CN2818871Y - Feedback loading multi-path valve - Google Patents
Feedback loading multi-path valve Download PDFInfo
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- CN2818871Y CN2818871Y CN 200520040516 CN200520040516U CN2818871Y CN 2818871 Y CN2818871 Y CN 2818871Y CN 200520040516 CN200520040516 CN 200520040516 CN 200520040516 U CN200520040516 U CN 200520040516U CN 2818871 Y CN2818871 Y CN 2818871Y
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Abstract
The utility model discloses a feedback loading multi-path valve, which relates to the technical field of the multi-path valve adapting to the control of the pressure of a hydraulic system working in a caterpillar bulldozer. The feedback loading multi-path valve is composed of a control sliding valve set and an inlet valve. An upper signal oil cavity of each reversing valve in the inlet valve forms a signal oil path passage with an oil passage. Operating oil pressure from the manipulated reversing valve to an oil cylinder after the manipulated reversing valve throttled, namely signal oil pressure is transported to the inlet valve, enters an unloading valve and the left end of a differential pressure valve, and simultaneously enters an induction cavity of a back pressure valve via a throttling orifice. When one reversing valve operates, the operating oil pressure generated by the corresponding oil cylinder enters the signal oil cavity via an oil orifice on a corresponding reversing valve rod and then enters a shuttle valve, to push away steel balls. The operating oil pressure, namely the signal oil pressure is transported to the inlet valve. When all the reversal valves do not operate, the upper signal oil cavity of each reversing valve is communicated with an oil return passage on the valve. Both ends of the shuttle valve of the last piece of the reversing valve are simultaneously communicated with an oil return cavity, and the pressure of the whole signal oil path is released.
Description
Technical field
The utility model relates to a kind of crawler dozer hydraulic system of working pressure adaptation control multi-way valve.
Background technique
Present domestic crawler dozer equipment HYDRAULIC CONTROL SYSTEM multi-way valve is all reversing slide valve, compound throttling speed control circuit known to just.Be the multi-way valve schematic diagram of the perching knife band ridge buster that typically directly inclines as shown in Figure 1, relief valve 41 initialization system maximum pressures; When oil hydraulic cylinder is not worked, middle road draining.When oil hydraulic cylinder low speed was regulated, the pressure oil that working pump is discharged partly flowed into operating cylinder according to oil cylinder to the needs of flow size, and all the other release from restriction and relief valve 41.This throttle grverning pressure applicable system has following shortcoming:
1) the oil cylinder movement velocity is subjected to load effect, and the low-speed motion instability;
2) for a certain little opening, because the variation of load, the power of surging that acts on the commutation valve rod changes, and when causing steering force constant, valve rod will move, and the opening amount is also along with variation.Speed regulating control inconvenience, fine setting are difficult to obtain;
3) during the little opening of selector valve, pump oil pressure and working oil pressure reduction are big before and after the valve port, and the throttling energy consumption is big, and the throttling energy consumption is big, and opening is healed more little;
4) unnecessary pump oil will be in the cracking pressure underflow stream of safety valve, and the overflow energy consumption is big, and the oil temperature is high.42,43,44 are the hydraulic control guiding valve among Fig. 1.
The model utility content
At the shortcoming that exists in the above-mentioned prior art, technical problem to be solved in the utility model provides a kind of commutation function that not only has multi-way valve, and when regulating, low speed can have the load feedback multi-way valve of pressure compensation effect and power saving function according to operating cylinder under the different operating mode situations to how much being configured that hydraulic fluid pressure and oil mass require.
In order to solve the problems of the technologies described above, a kind of load feedback multi-way valve provided by the utility model is made up of control guiding valve group and inlet valve two-part.Control guiding valve group comprises guiding valve, shuttle valve, one-way valve, safety overflow valve and the oil duct of controlling each equipment oil cylinder; Inlet valve comprises system pressure setting safety overflow valve, unloading valve, defferential valve, back pressure valve, one-way valve, throttle valve and oil duct.Signal oil pocket and oil duct form the signal oil paths on each selector valve in the inlet valve, is the operating oil pressure to oil cylinder after the quilt selector valve throttling of handling that the signal oil pressure passes to inlet valve, enter the left end of unloading valve, defferential valve, it enters the induction cavity of back pressure valve through throttle orifice simultaneously; When operating a certain selector valve, the operating oil pressure that corresponding oil cylinder forms enters shuttle valve again by the oilhole entering signal oil pocket on the corresponding commutation valve rod, and steel ball is pushed open, and operating oil pressure is that the signal oil pressure is delivered to inlet valve; All during inoperation, the signal oil pocket communicates with back oil road on the valve all selector valves on each selector valve, the shuttle valve two ends of last a slice selector valve simultaneously and oil back chamber communicate the pressure release of whole signal oil circuit.
