CN204491707U - Loader semi-variety hydraulic system - Google Patents
Loader semi-variety hydraulic system Download PDFInfo
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- CN204491707U CN204491707U CN201420801695.9U CN201420801695U CN204491707U CN 204491707 U CN204491707 U CN 204491707U CN 201420801695 U CN201420801695 U CN 201420801695U CN 204491707 U CN204491707 U CN 204491707U
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Abstract
The utility model relates to a kind of loader hydraulic system, plunger displacement pump is turned to connect steering cylinder by switching valve block, steering gear, switching valve block connects distributing valve, when turning to plunger displacement pump to provide flow needed for the steering cylinder of steering by switching valve block, steering gear, the pressure flow without unnecessary steering load in the middle bit port of distributing valve flows back to fuel tank; Switching valve block connect pilot valve, for loader swing arm decline or float decline or loader be in driving cycle time, make to turn to plunger displacement pump to export without flow; Working barrel connects distributing valve by unloader, and distributing valve connects rotary ink tank and boom cylinder, and when system enters high-pressure low-flow state, the flow that working barrel exports gets back to fuel tank by unloader with low pressure, turns to plunger displacement pump to provide flow needed for system.The utility model solves the larger power loss of existing quantitative system loader, the problem that entire variable system manufacturing cost is higher.
Description
Technical field
The utility model relates to a kind of loader that also can dig operation for shoveling the bulk materials such as dress soil, sandstone, coal to the slight shovel of the work such as ore, pan soil, especially a kind of hydraulic system of loader.
Background technology
Loader is a kind of cubic metre of earth and stone scraper engineering machinery being widely used in the construction projects such as highway, railway, building, water power, harbour, mine, is mainly used in the bulk materials such as shovel dress soil, sandstone, coal and also can does slightly to shovel to dig operation to ore, pan soil etc.In operation process, complete machine needs left and right turn, and equipment needs to receive bucket, lifting, discharging, decline frequently, and above action is all controlled by loader hydraulic system and realizes.
Loader hydraulic system is made up of steering hydraulic system and hydraulic system of working system.In addition according to the configuration of different complete machines, hydraulic braking system and fan motor cooling system is also furnished with.At present, loader hydraulic system great majority are quantitative system.Loader is in operation process, engine operation is in idling and most high-speed range, in order to ensure motor when idling, turn to not heavy, steering pump generally chooses comparatively huge discharge, when high engine speeds wait a moment beat steering wheel time, the flow of steering demand is less, the a large amount of hydraulic oil turning to constant displacement pump to export overflows to fuel tank with the pressure of steering load by the EF mouth of pressure-gradient control valve, causes a large amount of power losses.
When loader is in spading operating mode, equipment needs to overcome extraneous resistance, it is very slow that boom cylinder stretches out speed, now hydraulic system of working is in high-pressure low-flow state, a large amount of hydraulic oil that work constant displacement pump exports overflows to fuel tank by the main safety valve of distributing valve, causes a large amount of power losses.
Moreover loader is in haulagman without when turning to, and the flow turning to constant displacement pump to export needs the spring overcoming pressure-gradient control valve could flow out from EF mouth, and this makes to turn to pumping hole to have certain back pressure, causes certain power loss.
When loader is in decline operating mode, under the effect that scraper bowl and material are conducted oneself with dignity, swing arm can not decline under oil condition at steering pump.Because steering pump is constant displacement pump, steering pump can only fuel feeding, causes certain power loss.
Overcome the above problems, entire variable hydraulic load sensory system can be adopted, the flow required for system is provided, for system provides best flow matches, the spill losses of elimination system, but entire variable hydraulic system manufacturing cost is too high, at present cannot high volume applications.
Summary of the invention
There is power loss to overcome existing loader hydraulic system, use entire variable hydraulic system can bring the technical problem that manufacturing cost is higher again, the utility model provides a kind of loader semi-variety hydraulic system.
