CN202215524U - Flow switch control valve and hydraulic control device for loading machine - Google Patents
Flow switch control valve and hydraulic control device for loading machine Download PDFInfo
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- CN202215524U CN202215524U CN2011203439972U CN201120343997U CN202215524U CN 202215524 U CN202215524 U CN 202215524U CN 2011203439972 U CN2011203439972 U CN 2011203439972U CN 201120343997 U CN201120343997 U CN 201120343997U CN 202215524 U CN202215524 U CN 202215524U
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Abstract
The utility model discloses a flow switch control valve, which belongs to the technical field of engineering machinery. Ten valve cavities and eight oil holes are arranged on a valve body, five bosses and two hydraulic oil channels are arranged on a valve rod, and a compression spring is arranged between the valve rod and a safety valve. Simultaneously, the utility model further discloses a hydraulic control device of a loading machine, which comprises a load sensor turning hydraulic circuit and a working device hydraulic circuit. The load sensor turning hydraulic circuit uses a double connection turning pump and a flow control switch control valve, wherein a second oil hole of the flow switch control valve is connected with an outlet of a working pump of the working device hydraulic circuit. In working, the flow switch control valve can automatically adjust position of the valve rod according to pressure and flow of all oil holes to reasonably distribute oil inlet amount of the double connection turning pump, thereby improving low speed turning flow of an engine, improving comfort of turning operation, reducing high speed turning oil consumption of the engine, improving thermal balance temperature of a hydraulic system, and reducing fault rate of oil leakage of valve rods of multi-channel valves.
Description
Technical field
The utility model relates to a kind of flow switchover control valve and uses the loader hydraulic control device of this flow switchover control valve.
Background technique
In the present loader hydraulic system design; Loader load sensing steering hydraulic system adopts a steering pump to add the pressure-gradient control valve combination of application of load sensing all-hydraulic steering gear again; The hydraulic oil of steering pump output gets into pressure-gradient control valve and is divided into two-way; One the tunnel gets into the load sensing all-hydraulic steering gear, gets into to turn to oil cylinder control loading machine steering again; Another road gets into equipment hydraulic system and working pump interflow; Getting into rotary ink tank or boom cylinder through multiple directional control valve shovels and pretends industry; The oil return of rotary ink tank or boom cylinder gets into the multiple directional control valve return opening, with steering hydraulic system oil return interflow, through the throttling shunting of two restrictions; Control gets into the flow of hydraulic oil radiator, thereby hydraulic system is cooled off the thermal equilibrium temperature that reaches certain.Because during time of engine low speed, the steering pump rotating speed is lower, so displacement of steering pump can not be too little, otherwise hard steering; In high engine speeds when running,, the steering pump rotating speed is higher, so displacement of steering pump can not be too big, otherwise energy loss is bigger when only turning to; Existing domestic main flow loader load-sensitive steering hydraulic system has been chosen from the consideration of above two aspects and has been turned to pump delivery (5 tons of loading machine steering pump displacements are generally 80ml/r); Because engine idle (about about 750r/Min) differs too big with high speed (about about 2200r/Min); So ubiquity following problems: when time of engine low speed is beaten steering wheel soon; The hydraulic oil of steering pump output can not satisfy the demand of load sensing all-hydraulic steering gear; So cause hard steering (the steering wheel rotating speed is lower than 50r/min) and turn to shake, so operation comfort and Security are relatively poor; And high engine speeds turns round when only beating steering wheel, and the steering pump fuel feeding is very big again, much larger than load sensing hydraulic steering gear demand, therefore causes energy dissipation.In addition; Hydraulic oil heat radiation flow leans on the throttling shunting of two restrictions from the oil return of equipment hydraulic system, and control gets into the flow of hydraulic oil radiator; Because equipment when work oil return total discharge alters a great deal (falling like swing arm is about 5,6 times of moved arm lifting); And the return oil pressure that forms is big (about the about 1.5MPa of peak value), so radiating effect is relatively poor, and the long-time return oil pressure that changes repeatedly causes leaking outside of multiple directional control valve valve rod easily.