The beneficial effect of the load feedback multi-way valve that the utility model provides:
1) speed is stable, is not subjected to the influence of load, and can be with selector valve opening quantitative change realization proportionality velocity modulation;
2) in a certain little opening because selector valve restriction pressure reduction does not change with load size, and the steady-state fluid force that promptly acts on the commutation valve rod is a constant, and less, the driver controls speed governing and particularly finely tunes and be easy to.
3) during the little opening of selector valve, the chock pressure difference perseverance is 1.36MPa, and the relative oil cylinder operation of throttling energy consumption power is very little.
4) surplus pump oil is by differential pressure (overflow) valve oil sump tank, and oil pressure relief is a working pressure high 1.36MPa of operating oil pressure than oil cylinder of pump, and the output power of the relative pump of overflow energy consumption is little.
Description of drawings
Fig. 1 is a multi-way valve schematic diagram of the prior art.
Fig. 2 is the schematic diagram of multi-way valve of the present utility model.
When Fig. 3 is each selector valve attonity, inlet valve unloading condition effect structure principle chart.
When Fig. 4 is the little opening of certain selector valve, inlet valve differential pressure overflow situation effect structure principle chart.
31 is the 0.36MPa unloading valve in Fig. 2, and 32 is the 1.36MPa defferential valve, and 33 is the 1.05MPa back pressure valve, and 34 is 20MPa system pressure limit value relief valve, 35 hydraulic control guiding valves, 36 is shuttle valve, 37 is one-way valve, 38 is the 22MPa safety valve, and 39 are control guiding valve group, and 40 is inlet valve.
In Fig. 3 and Fig. 4,1 is unloading spring, and 2 is the differential pressure spring, 3 is the differential pressure valve rod, and 4 are the off-load valve rod, and 5 is oilhole, 6 is oilhole, and 7 is oil duct, and 8 are the off-load plunger, 9 is oilhole, and 10 is oil duct, and 11 is one-way valve, 12 is throttle valve, and 13 is oilhole, and 14 is throttle orifice, 15 is oil duct, and 16 is the signal oil pocket, and 17 is oilhole, 21 for advancing to control guiding valve, 22 is oil pumping chamber, and 23 are logical fuel tank chamber, and 24 refer to from the oil cylinder oil suction chamber, 25 is the back pressure valve induction cavity, 26 is back pressure valve, and 27 is the security of system valve, and 28 is the oil cylinder oil back chamber.
Embodiment
Below in conjunction with description of drawings embodiment of the present utility model is described in further detail, but present embodiment is not limited to the utility model, every employing analog structure of the present utility model and similar variation thereof all should be listed protection domain of the present utility model in.
The key problem in technology of the utility model multi-way valve is the structure and the action principle of inlet valve.The structure of inlet valve and action principle be as shown in Figure 3, Figure 4:
The action principle of inlet valve as shown in Figure 3 during each selector valve attonity.The all inoperation of each selector valve promptly are in the meta closing position, and oil pump pump oil enters inlet valve, come differential pressure valve rod 3 right-hand members through oilhole 5, oil duct 7, and after oil duct 10, oilhole 9 advanced plunger 8 right side oil pockets, pump oil began to boost.During each selector valve meta, signal oil circuit and oil cylinder oil back chamber 28 communicate, and oil cylinder oil back chamber 28 is connected by the throttling pore on the back pressure valve 26 14 with logical fuel tank chamber 23, and the signal oil cavity pressure is zero during each selector valve meta like this.When the pump oil pressure rose to 0.36MPa, plunger 8 moved to left the opening off-load of pump oil by forming between off-load valve rod 4 and the valve body by the effect promotion off-load valve rod 4 that oil pressure overcomes unloading spring 1.