The utility model realizes by the following technical solutions: a kind of loader hydraulic system, comprise hydraulic oil container, turn to plunger displacement pump, working barrel, unloader, accumulator, switching valve block, steering gear, steering cylinder, distributing valve, rotary ink tank, boom cylinder, pilot valve, the described plunger displacement pump that turns to is by switching valve block, steering gear connects steering cylinder, described switching valve block also connects distributing valve, when turning to plunger displacement pump by switching valve block, needed for the steering cylinder that steering gear provides steering during flow, without the pressure current oil sump tank of unnecessary steering load in the middle bit port of distributing valve, described switching valve block also connects pilot valve, for loader swing arm decline or float decline or loader be in driving cycle time, pilot valve no signal passes to switching valve block, makes to turn to plunger displacement pump to export without flow, described working barrel connects distributing valve by unloader, and distributing valve connects rotary ink tank and boom cylinder, and when system enters high-pressure low-flow state, the flow that working barrel exports gets back to fuel tank by unloader with low pressure, turns to plunger displacement pump to provide flow needed for system.
The described outlet of plunger pump P1 that turns to is connected with the import P2 of switching valve block, the LS mouth of plunger displacement pump is turned to be connected with the LS1 mouth of switching valve block, the inlet port S1 of plunger displacement pump is turned to be connected with fuel tank with drain tap D, the E mouth of switching valve block is connected with the P mouth of distributing valve, the F mouth of switching valve block is connected with the import P3 of steering gear, the LS2 mouth of switching valve block is connected with the LS3 mouth with steering gear, the T1 mouth of switching valve block is connected with fuel tank, the XP mouth of switching valve block is connected with the P7 mouth of pilot valve, the X1 mouth of switching valve block connects guide's hydraulic fluid port xa1 of distributing valve and the A mouth of pilot valve, the X2 mouth of switching valve block connects guide's hydraulic fluid port xb1 of distributing valve and the C mouth of pilot valve, the X3 mouth of switching valve block connects guide's hydraulic fluid port xb2 of distributing valve and the B mouth of pilot valve.
The inlet port S2 of described working barrel is connected with fuel tank, work delivery side of pump P4 is connected with the oil inlet P 5 of unloader block, the oil-out P6 of unloader block is connected with the import P of distributing valve, the A1 mouth of distributing valve is connected with the rodless cavity of rotary ink tank, the B1 mouth of distributing valve is connected with the rod chamber of rotary ink tank, the A2 mouth of distributing valve is connected with the rod chamber of boom cylinder, and the B2 mouth of distributing valve is connected with the rodless cavity of boom cylinder, and the T mouth of distributing valve is connected with the T4 mouth of radiator.
The L mouth of described steering gear is connected with the L1 mouth of steering cylinder, the R mouth of steering gear is connected with the R1 mouth of steering cylinder, the T2 mouth of steering gear is connected with the T4 mouth of radiator, and the T6 mouth of pilot valve is connected with fuel tank, and the D mouth of pilot valve is connected with guide's hydraulic fluid port xb2 of distributing valve.
Described switching valve block comprises two-way pressure compensator, turn signal damping, overflow valve, pilot operated directional control valve, first shuttle valve, three-way pressure compensating device, second shuttle valve, working signal damping, decompression overflow valve, one way valve, 3rd shuttle valve, the F mouth of described switching valve block connects the P2 mouth of switching valve block by two-way pressure compensator, pilot operated directional control valve, be connected the E mouth of switching valve block with three-way pressure compensating device by two-way pressure compensator, by two-way pressure compensator, decompression overflow valve, one way valve connects the XP mouth of switching valve block, by two-way pressure compensator, overflow valve connects decompression overflow valve, pilot operated directional control valve, the T1 mouth of switching valve block, the LS2 mouth of described switching valve block connects pilot operated directional control valve, is connected two-way pressure compensator by turn signal damper, be divided into two tunnels by the second shuttle valve, and a road connects the E mouth of switching valve block, and another road connects LS1 mouth through working signal damper, described pilot operated directional control valve is through turn signal damper connecting tee pressure compensator, described pilot operated directional control valve connects guide's hydraulic fluid port X3, X2 of switching valve block through the first shuttle valve, and guide's hydraulic fluid port X2 connects guide's hydraulic fluid port X1 through the 3rd shuttle valve.
