outlet end D is communicated with the F end of reversal valve.
Form the operation valves when a plurality of operating units, when operating a plurality of valve rods and carrying out composite move, system sets by overcoming that required pressure of maximum load (being Ls) by the shuttle valve network pressure (Ls1, Ls2, Ls3) of each valve rod relatively.If certain executive component load is little, that two logical pressure compensator 2 will turn down opening this moment, make that the flow that enters into the little executive component of load is few; And the big executive component of load is big because of the opening of two logical pressure compensators 2, makes that the flow that enters is more relatively, can realize the harmony of moving when carrying out composite move like this, and the maximum load that system's oil pressure relief is subjected to along with executive component changes and changes.When closing each valve rod of meta fixed quantitative load sensor-based system and all be in the meta state, Ls signal oil circuit is let out oil sump tank by flow speed control valve, and three-way pressure compensating device low pressure off-load this moment P pipeline oil circuit has guaranteed the energy-saving effect when fixed quantitative load sensing banked direction control valves is in meta.
The utility model has the advantages that and adopt the load feedback, system only offers the required flow of executive component, it is little relatively less because of the opening of two logical pressure compensators to enter into the little executive component of load, and it is more greatly relatively because of the opening of two logical pressure compensators to enter into the big executive component of load, can realize the harmony of moving when carrying out composite move; The maximum load that system's oil pressure relief is subjected to along with executive component changes and changes, and has strengthened loader hydraulic system ground energy-saving effect very significantly; When closing each valve rod of meta fixed quantitative load sensor-based system and all be in the meta state, Ls signal oil circuit is let out oil sump tank by the flow speed control valve in the three-way pressure compensating device, three-way pressure compensating device low pressure off-load this moment P pipeline oil circuit has guaranteed the energy-saving effect when fixed quantitative load sensing banked direction control valves is in meta.
Description of drawings
Accompanying drawing is embodiment of the present utility model.
Accompanying drawing 1 is control module structural representation of the utility model.
Accompanying drawing 2 be loader usually adopt open meta valve schematic diagram.
Accompanying drawing 3 is the utility model complete structure schematic diagrames when being used for loader.
The specific embodiment
A control module of the present utility model has three-way pressure compensating device 3 and two logical pressure compensators 2 as shown in Figure 1 in accompanying drawing 1, wherein the Ls mouth of three-way pressure compensating device 3 is communicated with the Ls1 mouth of two logical pressure compensators 2; The oil inlet end C of two logical pressure compensators 2 is communicated with the E of reversal valve 1 end, oil outlet end D is communicated with the F end of reversal valve 1.
Two operating positions of described reversal valve 1 have the passage of band choke valve, and the oil-in of this passage is communicated with pressure oil circuit P, and oil-out is communicated with two logical pressure compensators 2.
Described reversal valve 1 is when two operating positions, and pressure oil circuit P end all is communicated with the E end.
Accompanying drawing 3 is a plurality of operating units structural representations when forming the complete operation valve, be parallel with three control modules at pressure oil circuit P end, control the work of swing arm lifting, scraper bowl revolution, auxiliary three executive components respectively, two logical pressure compensators 22 are for controlling the operating unit that swing arm promotes.
Be elaborated with regard to 3 pairs of courses of work of the present utility model of accompanying drawing now:
The course of work has following several:
1. when banked direction control valves reversal valve 1 is failure to actuate, the zero load feedback signal of Ls oil circuit, Ls signal oil circuit is let out oil sump tank by the very little flow speed control valve of flow, overflow valve in the three-way pressure compensating device 3 is opened with minimum pressure, plays the off-load effect, and this moment, the oil of gear pump flowed back to fuel tank from overflow valve, because of the opening pressure of overflow valve very little, so the pressure loss that causes is also very little, this moment and traditional loader adopt, and to open the meta system similar, and promptly the constant displacement pump fluid of discharging directly flows back to fuel tank.