The action principle of inlet valve was as shown in Figure 4 when the little opening throttling of a certain selector valve is worked when the little opening throttling of certain selector valve was worked, load makes oil cylinder work fluid produce oil pressure, come inlet valve signal oil pocket 16 by signal oil passage 15, by oil duct 17, act on the left end of differential pressure valve rod 3, off-load valve rod 4.The active force of operating oil pressure and unloading spring 1 promotes off-load valve rod 4 to the right, and the opening between off-load valve rod 4 and the valve body is closed, and stops off-load.When oil cylinder operating oil pressure during less than pump oil pressure 1.36MPa, the active force that the active force of this oil pressure and differential pressure spring 2 forms at differential pressure valve rod 3 right-hand members less than the pump oil pressure, differential pressure valve rod 3 is moved to the left, open the aperture 5 on the off-load valve rod 4, pump oil is by gap, aperture 6 oil sump tanks between aperture 5, differential pressure valve rod 3 and the off-load valve rod 4, and differential pressure valve rod 3 is at pump oil pressure p
P, oil cylinder working pressure P
vBetween pressure differential deltap P=P
P-P
vAnd remain on a certain equilibrium position under the effect of differential pressure spring 2, and unnecessary pump oil is laid down, and the pump oil pressure no longer rises.The spillway discharge of pump
A wherein
yOpen the area of aperture on the off-load valve rod for the differential pressure valve rod; P
PBe the pump oil pressure; C is a flow coefficient.
When oil cylinder because load increases operating oil pressure P
vDuring increase, differential pressure valve rod 3 left end active forces increase, and valve rod moves right, and makes aperture 4 overflow openings amount A
yReduce spillway discharge Q
yMoment reduces, and impels pump oil pressure P
PIncrease, make differential pressure valve rod 3 two ends pressure differential deltap P constant, valve rod is got back to the position before load increases again.
When oil cylinder reduces operating oil pressure P owing to load
vReduce, the active force of differential pressure valve rod 3 left ends reduces, and valve rod is moved to the left, and makes aperture 4 overflow openings amount A
yIncrease spillway discharge Q
yMoment increases, and impels pump oil pressure P
PReduce, make differential pressure valve rod 3 two ends pressure differential deltap P constant, valve rod is got back to load again and is reduced preceding position.
For different little openings, the pump duty that engine speed change is different, the position difference of differential pressure valve rod 3, i.e. spillway discharge difference, but because differential pressure spring 2 rigidity are little, the effect pressure reduction during the defferential valve overflow
Substantially constant.Wherein, F
0Precompression for the differential pressure spring; K is the differential pressure spring rate; Δ L is the differential pressure valve rod amount of moving on to (differential pressure amount of spring compression); D is the defferential valve shank diameter.
The differential pressure valve rod more than has been described, and operating pressure differential Δ P is constant substantially in all cases.Main flow by the selector valve restriction
Substantially constant.Wherein, A is the little opening orifice size of selector valve; C is a flow coefficient; Q
VBe flow by the selector valve restriction.Act on the steady-state fluid force F on the commutation valve rod
s=C
sΔ P is constant substantially.Wherein, C
sBe the steady-state fluid force coefficient; A, Δ P is the same.
Can obtain to draw a conclusion from above explanation:
1) when a certain little opening throttling of selector valve was worked, selector valve restriction pressure differential deltap P was by the flow Q of selector valve
V, act on the steady-state fluid force F of commutation on the valve rod
sDo not change, promptly can obtain stable cylinder action speed with the size of load and engine speed;
2) Q
VChange with selector valve opening area A direct ratio, get final product proportionality velocity modulation, and steady-state fluid force is invariable when minute opening, the fine setting performance is good;
3) stable chock pressure difference Δ P=1.36MPa, and numerical value is little, has reduced the restriction loss of valve.
The effect of back pressure valve also is essential in the utility model multi-way valve, its structure such as Fig. 3 or shown in Figure 4, and action principle is as follows:
Just can promote spring when back pressure valve induction cavity 25 pressure reach 1.05MPa, spool moves down, and opens the emptying oilhole, and the oil cylinder oil return is connected with the oil sump tank chamber.
When above the working principle of defferential valve being described, the oil cylinder operating oil pressure of coming inlet valve is that the signal oil pressure is higher than 1.05MPa, enters back pressure valve induction cavity 25 by Φ 0.7 throttle orifice, and spool is pushed away downwards, open the deoil oilhole in case chamber of oil cylinder oil return, this moment, the oil cylinder oil return did not have back pressure.
When oil cylinder moves with certain speed, during the pump shortage of oil, or when selector valve commutation back working pressure was not set up as yet, the oil cylinder oil return will lean on the power of building the pressure of self to open back pressure valve.The oil cylinder oil return is opened one-way valve 11 and is come back pressure valve induction cavity 25 and throttle orifice 12 places, by throttle orifice 12 to the repairing of signal oil circuit, to avoid the unloading valve off-load, having suppressed 1.05MPa pressure at induction cavity in addition opens back pressure valve, make the oil cylinder oil return case that deoils, this moment, the oil cylinder oil return had back pressure, impacted when preventing to move fast termination impact and commutation.