The loader load sensing steering hydraulic system that has adopts an independent steering pump to add the pressure-gradient control valve combination of application of load sensing hydraulic commutator again; The equipment hydraulic system also adopts a big discharge capacity working pump separately; The hydraulic oil of steering pump output gets into pressure-gradient control valve and is divided into two-way; One the tunnel gets into the load sensing all-hydraulic steering gear, gets into to turn to oil cylinder control loading machine steering again; Another road gets into hydraulic oil radiator; This system is because displacement of steering pump big (5 tons of loaders are generally 80ml or 100ml); The steering pump flow was not bigger when high engine speeds did not turn to, and is therefore bigger to the impact of hydraulic oil radiator, so hydraulic oil radiator also needs a parallelly connected overload valve; This system's double pump works alone; Energy loss was equally very big when high engine speeds was only beaten steering wheel, and oil consumption is collaborated system apparently higher than double pump, still not basic solve (the steering wheel rotating speed also is lower than 60r/min during 100ml discharge capacity steering pump engine idle) of the heavy problem of low speed.
The employing that has three pump system, the hydraulic oil of loader load-sensitive steering hydraulic system steering pump output gets into pressure-gradient control valve and is divided into two-way, the one tunnel gets into the load sensing all-hydraulic steering gear, gets into to turn to oil cylinder control loading machine steering again; Another road and load sensing hydraulic steering gear oil return interflow get into hydraulic oil radiator; This hydraulic system also has the 3rd oil hydraulic pump and flow conversion valve, when having realized low speed by flow conversion valve to the steering hydraulic system fuel feeding, solved the heavy problem of low engine speed; When the high engine speeds running only turns to, because displacement of steering pump is less, more energy-conservation in theory; But steering system has added a sentinel valve, has increased restriction loss, and when low engine speed was only beaten direction slowly in addition, the 3rd oil hydraulic pump still collaborated steering system through flow conversion valve, has therefore increased energy consumption again; Hydraulic element are more simultaneously, and the loader upper pipeline is difficult arranges that cost is higher.
The model utility content
The utility model technical problem to be solved is: a kind of flow switchover control valve is provided, and compact structure has been realized the conversion of hydraulic oil multichannel and has been adjusted steering flow automatically.
For solving the problems of the technologies described above; The technological scheme of the utility model is: the flow switchover control valve; Comprise valve body, be provided with slideway in the said valve body, be slidingly fitted with valve rod in the said slideway; The two ends of said slideway are respectively equipped with safety valve and plug, and said slideway is interior from being provided with first valve pocket, second valve pocket, the 3rd valve pocket, the 4th valve pocket, the 5th valve pocket, the 6th valve pocket, the 7th valve pocket, the 8th valve pocket, the 9th valve pocket and the tenth valve pocket between safety valve to the plug successively; Be provided with first boss, second boss, the 3rd boss, the 4th boss and the 5th boss successively from safety valve to plug on the said valve rod; Said first boss is arranged at an end of said valve rod and between second valve pocket and the 3rd valve pocket; Be provided with pressure spring between said first boss and the safety valve; Said second boss is arranged at the 4th valve pocket place; Said second boss is provided with along the axially extended second boss groove of said valve rod away from an end surfaces of first boss; Said the 3rd boss is arranged at the 6th valve pocket place, and said the 3rd boss is provided with along axially extended the 3rd boss groove of said valve rod near an end surfaces of first boss, and said the 4th boss is positioned at the 8th valve pocket place; The surface at said the 4th boss two ends is equipped with along axially extended the 4th boss groove of said valve rod, and said the 5th boss is arranged at the other end of said valve rod and is positioned at the tenth valve pocket place; Said valve rod is provided with first passage and the second channel that is not connected; Said first passage extends to second boss from the end face of first boss; Said second channel extends to the 3rd boss from the end face of the 5th boss, between first boss and second boss, is provided with first through hole on the said valve rod, and said first through hole is communicated with first passage; Said the 3rd boss is provided with second through hole, and said second through hole is communicated with second channel; Said valve body is provided with first hydraulic fluid port, second hydraulic fluid port, the 3rd hydraulic fluid port, the 4th hydraulic fluid port, the 5th hydraulic fluid port, the 6th hydraulic fluid port, the 7th hydraulic fluid port and the 8th hydraulic fluid port; Said first hydraulic fluid port is communicated with the 4th valve pocket; Said second hydraulic fluid port is communicated with the 9th valve pocket, and said the 3rd hydraulic fluid port turns to channel connection the 6th valve pocket through first, and said the 3rd hydraulic fluid port turns to channel connection the 7th valve pocket through second; Said second turns to and is provided with the one-way valve that allows hydraulic oil to be flowed to the 3rd hydraulic fluid port by the 7th valve pocket in the passage; Said the 4th hydraulic fluid port is communicated with the 4th valve pocket and relative with the said first hydraulic fluid port position, and said the 5th hydraulic fluid port is communicated with the 3rd valve pocket, and said the 6th hydraulic fluid port is communicated with the 5th valve pocket; Said the 7th hydraulic fluid port is communicated with the 8th valve pocket, and said the 8th hydraulic fluid port is communicated with first valve pocket.