When loader only turns to, guide's hydraulic fluid port X1, X2, X3 of described switching valve block are without pressure, three-way pressure compensating device is in closed condition, the described plunger displacement pump that turns to is connected steering cylinder (9) by the two-way pressure compensator (101) controlled by spring force with the steering gear controlled by valve port opening, provides required flow to steering cylinder (9).
When steering load pressure is higher than workload pressure, described three-way pressure compensating device 106 compensates the pressure differential of steering load pressure and workload pressure; When workload pressure is higher than steering load pressure, the pressure differential of described two-way pressure compensator compensation work load pressure and steering load pressure.
Compared with prior art, the beneficial effects of the utility model are:
(1) turn to plunger displacement pump 2 large throttle spin slowly to operating mode under flow needed for steering gear 8 is provided, there is no flow by the E mouth of switching valve block 7 with bit port in the pressure overflow of steering load to distributing valve 10, saved energy.
(2) when swing arm decline and floating decline, only working barrel 3 goes out pressure, turns to plunger displacement pump 2 not output flow, has saved energy.
(3) when loader is in spading operating mode, hydraulic system of working is in high-pressure low-flow state, work constant displacement pump Low-pressure load discharge, plunger displacement pump is turned to provide flow needed for system, whole system does not have high pressure kicks to lose, and motor can give more power to transmission system, makes loader tractive force under this operating mode larger, operating efficiency is higher, more energy-conservation.
(4) after tested when doing V-shape operating mode, semi-variety system loading machine can save 10% ~ 15% than the loader of quantitative system.
Accompanying drawing explanation
Fig. 1 is the schematic diagram of semi-variety system;
Fig. 2 is the schematic diagram of switching valve block.
Detailed description of the invention
Below in conjunction with accompanying drawing and embodiment, the utility model is described in further detail.
As shown in Figure 1, a kind of loader semi-variety hydraulic system, comprise hydraulic oil container 1, turn to plunger displacement pump 2, working barrel 3, hydraulic oil are loose 4, unloader 5, accumulator 6, switching valve block 7, steering gear 8, steering cylinder 9, distributing valve 10, rotary ink tank 11, boom cylinder 12, pilot valve 13, oil return filter 14.
Plunger displacement pump 2 is turned to connect steering cylinder 9 by switching valve block 7, steering gear 8, the unloading port of described switching valve block 7 connects hydraulic oil container 1, switching valve block 7 connects distributing valve 10, when turning to plunger displacement pump 2 to provide flow needed for the steering cylinder 9 of steering by switching valve block 7, steering gear 8, without the pressure current oil sump tank of unnecessary steering load in the middle bit port of distributing valve 10, save energy.Switching valve block 7 connects pilot valve 13, the swing arm for loader decline or float decline or loader is in driving cycle time, pilot valve 13 no signal passes to switching valve block 7, makes to turn to plunger displacement pump 2 to export without flow, saves energy.Working barrel 3 connects distributing valve 10 by unloader 5, distributing valve 10 connects rotary ink tank 11 and boom cylinder 12, when system enters high-pressure low-flow state, the flow that working barrel 3 exports gets back to fuel tank by unloader 5 with low pressure, turns to plunger displacement pump 2 to provide flow needed for system.Whole system, without spill losses, saves energy.
