CN104358286B - Deciliter stream selects function pilot operated valve device and loader to determine variable delivery hydraulic system - Google Patents
Deciliter stream selects function pilot operated valve device and loader to determine variable delivery hydraulic system Download PDFInfo
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- CN104358286B CN104358286B CN201410627890.9A CN201410627890A CN104358286B CN 104358286 B CN104358286 B CN 104358286B CN 201410627890 A CN201410627890 A CN 201410627890A CN 104358286 B CN104358286 B CN 104358286B
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Abstract
The present invention relates to deciliter stream and select function pilot operated valve device, determine the energy loss of variable delivery hydraulic system for solving existing loader and turn to jitter problem, disclosure deciliter stream selects the first pilot operated valve device in function pilot operated valve device to be in during right position its oil-in through the 3rd check valve to C hydraulic fluid port one-way conduction, is in its oil-in during left position and is communicated in the oil-in of the second pilot operated valve device；Second pilot operated valve device left and right hydraulic control end connects with C hydraulic fluid port through the entrance of the first check valve through throttle orifice respectively, second pilot operated valve device is in during left position its oil-in and turns on to C hydraulic fluid port through the first check valve, be in during right position its oil-in through the first check valve to C hydraulic fluid port one-way conduction and through the second check valve to E hydraulic fluid port one-way conduction.Deciliter stream select function pilot operated valve device determine variable system can be avoided energy loss and the problem preventing from turning to shake at loader.
Description
Technical field
The present invention relates to a kind of Hydraulic Elements, particularly relate to a kind of deciliter stream and select function pilot operated valve device and loader to determine variable delivery hydraulic system.
Background technology
The load-sensitive adopted at present turns to combining hydraulic system, and used by it, converging valve is generally pressure-gradient control valve, and when hydraulic work system, pump is preferentially carried out oily supply steering hydraulic system by this pressure-gradient control valve, and unnecessary flow then collaborates in the middle of main valve oil circuit.When it is applied to coupling single argument pump and opens when determining variable delivery hydraulic system of middle position banked direction control valves, hydraulic system is under Part load, executor does not carry out action or carries out fine motion work, can cause that variable pump is in huge discharge for oil condition, unnecessary flow can pass through to hold middle position banked direction control valves and flow back to fuel tank, produces bit-loss and restriction loss in greatly；Thus, causing hydraulic system to produce very big heat, energy consumption is big.In order to solve and avoid this problem, for coupling variable pump and open middle position banked direction control valves determine variable delivery hydraulic system, whether presently, there are works the load hydraulic control mouth of normal precedence valve according to hydraulic system of working is at cut-off state, but consequently leads to steering hydraulic system instability of flow and turn to jitter problem.
Summary of the invention
Present invention aims to existing pressure-gradient control valve to realize common preferential oil supply function and cause the energy loss determining variable delivery hydraulic system and turn to jitter problem and provide a kind of and possess deciliter pilot operated valve device of stream selectable punction and there is the loader of this pilot operated valve device determine variable delivery hydraulic system.
The present invention is that the technical scheme realizing its purpose is such that a kind of deciliter stream selection function pilot operated valve device of structure, it includes the first pilot operated valve device, second pilot operated valve device, first check valve, second check valve and the 3rd check valve, first segment discharge orifice, second section discharge orifice, 3rd throttle orifice and P hydraulic fluid port, b hydraulic fluid port, T hydraulic fluid port, a hydraulic fluid port, C hydraulic fluid port, E hydraulic fluid port, P hydraulic fluid port is communicated in the oil-in of the first pilot operated valve device, b hydraulic fluid port and T hydraulic fluid port are respectively communicated with the left and right hydraulic control end in the first pilot operated valve device, first pilot operated valve device is in during right position its oil-in through the 3rd check valve to C hydraulic fluid port one-way conduction, first pilot operated valve device is in its oil-in during left position and is communicated in the oil-in of the second pilot operated valve device；A hydraulic fluid port is communicated in the left hydraulic control end of the second pilot operated valve device through first segment discharge orifice, the left hydraulic control end of the second pilot operated valve device is communicated in the entrance of the first check valve through second section discharge orifice, right hydraulic control end through the 3rd throttle orifice, the outlet of the first check valve is in C hydraulic fluid port, second pilot operated valve device is in during left position its oil-in and turns on to C hydraulic fluid port through the first check valve, the second pilot operated valve device be in during right position its oil-in through the first check valve to C hydraulic fluid port one-way conduction and through the second check valve to E hydraulic fluid port one-way conduction.Above-mentioned deciliter stream selects the right hydraulic control end of the first pilot operated valve device in function pilot operated valve device to be spring cavity, and the T hydraulic fluid port connected with this spring cavity is oil return opening.The left hydraulic control end of the second pilot operated valve device is spring cavity.