Owing to adopted technique scheme; The beneficial effect of the utility model is: because valve body is provided with ten valve pockets and eight hydraulic fluid ports; Valve rod is provided with five boss and two hydraulic oil channels; Between valve rod and safety valve, be provided with pressure spring, valve rod can be adjusted the position automatically according to hydraulic fluid pressure and pressure spring, thereby changes the hydraulic fluid flow rate of each hydraulic fluid port.
The utility model technical problem to be solved also has: a kind of loader hydraulic control device is provided; Can improve the low engine speed steering flow, promote the handling maneuver travelling comfort, reduce high engine speeds and turn to energy consumption; And improve the heat equilibrium of hydraulic system temperature, reduce multi-way valve valve rod oil leakage phenomenon.
For solving the problems of the technologies described above; The technological scheme of the utility model is: the loader hydraulic control device; Comprise load sensing steering hydraulic loop and equipment oil hydraulic circuit, said load sensing steering hydraulic loop comprises duplex steering pump, flow switchover control valve, all-hydraulic steering gear and hydraulic oil radiator, and said equipment oil hydraulic circuit comprises working pump, multiple directional control valve; Said first hydraulic fluid port connects the return opening of said all-hydraulic steering gear; Said second hydraulic fluid port is connected with the working pump outlet of said equipment oil hydraulic circuit, and said the 3rd hydraulic fluid port connects the filler opening of said all-hydraulic steering gear, and said the 4th hydraulic fluid port connects fuel tank through hydraulic oil radiator; Said the 5th hydraulic fluid port connects the load sensing mouth of all-hydraulic steering gear; Said the 6th hydraulic fluid port connects said duplex steering pump main pump, and said the 7th hydraulic fluid port connects the auxilliary pump of said duplex steering pump, and said the 8th hydraulic fluid port connects fuel tank.
Owing to adopted technique scheme, the beneficial effect of the utility model is: because duplex steering pump and flow switchover control valve have been used in load sensing steering hydraulic loop, second hydraulic fluid port of flow switchover control valve is connected with the outlet of the working pump of equipment oil hydraulic circuit; When work; The flow switchover control valve can be adjusted the position automatically according to the pressure and the flow of each hydraulic fluid port, and the oil inlet quantity of reasonable distribution duplex steering pump improves the low engine speed steering flow; Promoted the travelling comfort of handling maneuver; Reduce high engine speeds and turned to energy consumption, and improved the heat equilibrium of hydraulic system temperature, reduced multi-way valve valve rod oil leakage phenomenon.
Description of drawings
Below in conjunction with accompanying drawing and embodiment the utility model is further specified.