As shown in Figure 1, be the schematic diagram of semi-variety system, turn to plunger displacement pump 2 to export P1 and be connected with the import P2 of switching valve block 7, turn to the LS mouth of plunger displacement pump 2 to be connected with the LS1 mouth of switching valve block 7, turn to the inlet port S1 of plunger displacement pump 2 and drain tap D to be connected with fuel tank 1.The E mouth of switching valve block 7 is connected with the P of distributing valve 10.The F mouth of switching valve block 7 is connected with the import P3 of steering gear 8.The LS2 mouth of switching valve block 7 is connected with the LS3 mouth of steering gear 8.The T1 mouth of switching valve block 7 is connected with fuel tank 1.The XP mouth of switching valve block 7 is connected with the P mouth of pilot valve 13.Accumulator 6 is connected across on the pipeline of connection XP mouth and pilot valve 13 oil inlet P.The X1 mouth of switching valve block 7 connects guide's hydraulic fluid port xa1 of distributing valve 10 and the A mouth of pilot valve, the X2 mouth of switching valve block 7 connects guide's hydraulic fluid port xb1 of distributing valve 10 and the C mouth of pilot valve, and the X3 mouth of switching valve block 7 connects guide's hydraulic fluid port xb2 of distributing valve 10 and the B mouth of pilot valve.The inlet port S2 of working barrel 3 is connected with fuel tank 1, and the outlet P4 of working barrel 3 is connected with the oil inlet P 5 of unloader block 5, and the oil-out P6 of unloader block 5 is connected with the import P of distributing valve 10.The A1 mouth of distributing valve 10 is connected with the rodless cavity of bucket cylinder 11, and the B1 mouth of distributing valve 10 is connected with the rod chamber of bucket cylinder 11.The A2 mouth of distributing valve 10 is connected with the rod chamber of boom cylinder 12, and the B2 mouth of distributing valve 10 is connected with the rodless cavity of boom cylinder 12, and the T mouth of distributing valve 10 is connected with the T4 mouth of radiator.The L mouth of steering gear 8 is connected with the L1 mouth of steering cylinder 9, and the R mouth of steering gear 8 is connected with the R1 of steering cylinder 9, and the T2 of steering gear 8 is connected with the T4 mouth of radiator.The T6 mouth of pilot valve 13 is connected with fuel tank 1, and the D mouth of pilot valve 13 is connected with guide's hydraulic fluid port xa2 of distributing valve 10.The outlet T5 of radiator 4 is connected with the oil-in of oil return filter 14, and the oil-out of oil return filter 14 is connected with fuel tank 1.
Be illustrated in figure 2 the schematic diagram of switching valve block 7, switching valve block 7 comprises two-way pressure compensator 101, turn signal damping 102, overflow valve 103, pilot operated directional control valve 104, first shuttle valve 105, three-way pressure compensating device 106, second shuttle valve 107, working signal damping 108, decompression overflow valve 109, one way valve 110, the 3rd shuttle valve 111, oil inlet P 2, oil-out E, F, XP, signal port LS1, LS2, guide's hydraulic fluid port X1, X2, X3; Oil return inlet T 2.
The F mouth of switching valve block 7 connects P2 mouth, the pilot operated directional control valve 104 of switching valve block 7 by two-way pressure compensator 101, be connected the E mouth of switching valve block 7 with three-way pressure compensating device 106 by two-way pressure compensator 101, connected the XP mouth of switching valve block 7 by two-way pressure compensator 101, decompression overflow valve 109, one way valve 110, connected the T1 mouth of decompression overflow valve 109, pilot operated directional control valve 104, switching valve block 7 by two-way pressure compensator 101, overflow valve 103; The LS2 mouth of described switching valve block 7 is connected pilot operated directional control valve 104, is connected two-way pressure compensator 101 by turn signal damping 102, is divided into two tunnels by the second shuttle valve 107, one tunnel connects the E mouth of switching valve block 7, and another road connects LS1 mouth through working signal damper 108; Described pilot operated directional control valve 104 is through turn signal damping 102 connecting tee pressure compensator 106; Described pilot operated directional control valve 104 connects guide's hydraulic fluid port X3, X2 of switching valve block 7 through the first shuttle valve 105, and guide's hydraulic fluid port X2 connects guide's hydraulic fluid port X1 through the 3rd shuttle valve 111.
Overflow valve 103 sets steering maximum pressure.Decompression overflow valve 109 sets the pressure of pilot control, and one way valve 110 ensure that accumulator can pressurize for a long time.