The present invention realizes another technical scheme of its purpose to be such that constructing a kind of loader and determine variable delivery hydraulic system, including variable pump, steering gear, flux amplification valve, banked direction control valves, additionally include aforesaid deciliter stream and select function pilot operated valve device, deciliter stream selects a hydraulic fluid port of function pilot operated valve device to be communicated in the LS feedback port of steering gear, what C hydraulic fluid port was communicated in flux amplification valve turns to oil-in, E hydraulic fluid port is communicated in the working oil entrance of banked direction control valves, P hydraulic fluid port is communicated in the oil-out of variable pump, and b hydraulic fluid port is communicated in the pilot pressure oil circuit of banked direction control valves.Determine in variable delivery hydraulic system at loader of the present invention: dosing pump is by banked direction control valves to the boom cylinder of loader, rotary ink tank fuel feeding, and banked direction control valves is controlled by pilot valve.
When the equal attonity of the pilot valve of steering gear and banked direction control valves, owing to deciliter stream selects the fuel-displaced C hydraulic fluid port of function pilot operated valve device and fuel-displaced E hydraulic fluid port to be all cut off, the load-sensitive mouth no signal of variable pump, variable pump is fuel feeding not, it is to avoid banked direction control valves opens the energy loss that middle position is caused.
When steering gear single movement, owing to the leading role of steering gear makes the valve port of flux amplification valve open, steering gear load-sensitive LS mouth pressure signal is transferred to the load-sensitive mouth of variable pump and the hydraulic control a hydraulic fluid port of pilot operated valve device simultaneously；Now, selecting function pilot operated valve device for deciliter stream, variable pump carrys out the oily oil-in being directly entered flux amplification valve by the first pilot operated valve device and the 3rd check valve, and deciliter stream selects the E hydraulic fluid port of function pilot operated valve device not have fluid to pass through；Variable pump is only according to carrying out fuel feeding needed for steering load, it is to avoid there is excess traffic and opens middle position oil sump tank by banked direction control valves, decreases energy loss；Deciliter stream selects the hydraulic control a hydraulic fluid port of function pilot operated valve device to be connected with load signal simultaneously, the valve precompensation function of second pilot operated valve device is completely eliminated, avoiding deciliter stream selects the hydraulic control a hydraulic fluid port of function pilot operated valve device by causing turning to oil circuit to be subject to the effect of jitter of the second pilot operated valve device when ending and cause turn to jitter problem, keeps the stationarity turned to.
When the pilot valve single movement of banked direction control valves, hydraulic system of working load signal connects with variable pump, owing to the effect of the b hydraulic fluid port pressure of the first pilot operated valve device makes the valve rod action of the first pilot operated valve device be in left position, second pilot operated valve device does not have pressure oil effect to be in right position due to its hydraulic control end a hydraulic fluid port, but lead to the C hydraulic fluid port cut-off of flux amplification valve, variable pump carrys out the oily working oil entrance feeding to banked direction control valves all through fuel-displaced E hydraulic fluid port, it is achieved the interflow of work branch.
When the pilot valve of steering gear and banked direction control valves all has action, variable pump comes that oily elder generation is on-demand is supplied to flux amplification valve and steering cylinder, simultaneously according to turning to the contrast situation with live load signal, on-demand carry out fuel feeding by fuel-displaced E hydraulic fluid port to banked direction control valves, avoid excess traffic loss in work and steering procedure, and ensure that steering load signal connects with the hydraulic control a hydraulic fluid port of pilot operated valve device all the time, keep the stationarity turned to.When variable pump 2 reaches the cut-out pressure set, variable pump 2 keeps high-pressure low-flow fuel feeding, decreases energy loss.