Fig. 1 is the utility model embodiment's a structural representation;
Fig. 2 is the sectional view of A-A among Fig. 1;
Fig. 3 is the utility model embodiment's a hydraulic schematic diagram;
Fig. 4 is flow switchover control valve working state figure during time of engine low speed among the utility model embodiment;
Fig. 5 is the sectional view of B-B in the accompanying drawing 4;
Fig. 6 is the flow switchover control valve working state figure when motor high speed turns round among the utility model embodiment;
Fig. 7 is the sectional view of E-E in the accompanying drawing 6;
Flow switchover control valve working state figure when Fig. 8 stops for engine running steering wheel among the utility model embodiment;
Fig. 9 is the sectional view of F-F among Fig. 8;
Among the figure: the M-all-hydraulic steering gear; The N-working pump; The K-hydraulic oil radiator; The T-fuel tank; Q-flow switchover control valve; X-duplex steering pump main pump; Y-duplex steering pump is assisted pump; The G-multiple directional control valve;
The 1-safety valve; The 2-valve body; The 3-pressure spring; 4-first boss; 5-the 3rd valve pocket; 6-first hydraulic fluid port; 7-second boss; 8-second valve pocket; The 9-second boss groove; The 10-first passage; 11-the 3rd boss groove; 12-second through hole; 13-the 3rd boss; 14-the 4th boss groove; 15-the 4th boss; 16-the 5th valve pocket; 17-second hydraulic fluid port; The 18-valve rod; 19-the tenth valve pocket; 20-the 9th valve pocket; 21-the 8th valve pocket; 22-second turns to passage; The 23-one-way valve; The 24-plug; 25-first turns to passage; 26-the 3rd hydraulic fluid port; 27-the 4th valve pocket; 28-the 4th hydraulic fluid port; 29-first through hole; 30-the 7th valve pocket; 31-first valve pocket; 32-the 8th hydraulic fluid port; 33-the 5th hydraulic fluid port; 34-the 6th hydraulic fluid port; 35-the 7th hydraulic fluid port; The 36-second channel; 37-the 5th boss; 38-the 6th valve pocket.
Embodiment
As depicted in figs. 1 and 2; A kind of flow switchover control valve; Comprise valve body 2, be provided with slideway in the said valve body 2, be slidingly fitted with valve rod 18 in the said slideway; The two ends of said slideway are respectively equipped with safety valve 1 and plug 24, in the said slideway from being provided with first valve pocket 31, second valve pocket 8, the 3rd valve pocket 5, the 4th valve pocket 27, the 5th valve pocket 16, the 6th valve pocket 38, the 7th valve pocket 30, the 8th valve pocket 21, the 9th valve pocket 20 and the tenth valve pocket 19 between safety valve 1 to the plug 24 successively; Be provided with first boss 4, second boss 7, the 3rd boss 13, the 4th boss 15 and the 5th boss 37 successively from safety valve 1 to plug 24 on the said valve rod 18; Said first boss 4 is arranged at an end of said valve rod 18 and between second valve pocket 8 and the 3rd valve pocket 5; Be provided with pressure spring 3 between said first boss 4 and the safety valve 1; Said second boss 7 is arranged at the 4th valve pocket 27 places; Said second boss 7 is provided with along the said valve rod 18 axially extended second boss grooves 9 away from an end surfaces of first boss 4; Said the 3rd boss 13 is arranged at the 6th valve pocket 38 places, and said the 3rd boss 13 is provided with along said valve rod 18 axially extended the 3rd boss grooves 11 near an end surfaces of first boss 4, and said the 4th boss 15 is positioned at the 8th valve pocket 21 places; The surface at said the 4th boss 15 two ends is equipped with along said valve rod 18 axially extended the 4th boss grooves 14, and said the 5th boss 37 is arranged at the other end of said valve rod 18 and is positioned at the tenth valve pocket 19 places; Said valve rod 18 is provided with the first passage 10 and second channel 36 that is not connected; Said first passage 10 extends to second boss 7 from the end face of first boss 4; Said second channel 36 extends to the 3rd boss 13 from the end face of the 5th boss 37, between first boss 4 and second boss 7, is provided with first through hole 29 on the said valve rod 18, and said first through hole 29 is communicated with first passage 10; Said the 3rd boss 13 is provided with second through hole 12, and said second through hole 12 is communicated with second channel 36; Said valve body 2 is provided with first hydraulic fluid port 6, second hydraulic fluid port 17, the 3rd hydraulic fluid port 26, the 4th hydraulic fluid port 28, the 5th hydraulic fluid port 33, the 6th hydraulic fluid port 34, the 7th hydraulic fluid port 35 and the 8th hydraulic fluid port 32; Said first hydraulic fluid port 6 is communicated with the 4th valve pocket 27; Said second hydraulic fluid port 17 is communicated with the 9th valve pocket 20; Said the 3rd hydraulic fluid port 26 turns to passage 25 to be communicated with the 6th valve pocket 38 through first; Said the 3rd hydraulic fluid port 26 turns to passage 22 to be communicated with the 7th valve pocket 30 through second, and said second turns to be provided with in the passage 22 and allow hydraulic oil to flow to the one-way valve 23 of the 3rd hydraulic fluid port 26 by the 7th valve pocket 30, and said the 4th hydraulic fluid port 28 is communicated with the 4th valve pockets 27 and relative with said first hydraulic fluid port 6 positions; Said the 5th hydraulic fluid port 33 is communicated with the 3rd valve pocket 5; Said the 6th hydraulic fluid port 34 is communicated with the 5th valve pocket 16, and said the 7th hydraulic fluid port 35 is communicated with the 8th valve pocket 21, and said the 8th hydraulic fluid port 32 is communicated with first valve pocket 31.