When loader only turns to, guide's hydraulic fluid port X1, X2, X3 of switching valve block 7 do not have pressure signal, pilot operated directional control valve 104 does not commutate, be operated in bottom, the epicoele of three-way pressure compensating device 106 is equal with spring cavity pressure, and three-way pressure compensating device 106 is in closed condition, and the flow needed for steering is determined by the spring force of two-way pressure compensator 101 and the valve port opening of steering gear 8, turn to plunger displacement pump 2 to be load sensitive pumps, the flow needed for steering is provided;
When swing arm promote or scraper bowl receive bucket or when putting bucket, a pressure signal transmission is had to pilot operated directional control valve 104 in guide's hydraulic fluid port X1, X2, X3 of switching valve block 7, liquid controlled reversing 104 commutates, the spring cavity of three-way pressure compensating device 106 is in low-pressure state, three-way pressure compensating device 106 is unlocked, the E mouth of switching valve block is communicated with LS1 mouth, and workload pressure signal transmission, to the LS mouth turning to plunger displacement pump 2, turns to plunger displacement pump delivery fuel feeding.When pressure does not reach the pressure unloading of unloader block 5, working barrel 3 fuel feeding is to unloader block 5, and hydraulic oil enters the P mouth of distributing valve 10 by P6 mouth.When pressure reaches the pressure unloading of unloader block 5, working barrel 3 to unloader block 5, enters the T4 mouth oil sump tank of radiator 4 with very low forced feed by T7 mouth.When the pressure turning to plunger displacement pump 2 to export reaches its cut-out pressure and workload does not reach cut-out pressure, turn to the discharge capacity of plunger displacement pump 2 to be decided by load pressure, pressure is higher, and pump delivery is less.When load pressure reach turn to plunger displacement pump 2 cut-out pressure time, the theoretical displacement of pump is zero.
When loader is existing turn to and have swing arm promote or scraper bowl receive bucket or put bucket time, a pressure signal transmission is had to pilot operated directional control valve 4 in guide's hydraulic fluid port X1, X2, X3 of switching valve block 7, liquid controlled reversing 4 commutates, and three-way pressure compensating device 106 spring cavity and steering load signal are connected.When workload pressure is greater than steering load pressure, the steel ball in shuttle valve 107 is in left position, and the pressure signal transmission of workload is to the signal port LS turning to plunger displacement pump 2.The outlet pressure of plunger displacement pump 2 is turned to be determined by workload.The load pressure that two-way pressure compensator 102 compensate for workload and steering load is poor.When steering load pressure is greater than workload pressure, steel ball in shuttle valve 107 is in right position, the pressure signal transmission of steering load is to the signal port LS turning to plunger displacement pump 2, turn to the outlet pressure of plunger displacement pump 2 to be determined by steering load, three-way pressure compensating device 106 compensate for the pressure differential of steering load pressure and workload pressure.Three-way pressure compensating device 106 ensure that and turns to plunger displacement pump 2 in any case by the preferential fuel feeding of F mouth to steering, and unnecessary oil just can by E mouth supply hydraulic system of working.
When swing arm decline or the floating decline of loader, guide's hydraulic fluid port X1, X2, X3 of switching valve block 7 do not have pressure signal, pilot operated directional control valve 4 does not commutate, be operated in bottom, the epicoele of three-way pressure compensating device 106 is equal with spring cavity pressure, three-way pressure compensating device 106 is in closed condition, turns to plunger displacement pump 2 to be in low pressure armed state, and theoretical displacement is zero.
Claims (7)
1. a loader semi-variety hydraulic system, comprise hydraulic oil container (1), turn to plunger displacement pump (2), working barrel (3), unloader (5), accumulator (6), switching valve block (7), steering gear (8), steering cylinder (9), distributing valve (10), rotary ink tank (11), boom cylinder (12), pilot valve (13), the described plunger displacement pump (2) that turns to is by switching valve block (7), steering gear (8) connects steering cylinder (9), the unloading port of described switching valve block (7) connects hydraulic oil container (1), it is characterized in that: described switching valve block (7) also connects distributing valve (10), when turning to plunger displacement pump (2) by switching valve block (7), when steering gear (8) provides the steering cylinder (9) of steering required flow, without the pressure current oil sump tank of unnecessary steering load in the middle bit port of distributing valve (10), described switching valve block (7) also connects pilot valve (13), for loader swing arm decline or float decline or loader be in driving cycle time, described pilot valve (13) no signal passes to switching valve block (7), makes to turn to plunger displacement pump (2) to export without flow, described working barrel (3) connects distributing valve (10) by unloader (5), distributing valve (10) connects rotary ink tank (11) and boom cylinder (12), when system enters high-pressure low-flow state, the flow that working barrel (3) exports gets back to fuel tank by unloader (5) with low pressure, turns to plunger displacement pump (2) to provide flow needed for system.