The present invention compared with prior art, the function of the present invention and advantage:
When a, loader attonity so that steering pump is in low-pressure low flow state, hardly fuel feeding, save energy consumption；
In b, independent steering procedure, steering pump, according to the on-demand fuel feeding of steering load, reduces restriction loss and middle bit-loss；
C, working independently in process, steering pump can realize the interflow function of steering pump fluid according to work pilot control；
D, when working and turn to simultaneously action, steering pump digs up the roots according to the on-demand fuel feeding of steering hydraulic system demand, and unnecessary flow is supplied to hydraulic system of working；
E, when steering hydraulic system pressure or hydraulic system of working pressure reach the cut-out pressure of steering pump, it is achieved Isobarically Control；
F, realizing on the basis determine variable delivery hydraulic system, recovering the function that tradition load sensitive sensor turns to, solution turns to jitter problem；
G, solve engine idle hard steering or the problem turning to the number of turns too much.
Accompanying drawing explanation
Fig. 1 is that the present invention deciliter stream selects function pilot operated valve device hydraulic principle schematic diagram；
Fig. 2 is the hydraulic principle schematic diagram that loader of the present invention determines knuckle section in variable delivery hydraulic system.
In figure: fuel tank 1, variable pump 2, deciliter stream select function pilot operated valve device the 3, first pilot operated valve device the 31, second pilot operated valve device the 32, first check valve the 35, second check valve 37 and the 3rd check valve 38, first segment discharge orifice 33, second section discharge orifice the 34, the 3rd throttle orifice 36, shuttle valve 4, steering gear 5, flux amplification valve 6, steering cylinder 7.
Detailed description of the invention
Below in conjunction with accompanying drawing, specific embodiments is described.
One deciliter stream as shown in Figure 1 selects function pilot operated valve device 3, first pilot operated valve device the 31, second pilot operated valve device the 32, first check valve the 35, second check valve the 37, the 3rd check valve 38, first segment discharge orifice 33, second section discharge orifice the 34, the 3rd throttle orifice 36 and P hydraulic fluid port, b hydraulic fluid port, T hydraulic fluid port, a hydraulic fluid port, C hydraulic fluid port, E hydraulic fluid port is included including it, P hydraulic fluid port is communicated in the oil-in of the first pilot operated valve device 31, b hydraulic fluid port and T hydraulic fluid port are respectively communicated with the left and right hydraulic control end in the first pilot operated valve device 31, the right hydraulic control end of the first pilot operated valve device 31 is spring cavity, and the T hydraulic fluid port connected with this spring cavity is oil return opening.The left hydraulic control end of the second pilot operated valve device 32 is spring cavity, and this chamber connects with a hydraulic fluid port.
First pilot operated valve device 31 is in during right position that its oil-in is through the 3rd check valve 38 to C hydraulic fluid port one-way conduction, and the first pilot operated valve device 31 is in its oil-in during left position and is communicated in the oil-in of the second pilot operated valve device 32；A hydraulic fluid port is communicated in the left hydraulic control end of the second pilot operated valve device 32 through first segment discharge orifice 33, the left hydraulic control end of the second pilot operated valve device 32 is communicated in the entrance of the first check valve 35 through second section discharge orifice 34, right hydraulic control end through the 3rd throttle orifice 36, the outlet of the first check valve 35 is in C hydraulic fluid port, second pilot operated valve device 32 is in during left position its oil-in through the first check valve 35 to C hydraulic fluid port one-way conduction, the second pilot operated valve device 32 be in during right position its oil-in through the first check valve 35 to C hydraulic fluid port one-way conduction and through the second check valve 37 to E hydraulic fluid port one-way conduction.
Loader determines the knuckle section in variable delivery hydraulic system as shown in Figure 2.Loader shown in Fig. 2 is determined the knuckle section in variable delivery hydraulic system and is included fuel tank 1, variable pump 2, steering gear 5, flux amplification valve 6, steering cylinder 7, shuttle valve 4 and above-mentioned deciliter stream selection function pilot operated valve device 3.Steering gear 5 introduces the pressure oil pilot pressure oil sources as steering gear 5 from flux amplification valve 6, and control output end is communicated in the corresponding hydraulic fluid port of flux amplification valve 6 thus controlling the relevant action of steering cylinder 7.Deciliter stream selects a hydraulic fluid port of function pilot operated valve device 3 to be communicated in the LS feedback port of steering gear 5, what C hydraulic fluid port was communicated in flux amplification valve 6 turns to oil-in, E hydraulic fluid port is communicated in the working oil entrance of banked direction control valves, and P hydraulic fluid port is communicated in the oil-out of variable pump 2, and b hydraulic fluid port is communicated in banked direction control valves pilot control oil circuit.The LS feedback port of steering gear 5 is communicated in an entrance of shuttle valve 4, and the outlet of shuttle valve 4 is in the load-sensitive mouth of variable pump 2.In Fig. 2, loader is determined unshowned working hydraulic pressure part in variable delivery hydraulic system and is included dosing pump, banked direction control valves, rotary ink tank and boom cylinder, pilot valve etc., dosing pump by banked direction control valves to the boom cylinder of loader, rotary ink tank fuel feeding, banked direction control valves is controlled by pilot valve, and the load feedback oil communication of banked direction control valves is in the another one entrance of shuttle valve 4.