As shown in Figure 3; A kind of loader hydraulic control device; Comprise load sensing steering hydraulic loop and equipment oil hydraulic circuit; Said load sensing steering hydraulic loop comprises duplex steering pump, flow switchover control valve Q, all-hydraulic steering gear M and hydraulic oil radiator K, and said equipment oil hydraulic circuit comprises working pump N, multiple directional control valve G, and said first hydraulic fluid port 6 connects the return opening of said all-hydraulic steering gear M; Said second hydraulic fluid port 17 is connected with the working pump N outlet of said equipment oil hydraulic circuit; Said the 3rd hydraulic fluid port 26 connects the filler opening of said all-hydraulic steering gear M, and said the 4th hydraulic fluid port 28 connects fuel tank T through hydraulic oil radiator K, and said the 5th hydraulic fluid port 33 connects the load sensing mouth of all-hydraulic steering gear M; Said the 6th hydraulic fluid port 34 connects said duplex steering pump main pump X; Said the 7th hydraulic fluid port 35 connects the auxilliary pump Y of said duplex steering pump, and said the 8th hydraulic fluid port 32 connects fuel tank T (also can cancellation the 8th hydraulic fluid port 32 outer connected tank T directly being communicated with first valve pocket 31 with the 4th valve pocket 27) in valve body 2.
Its working principle is:
The filler opening pressure of all-hydraulic steering gear M turns to passage 25, second through hole 12, second channel 36 to affact the right-hand member of the 5th boss 37 of valve rod 18 through the 3rd hydraulic fluid port 26, first; Load sensing mouth (load) pressure of all-hydraulic steering gear M affacts the left end of valve rod 18 through the 5th hydraulic fluid port 33, the 3rd valve pocket 5, first through hole 29, first passage 10; The active force that the pressure at two ends difference forms and the power of surging and the power of pressure spring 3 that affact on the valve rod 18 balance each other; Make valve rod 18 be in a certain position in the valve body 2; Change flow switchover control valve Q inside and lead to the openings of sizes of second hydraulic fluid port 17 and the 4th hydraulic fluid port 28, thereby the oily flow distribution that changes duplex steering pump main pump X and the auxilliary pump Y of duplex steering pump concerns.
Like Fig. 4 and shown in Figure 5; During loader time of engine low speed steering wheel rotation; The hydraulic fluid flow rate that gets into the 6th hydraulic fluid port 34 is less; Get into first and turn to the hydraulic fluid flow rate of passage 25 also just less, pressure reduction through hydraulic steering gear M and the power of surging that valve rod 18 is formed are less, under the effect of pressure spring 3; Valve rod 18 deflection right-hand members, this moment, the hydraulic oil of the 6th hydraulic fluid port 34 turned to the hydraulic oil of passage 25 and the 7th hydraulic fluid port 35 to turn to passage 22, one-way valve 23 common the 3rd hydraulic fluid ports 26 that get into through second through first; The 7th hydraulic fluid port 35 unnecessary hydraulic oil get into second hydraulic fluid port 17 through the 4th boss groove 14 on the 4th boss 15, and all-hydraulic steering gear M oil return gets into the 4th hydraulic fluid port 28 through first hydraulic fluid port 6.