2. loader semi-variety hydraulic system according to claim 1, it is characterized in that: described in turn to plunger displacement pump (2) export P1 be connected with the import P2 of switching valve block (7), the LS mouth of plunger displacement pump (2) is turned to be connected with the LS1 mouth of switching valve block (7), the inlet port S1 of plunger displacement pump (2) is turned to be connected with fuel tank (1) with drain tap D, the E mouth of switching valve block (7) is connected with the P mouth of distributing valve (10), the F mouth of switching valve block (7) is connected with the import P3 of steering gear (8), the LS2 mouth of switching valve block (7) is connected with the LS3 mouth with steering gear (8), the T1 mouth of switching valve block (7) is connected with fuel tank (1), the XP mouth of switching valve block (7) is connected with the P mouth of pilot valve (13), the X1 mouth of switching valve block (7) connects guide's hydraulic fluid port xb1 of distributing valve (10) and the A mouth of pilot valve, the X2 mouth of switching valve block (7) connects guide's hydraulic fluid port xa1 of distributing valve (10) and the C mouth of pilot valve, the X3 mouth of switching valve block (7) connects guide's hydraulic fluid port xa2 of distributing valve (10) and the B mouth of pilot valve.
3. loader semi-variety hydraulic system according to claim 2, it is characterized in that: the inlet port S2 of described working barrel (3) is connected with fuel tank 1, the outlet P4 of working barrel (3) is connected with the oil inlet P 5 of unloader block (5), the oil-out P6 of unloader block (5) is connected with the import P of distributing valve, the A1 mouth of distributing valve (10) is connected with the rodless cavity of rotary ink tank (11), the B1 mouth of distributing valve (10) is connected with the rod chamber of bucket cylinder (11), the A2 mouth of distributing valve (10) is connected with the rod chamber of boom cylinder (11), the B2 mouth of distributing valve (10) is connected with the rodless cavity of boom cylinder (11), the T mouth of distributing valve (10) is connected with the T4 mouth of radiator.
4. loader semi-variety hydraulic system according to claim 3, it is characterized in that: the L mouth of described steering gear (8) is connected with the L1 mouth of steering cylinder (9), the R mouth of steering gear (8) is connected with the R1 mouth of steering cylinder (9), the T2 mouth of steering gear (8) is connected with the T4 mouth of radiator, the T6 mouth of pilot valve (13) is connected with fuel tank 1, and the D mouth of pilot valve (13) is connected with guide's hydraulic fluid port xb2 of distributing valve (10).
5. loader semi-variety hydraulic system according to claim 4, is characterized in that: described switching valve block (7) comprises two-way pressure compensator (101), turn signal damping (102), overflow valve (103), pilot operated directional control valve (104), first shuttle valve (105), three-way pressure compensating device (106), second shuttle valve (107), working signal damper (108), decompression overflow valve (109), one way valve (110), 3rd shuttle valve (111), the F mouth of described switching valve block (7) connects the P2 mouth of switching valve block (7) by two-way pressure compensator (101), pilot operated directional control valve (104), is connected the E mouth of switching valve block (7), by two-way pressure compensator (101) with three-way pressure compensating device (106) by two-way pressure compensator (101), decompression overflow valve (109), one way valve (110) connects the XP mouth of switching valve block (7), by two-way pressure compensator (101), overflow valve (103) connects decompression overflow valve (109), pilot operated directional control valve (104), the T1 mouth of switching valve block (7), the LS2 mouth of described switching valve block (7) connects pilot operated directional control valve (104), is connected two-way pressure compensator (101) by turn signal damper (102), be divided into two tunnels by the second shuttle valve (107), one tunnel connects the E mouth of switching valve block (7), and another road connects LS1 mouth through working signal damper (108), described pilot operated directional control valve (104) is through turn signal damper (102) connecting tee pressure compensator (106), described pilot operated directional control valve (104) connects guide's hydraulic fluid port X3, X2 of switching valve block (7) through the first shuttle valve (105), and guide's hydraulic fluid port X2 connects guide's hydraulic fluid port X1 through the 3rd shuttle valve (111).