In the present embodiment, when the equal attonity of the pilot valve of steering gear 5 and banked direction control valves, owing to deciliter stream selects the fuel-displaced C hydraulic fluid port of function pilot operated valve device 3 and fuel-displaced E hydraulic fluid port to be all cut off, the load-sensitive mouth no signal of variable pump 2, variable pump 2 not fuel feeding, it is to avoid banked direction control valves opens the energy loss that middle position is caused.
When steering gear 5 single movement, owing to the leading role of steering gear 5 makes the valve port of flux amplification valve 6 open, steering gear 5 load-sensitive LS mouth pressure signal is transferred to the load-sensitive mouth of variable pump 2 and a hydraulic fluid port of deciliter stream selection function pilot operated valve device 3 simultaneously, now, function pilot operated valve device 3 is selected for deciliter stream, the second pilot operated valve device 32 is made to be in left position, first pilot operated valve device 31 is in right position, the oily oil-in being directly entered flux amplification valve 6 by the first pilot operated valve device 31 and the 3rd check valve 38 through C hydraulic fluid port of variable pump 2, deciliter stream select function pilot operated valve device 3 E hydraulic fluid port do not have fluid to pass through；Variable pump 2 is only according to carrying out fuel feeding needed for steering load, it is to avoid there is excess traffic and opens middle position oil sump tank by banked direction control valves, decreases energy loss；Deciliter stream selects the hydraulic control a hydraulic fluid port of function pilot operated valve device 3 to be connected with load signal simultaneously, the valve precompensation function of second pilot operated valve device 32 is completely eliminated, avoiding deciliter stream selects the hydraulic control a hydraulic fluid port of function pilot operated valve device 3 by causing turning to oil circuit to be subject to the effect of jitter of the second control valve when ending and cause turn to jitter problem, keeps the stationarity turned to.
When the pilot valve single movement of banked direction control valves, hydraulic system of working load signal connects with variable pump, owing to the effect of the b hydraulic fluid port pressure of the first pilot operated valve device 31 makes the valve rod action of the first control valve 31 be in left position, second pilot operated valve device 32 does not have pressure oil effect to be in right position due to its hydraulic control end a hydraulic fluid port, but lead to the C hydraulic fluid port cut-off of flux amplification valve, the oily working oil entrance feeding to banked direction control valves all through fuel-displaced E hydraulic fluid port of variable pump 2, it is achieved the interflow of work branch.
When the pilot valve of steering gear 5 and banked direction control valves all has action, variable pump comes that oily elder generation is on-demand is supplied to flux amplification valve and steering cylinder, simultaneously according to turning to the contrast situation with live load signal, on-demand carry out fuel feeding by fuel-displaced E hydraulic fluid port to banked direction control valves, avoid excess traffic loss in work and steering procedure, and ensure that steering load signal connects with the hydraulic control a hydraulic fluid port of pilot operated valve device all the time, keep the stationarity turned to.When variable pump 2 reaches the cut-out pressure set, variable pump 2 keeps high-pressure low-flow fuel feeding, decreases energy loss.
Claims (4)
1. one kind of deciliter stream selects function pilot operated valve device, it is characterized in that including the first pilot operated valve device (31), second pilot operated valve device (32), first check valve (35), second check valve (37) and the 3rd check valve (38), first segment discharge orifice (33), second section discharge orifice (34), 3rd throttle orifice (36) and P hydraulic fluid port, b hydraulic fluid port, T hydraulic fluid port, a hydraulic fluid port, C hydraulic fluid port, E hydraulic fluid port, described P hydraulic fluid port is communicated in the oil-in of described first pilot operated valve device, described b hydraulic fluid port and T hydraulic fluid port are respectively communicated with the left and right hydraulic control end in described first pilot operated valve device, described first pilot operated valve device is in during right position its oil-in through the 3rd check valve to C hydraulic fluid port one-way conduction, described first pilot operated valve device is in its oil-in during left position and is communicated in the oil-in of described second pilot operated valve device；Described a hydraulic fluid port is communicated in the left hydraulic control end of described second pilot operated valve device through first segment discharge orifice, the left hydraulic control end of described second pilot operated valve device is communicated in the entrance of described first check valve through second section discharge orifice, right hydraulic control end through the 3rd throttle orifice, the outlet of described first check valve is in described C hydraulic fluid port, described second pilot operated valve device is in during left position its oil-in and turns on to C hydraulic fluid port through the first check valve, described second pilot operated valve device be in during right position its oil-in through the first check valve to C hydraulic fluid port one-way conduction and through the second check valve to E hydraulic fluid port one-way conduction.