Like Fig. 6 and shown in Figure 7; During loader motor high speed running steering wheel rotation; The hydraulic fluid flow rate that gets into the 6th hydraulic fluid port 34 is bigger, and pressure reduction through hydraulic steering gear M and the power of surging that valve rod 18 is formed are bigger, under the effect of pressure spring 3; Valve rod 18 deflection left ends, this moment, the hydraulic oil of the 6th hydraulic fluid port 34 turned to passage 25 to get into the 3rd hydraulic fluid port 26 through first; The 6th hydraulic fluid port 34 unnecessary hydraulic oil get into the 4th hydraulic fluid port 28 through the second boss groove 9 on second boss 7; The hydraulic oil of the 7th hydraulic fluid port 35 gets into second hydraulic fluid port 17 through the 4th boss groove 14 on the 4th boss 15.
Like Fig. 8 and shown in Figure 9; When loader engine running steering wheel was motionless, the hydraulic oil that gets into the 6th hydraulic fluid port 34 was had an appointment the flow of 4L/min through all-hydraulic steering gear M, and this moment, the pressure reduction of all-hydraulic steering gear M was maximum; This differential pressure action is to the two ends of valve rod 18; Balance pressure spring 3 makes valve rod 18 be in high order end, and the hydraulic oil of the 6th hydraulic fluid port 34 gets into the 4th hydraulic fluid port 28 through the second boss groove 9 on second boss 7; The hydraulic oil of the 7th hydraulic fluid port 35 gets into second hydraulic fluid port 17 through the 4th boss groove 14 on the 4th boss 15.
Heavy, direction shake of steering wheel and high engine speeds steering pump energy dissipation problem when this flow switchover control valve Q has solved low engine speed that existing domestic main flow loader load sensing steering hydraulic system exists and beats direction soon; Reduced heat equilibrium of hydraulic system temperature and multiple directional control valve G valve rod oil leakage fault rate simultaneously, be embodied in:
During time of engine low speed; The auxilliary pump Y of duplex steering pump main pump X and duplex steering pump preferentially collaborates hydraulic steering gear M through flow switchover control valve Q, has strengthened steering flow; Improve steering wheel rotating speed (maximum speed can surpass 75r/min), promoted handling comfort and Security; When the motor high speed only turns round steering situation, only make hydraulic oil flow that duplex steering pump main pump X provides, reduced turning to pump delivery to reduce energy consumption to steering system; When loader does not turn to; The whole hydraulic oil flows of duplex steering pump main pump X dispel the heat to the 4th hydraulic fluid port 28; The auxilliary pump Y of duplex steering pump gets into the equipment oil hydraulic circuit through the inner oil duct of flow switchover control valve Q; Reduced energy consumption, also can connect equivalent unloading valve, further cut down the consumption of energy at second hydraulic fluid port 17; The all working operating mode has guaranteed the stability of flow of hydraulic oil through hydraulic oil radiator K, has reduced the heat equilibrium of hydraulic system temperature, has reduced multiple directional control valve G valve rod oil leakage fault rate, has bigger applying and actual use value.
The utility model is not limited to above-mentioned concrete mode of execution, and those of ordinary skill in the art is from above-mentioned design, and without performing creative labour, all conversion of having done all drop within the protection domain of the utility model.