6. loader semi-variety hydraulic system according to claim 5, it is characterized in that: when loader only turns to, guide's hydraulic fluid port X1, X2, X3 of described switching valve block (7) are without pressure, described three-way pressure compensating device (106) is in closed condition, the described plunger displacement pump (2) that turns to is connected steering cylinder (9) by the two-way pressure compensator (101) controlled by spring force with the steering gear (8) controlled by valve port opening, provides required flow to steering cylinder (9).
7. loader semi-variety hydraulic system according to claim 5, is characterized in that: when steering load pressure is higher than workload pressure, and described three-way pressure compensating device (106) compensates the pressure differential of steering load pressure and workload pressure; When workload pressure is higher than steering load pressure, the pressure differential of described two-way pressure compensator (102) compensation work load pressure and steering load pressure.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420801695.9U CN204491707U (en) | 2014-12-16 | 2014-12-16 | Loader semi-variety hydraulic system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420801695.9U CN204491707U (en) | 2014-12-16 | 2014-12-16 | Loader semi-variety hydraulic system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN204491707U true CN204491707U (en) | 2015-07-22 |
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ID=53571011
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420801695.9U Withdrawn - After Issue CN204491707U (en) | 2014-12-16 | 2014-12-16 | Loader semi-variety hydraulic system |
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| Country | Link |
|---|---|
| CN (1) | CN204491707U (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104405006A (en) * | 2014-12-16 | 2015-03-11 | 派克汉尼汾流体传动产品（上海）有限公司 | Loading machine hemi-variate hydraulic system |
| CN108978772A (en) * | 2018-07-20 | 2018-12-11 | 广西柳工机械股份有限公司 | Load-sensitive steering hydraulic system and loading machine |
| CN109235533A (en) * | 2018-09-13 | 2019-01-18 | 广西柳工机械股份有限公司 | Loading machine hydraulic system of working |
| CN110984285A (en) * | 2019-12-09 | 2020-04-10 | 广西柳工机械股份有限公司 | Distribution valve for loader and loader hydraulic system |
-
2014
- 2014-12-16 CN CN201420801695.9U patent/CN204491707U/en not_active Withdrawn - After Issue
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104405006A (en) * | 2014-12-16 | 2015-03-11 | 派克汉尼汾流体传动产品（上海）有限公司 | Loading machine hemi-variate hydraulic system |
| CN104405006B (en) * | 2014-12-16 | 2016-09-07 | 派克汉尼汾流体传动产品（上海）有限公司 | Loading machine semi-variety hydraulic system |
| CN108978772A (en) * | 2018-07-20 | 2018-12-11 | 广西柳工机械股份有限公司 | Load-sensitive steering hydraulic system and loading machine |
| CN108978772B (en) * | 2018-07-20 | 2020-11-20 | 广西柳工机械股份有限公司 | Load-sensitive steering hydraulic system and loader |
| CN109235533A (en) * | 2018-09-13 | 2019-01-18 | 广西柳工机械股份有限公司 | Loading machine hydraulic system of working |
| CN109235533B (en) * | 2018-09-13 | 2020-11-17 | 广西柳工机械股份有限公司 | Loader working hydraulic system |
| CN110984285A (en) * | 2019-12-09 | 2020-04-10 | 广西柳工机械股份有限公司 | Distribution valve for loader and loader hydraulic system |
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