2. when single group oil cylinder moves (is example with rotary ink tank 4), the pressure oil of gear pump is because the action of reversal valve 1 spool, be communicated with the oil inlet end C-1 oil duct of two logical pressure compensators 2, two logical pressure compensators 2 are under the effect of C-1 oil duct pressure oil, move on the spool and be in the upper state, C-1 is communicated with D-1, load feedback oil circuit Ls1-1 also offers 3 one load pressure signals of three-way pressure compensating device when pressure oil leads to rotary ink tank power is provided, the a little higher than load of overflow valve opening pressure in the three-way pressure compensating device 3 at this moment, and change in pressure along with load, remove the unsupported opening pressure that reaches safety valve, otherwise can under the rated pressure of system, not open overflow, significantly reduce the pressure loss of system.
3. when many group oil cylinders move, Ls1-1, Ls1-2, Ls1-3 has the load pressure signal D-1 of control oil channel separately on figure, D-2, D-3, but because of this three road load signal is in parallel, so when the pressure of hypothesis swing arm lift cylinder this moment 5 is maximum, be D-1, D-2, the D-3 D-2 maximum of comparing, the load signal pressure maximum of Ls1-2 so, the overflow valve opening pressure of three-way pressure compensating device is by the boom cylinder 5 loads decision of load maximum, the right of two logical pressure compensator 2-1 and two logical pressure compensator 2-3 is subjected to the signal pressure effect of Ls1-2, spool moves down, the relatively large two logical pressure compensator openings of i.e. load this moment are big relatively, and the less relatively two logical pressure compensator openings of load are relatively littler, like this when loader carries out composite move, each action can be moved simultaneously, show good coordination and flow distribution according to need property.
Claims (2)
1. the quantitative hydraulic pressure load sensing of a loader device is characterized in that having three-way pressure compensating device (3) and two logical pressure compensators (2), and wherein (Ls) of three-way pressure compensating device (3) mouth is communicated with (Ls1) mouth of two logical pressure compensators (2); The oil inlet end (C) of two logical pressure compensators (2) is communicated with (E) of reversal valve (1) end, oil outlet end (D) is communicated with (F) end of reversal valve (1).
2. the quantitative hydraulic pressure load sensing of loader according to claim 1 device, it is characterized in that two operating positions of described reversal valve (1) have the passage of band choke valve, the oil-in of this passage is communicated with pressure oil circuit (P), and oil-out is communicated with two logical pressure compensators (2).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009203021485U CN201437601U (en) | 2009-04-13 | 2009-04-13 | Loading machine quantitative hydraulic load sensing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009203021485U CN201437601U (en) | 2009-04-13 | 2009-04-13 | Loading machine quantitative hydraulic load sensing device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201437601U true CN201437601U (en) | 2010-04-14 |
Family
ID=42399577
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009203021485U Expired - Lifetime CN201437601U (en) | 2009-04-13 | 2009-04-13 | Loading machine quantitative hydraulic load sensing device |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201437601U (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102251996A (en) * | 2011-07-05 | 2011-11-23 | 天津柳工机械有限公司 | Engineering mechanical load sensing hydraulic system |
| CN103807243A (en) * | 2014-01-21 | 2014-05-21 | 广西柳工机械股份有限公司 | Electric proportional decompression cushion valve for engineering machines |
| CN104047931A (en) * | 2014-06-23 | 2014-09-17 | 柳州柳工液压件有限公司 | Three-way pressure compensator assembly |
| CN107269612A (en) * | 2016-09-13 | 2017-10-20 | 江苏恒立液压科技有限公司 | Load sensing multi-way valve system |
-
2009
- 2009-04-13 CN CN2009203021485U patent/CN201437601U/en not_active Expired - Lifetime
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102251996A (en) * | 2011-07-05 | 2011-11-23 | 天津柳工机械有限公司 | Engineering mechanical load sensing hydraulic system |
| CN103807243A (en) * | 2014-01-21 | 2014-05-21 | 广西柳工机械股份有限公司 | Electric proportional decompression cushion valve for engineering machines |
| CN104047931A (en) * | 2014-06-23 | 2014-09-17 | 柳州柳工液压件有限公司 | Three-way pressure compensator assembly |
| CN104047931B (en) * | 2014-06-23 | 2017-01-04 | 柳州柳工液压件有限公司 | Three-way pressure compensating device assembly |
| CN107269612A (en) * | 2016-09-13 | 2017-10-20 | 江苏恒立液压科技有限公司 | Load sensing multi-way valve system |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CX01 | Expiry of patent term |
Granted publication date: 20100414 |
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| CX01 | Expiry of patent term |