Claims (2)
1. the flow switchover control valve comprises valve body, is provided with slideway in the said valve body, is slidingly fitted with valve rod in the said slideway, and the two ends of said slideway are respectively equipped with safety valve and plug, it is characterized in that:
Said slideway is interior from being provided with first valve pocket, second valve pocket, the 3rd valve pocket, the 4th valve pocket, the 5th valve pocket, the 6th valve pocket, the 7th valve pocket, the 8th valve pocket, the 9th valve pocket and the tenth valve pocket between safety valve to the plug successively;
Be provided with first boss, second boss, the 3rd boss, the 4th boss and the 5th boss successively from safety valve to plug on the said valve rod; Said first boss is arranged at an end of said valve rod and between second valve pocket and the 3rd valve pocket; Be provided with pressure spring between said first boss and the safety valve; Said second boss is arranged at the 4th valve pocket place; Said second boss is provided with along the axially extended second boss groove of said valve rod away from an end surfaces of first boss; Said the 3rd boss is arranged at the 6th valve pocket place, and said the 3rd boss is provided with along axially extended the 3rd boss groove of said valve rod near an end surfaces of first boss, and said the 4th boss is positioned at the 8th valve pocket place; The surface at said the 4th boss two ends is equipped with along axially extended the 4th boss groove of said valve rod, and said the 5th boss is arranged at the other end of said valve rod and is positioned at the tenth valve pocket place; Said valve rod is provided with first passage and the second channel that is not connected; Said first passage extends to second boss from the end face of first boss; Said second channel extends to the 3rd boss from the end face of the 5th boss, between first boss and second boss, is provided with first through hole on the said valve rod, and said first through hole is communicated with first passage; Said the 3rd boss is provided with second through hole, and said second through hole is communicated with second channel;
Said valve body is provided with first hydraulic fluid port, second hydraulic fluid port, the 3rd hydraulic fluid port, the 4th hydraulic fluid port, the 5th hydraulic fluid port, the 6th hydraulic fluid port, the 7th hydraulic fluid port and the 8th hydraulic fluid port; Said first hydraulic fluid port is communicated with the 4th valve pocket; Said second hydraulic fluid port is communicated with the 9th valve pocket, and said the 3rd hydraulic fluid port turns to channel connection the 6th valve pocket through first, and said the 3rd hydraulic fluid port turns to channel connection the 7th valve pocket through second; Said second turns to and is provided with the one-way valve that allows hydraulic oil to be flowed to the 3rd hydraulic fluid port by the 7th valve pocket in the passage; Said the 4th hydraulic fluid port is communicated with the 4th valve pocket and relative with the said first hydraulic fluid port position, and said the 5th hydraulic fluid port is communicated with the 3rd valve pocket, and said the 6th hydraulic fluid port is communicated with the 5th valve pocket; Said the 7th hydraulic fluid port is communicated with the 8th valve pocket, and said the 8th hydraulic fluid port is communicated with first valve pocket.
2. use the loader hydraulic control device of flow switchover control valve as claimed in claim 1; Comprise load sensing steering hydraulic loop and equipment oil hydraulic circuit; Said load sensing steering hydraulic loop comprises duplex steering pump, flow switchover control valve, all-hydraulic steering gear and hydraulic oil radiator; Said equipment oil hydraulic circuit comprises working pump, multiple directional control valve, it is characterized in that: said first hydraulic fluid port connects the return opening of said all-hydraulic steering gear, and said second hydraulic fluid port is connected with the working pump outlet of said equipment oil hydraulic circuit; Said the 3rd hydraulic fluid port connects the filler opening of said all-hydraulic steering gear; Said the 4th hydraulic fluid port connects fuel tank through hydraulic oil radiator, and said the 5th hydraulic fluid port connects the load sensing mouth of all-hydraulic steering gear, and said the 6th hydraulic fluid port connects said duplex steering pump main pump; Said the 7th hydraulic fluid port connects the auxilliary pump of said duplex steering pump, and said the 8th hydraulic fluid port connects fuel tank.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011203439972U CN202215524U (en) | 2011-09-14 | 2011-09-14 | Flow switch control valve and hydraulic control device for loading machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011203439972U CN202215524U (en) | 2011-09-14 | 2011-09-14 | Flow switch control valve and hydraulic control device for loading machine |
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| Publication Number | Publication Date |
|---|---|
| CN202215524U true CN202215524U (en) | 2012-05-09 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011203439972U Expired - Fee Related CN202215524U (en) | 2011-09-14 | 2011-09-14 | Flow switch control valve and hydraulic control device for loading machine |
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| Country | Link |
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| CN (1) | CN202215524U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111152838A (en) * | 2018-11-08 | 2020-05-15 | 扬州盛达特种车有限公司 | Hydraulic integrated control device for mine car steering system and box body lifting system |
-
2011
- 2011-09-14 CN CN2011203439972U patent/CN202215524U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111152838A (en) * | 2018-11-08 | 2020-05-15 | 扬州盛达特种车有限公司 | Hydraulic integrated control device for mine car steering system and box body lifting system |
| CN111152838B (en) * | 2018-11-08 | 2023-08-15 | 潍柴(扬州)特种车有限公司 | Hydraulic integrated control device for mine car steering system and box lifting system |
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| 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 |
Granted publication date: 20120509 Termination date: 20150914 |
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| EXPY | Termination of patent right or utility model |