2. according to claim 1 deciliter stream selects function pilot operated valve device, it is characterised in that the right hydraulic control end of described first pilot operated valve device is spring cavity, and the T hydraulic fluid port connected with this spring cavity is oil return opening.
3. according to claim 1 deciliter stream selects function pilot operated valve device, it is characterised in that the left hydraulic control end of described second pilot operated valve device is spring cavity.
4. a loader determines variable delivery hydraulic system, including variable pump (2), steering gear (5), flux amplification valve (6), banked direction control valves, characterized by further comprising deciliter stream according to any one of claims 1 to 3 and select function pilot operated valve device, the LS feedback port that described deciliter stream selects a hydraulic fluid port of function pilot operated valve device to be communicated in described steering gear, C hydraulic fluid port is communicated in the oil-in of described flux amplification valve, E hydraulic fluid port is communicated in the working oil entrance of described banked direction control valves, P hydraulic fluid port is communicated in the oil-out of described variable pump, and b hydraulic fluid port is communicated in the pilot pressure oil circuit control of banked direction control valves.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201410627890.9A CN104358286B (en) | 2014-11-10 | 2014-11-10 | Deciliter stream selects function pilot operated valve device and loader to determine variable delivery hydraulic system |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201410627890.9A CN104358286B (en) | 2014-11-10 | 2014-11-10 | Deciliter stream selects function pilot operated valve device and loader to determine variable delivery hydraulic system |
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| CN104358286A CN104358286A (en) | 2015-02-18 |
| CN104358286B true CN104358286B (en) | 2016-06-29 |
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| CN104929183B (en) * | 2015-05-21 | 2017-03-15 | 徐工集团工程机械股份有限公司科技分公司 | A kind of loader turned to based on Flow amplification determines variable delivery hydraulic system |
| CN105134678A (en) * | 2015-08-26 | 2015-12-09 | 徐工集团工程机械股份有限公司科技分公司 | Pilot control valve block, core opening and closing hydraulic system and engineering machine |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
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| DE10104298A1 (en) * | 2000-05-11 | 2001-11-15 | Mannesmann Rexroth Ag | Hydraulic control device for damping travel vibrations of mobile work apparatus involves hydro-cylinder supporting work tool, cylinder chambers of which are connectable via control valve arrangement with pressure medium source or tank |
| CN201301466Y (en) * | 2008-11-13 | 2009-09-02 | 贵州詹阳动力重工有限公司 | Rotary oil supply loop for hydraulic excavator |
| CN102296664A (en) * | 2011-06-23 | 2011-12-28 | 徐州徐工挖掘机械有限公司 | Hydraulic driving device of excavator |
| CN102912823A (en) * | 2012-11-09 | 2013-02-06 | 浙江大学 | Rotary energy saving system of excavator |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2003106305A (en) * | 2001-09-28 | 2003-04-09 | Kobelco Contstruction Machinery Ltd | Gyrating control circuit |
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Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10104298A1 (en) * | 2000-05-11 | 2001-11-15 | Mannesmann Rexroth Ag | Hydraulic control device for damping travel vibrations of mobile work apparatus involves hydro-cylinder supporting work tool, cylinder chambers of which are connectable via control valve arrangement with pressure medium source or tank |
| CN201301466Y (en) * | 2008-11-13 | 2009-09-02 | 贵州詹阳动力重工有限公司 | Rotary oil supply loop for hydraulic excavator |
| CN102296664A (en) * | 2011-06-23 | 2011-12-28 | 徐州徐工挖掘机械有限公司 | Hydraulic driving device of excavator |
| CN102912823A (en) * | 2012-11-09 | 2013-02-06 | 浙江大学 | Rotary energy saving system of excavator |
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