Back pressure valve falls also for oil cylinder soon and has brought convenience.The soil-shifting oil cylinder is by the perching knife downward rapid movement of conducting oneself with dignity, the big opening of selector valve, the pump shortage of oil is because the cylinder rod chamber oil return that exists of selector valve has little time to open back pressure valve, all oil returns are through the Fill valve cylinder rodless cavity repairing of deoiling, and this is the booster action that back pressure valve falls soon to perching knife.
On the back pressure valve body, spool upper end awl makes oil cylinder oil return and connected tank chamber normal open along the aperture that there are 4 Φ 1.2 at the place in addition.After on the one hand playing each selector valve and returning meta, it is zero-pressure that the oil cylinder oil return is not built the pressure, and makes also zero-pressure of the signal oil circuit that communicates with it, guarantees the unloading valve off-load.The soil-shifting valve is just connected two chambeies (rod chamber, rodless cavity) during blade float on the other hand, and and fuel tank obstructed, emptying when this oilhole can make perching knife float, when perching knife is floated downward from the fuel tank repairing.
For hydraulic control system that has accumulator or mechanical linkage control system, fall equipment after the parking, the oil cylinder oil return will be opened the back pressure valve oil return or be passed through its repairing.
Claims (1)
1, a kind of load feedback multi-way valve is made up of control guiding valve group and inlet valve two-part; Control guiding valve group comprises guiding valve, shuttle valve, one-way valve, safety overflow valve and the oil duct of controlling each equipment oil cylinder; Inlet valve comprises system pressure setting safety overflow valve, unloading valve, defferential valve, selector valve, back pressure valve, one-way valve, throttle valve and oil duct; It is characterized in that described selector valve and oil duct form the signal oil paths, the signal oil paths of described selector valve is connected with inlet valve, is connected with an end of unloading valve, defferential valve again, connects induction cavity simultaneously; Described selector valve also can be connected with shuttle valve by the oilhole on the commutation valve rod, is connected with inlet valve again; The signal oil pocket communicates with back oil road on the selector valve on the described selector valve, and described selector valve, shuttle valve two ends communicate with oil back chamber.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200520040516 CN2818871Y (en) | 2005-03-30 | 2005-03-30 | Feedback loading multi-path valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200520040516 CN2818871Y (en) | 2005-03-30 | 2005-03-30 | Feedback loading multi-path valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2818871Y true CN2818871Y (en) | 2006-09-20 |
Family
ID=37004927
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200520040516 Expired - Lifetime CN2818871Y (en) | 2005-03-30 | 2005-03-30 | Feedback loading multi-path valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2818871Y (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101993009A (en) * | 2009-08-24 | 2011-03-30 | 杨洁 | Follow-up damping control method for eliminating boarding inertial jitter and impact of construction crane |
| CN102678649A (en) * | 2012-06-07 | 2012-09-19 | 龙工（上海）桥箱有限公司 | Half integral load-sensing multiway valve |
| CN103771305A (en) * | 2014-01-16 | 2014-05-07 | 杭州爱知工程车辆有限公司 | Hydraulically-controlled proportional speed-adjusting energy-saving control system for overhead working automobile and control method thereof |
| CN104033436A (en) * | 2014-05-04 | 2014-09-10 | 柳州柳工液压件有限公司 | Load-sensitive multi-way reversing valve |
-
2005
- 2005-03-30 CN CN 200520040516 patent/CN2818871Y/en not_active Expired - Lifetime
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101993009A (en) * | 2009-08-24 | 2011-03-30 | 杨洁 | Follow-up damping control method for eliminating boarding inertial jitter and impact of construction crane |
| CN102678649A (en) * | 2012-06-07 | 2012-09-19 | 龙工（上海）桥箱有限公司 | Half integral load-sensing multiway valve |
| CN102678649B (en) * | 2012-06-07 | 2014-12-24 | 龙工（上海）精工液压有限公司 | Half integral load-sensing multiway valve |
| CN103771305A (en) * | 2014-01-16 | 2014-05-07 | 杭州爱知工程车辆有限公司 | Hydraulically-controlled proportional speed-adjusting energy-saving control system for overhead working automobile and control method thereof |
| CN103771305B (en) * | 2014-01-16 | 2016-04-20 | 杭州爱知工程车辆有限公司 | A kind of hydraulic control proportionality velocity modulation energy-saving control system for aerial platform and control method thereof |
| CN104033436A (en) * | 2014-05-04 | 2014-09-10 | 柳州柳工液压件有限公司 | Load-sensitive multi-way reversing valve |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CX01 | Expiry of patent term |
Expiration termination date: 20150330 Granted publication date: 20060920 |