CN102913493A - Hydraulic system capable of independently adjusting speed by adopting two pressure compensators - Google Patents
Hydraulic system capable of independently adjusting speed by adopting two pressure compensators Download PDFInfo
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- CN102913493A CN102913493A CN2012103281686A CN201210328168A CN102913493A CN 102913493 A CN102913493 A CN 102913493A CN 2012103281686 A CN2012103281686 A CN 2012103281686A CN 201210328168 A CN201210328168 A CN 201210328168A CN 102913493 A CN102913493 A CN 102913493A
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Abstract
The invention discloses a hydraulic system capable of independently adjusting speed by adopting two pressure compensators. The hydraulic system comprises an oil filter (1), an overflow valve (2), a quantification pump (3), a pressure compensator I (4), a pressure compensator II (7), a proportion reversing valve (5), a shuttle valve (6), a unidirectional valve (8) and a bidirectional motor (9), wherein the pressure compensator I (4) is arranged in front of an oil inlet P2 of the proportion reversing valve (5); the pressure compensator II (7) is arranged behind an oil outlet B4 of the proportion reversing valve (5); an oil outlet B3 of the pressure compensator I (4) is communicated with the oil inlet P2 of the proportion reversing valve (5); an oil outlet A4 of the proportion reversing valve (5) is communicated with an oil inlet A5 of the shuttle valve (6) and an oil inlet A8 of the bidirectional motor (9) respectively; and an oil outlet B4 of the proportion reversing valve (5) is communicated with an oil inlet B5 of the shuttle valve (6), an oil inlet A7 of the unidirectional valve (7) and an oil outlet B6 of the pressure compensator II (7).
Description
Technical field
The present invention relates to the hydraulics field, relate in particular to the two pressure compensator independence speed-regulating hydraulic systems of a kind of employing.
Background technique
Hydraulic control technology has a wide range of applications in engineering machinery field, such as truck crane, and excavator etc.Adopt the combination of pressure compensator and proportional direction valve, thereby the control that realizes hydraulic actuator speed has obtained good application.The position of pressing force compensator, pressure compensation scheme are divided into the upstream pressure compensation, downstream pressure compensation, corresponding pressure compensator of load in the General System.The negative loading speed stationarity control problem of large inertia is of long duration, especially in the truck crane field, the hydraulic wireline winch field, to load on outlet plenum and produce high back pressure and prevent final controlling element stall in order to overcome, traditional hydraulic system employing provides back pressure in the scheme that the final controlling element oil outlet arranges equilibrium valve, prevents final controlling element stall.In order to take into account speed adjusting performance, usually need to compensate at inlet's plus-pressure compensator, but the parameter matching of pressure compensator and equilibrium valve is improper the easy unstability of system.The design has proposed the hydraulic system of the two pressure compensator independence speed governing of a kind of novel employing, is pressed for the negative load of large inertia provides by pressure compensator, takes into account simultaneously speed-regulating function.
Summary of the invention
Technical problem to be solved by this invention provides a kind of hydraulic system that adopts two pressure compensator independence speed governing, the invention belongs in the oil-feed of reversing motor and go out the hydraulic speed regulation system that oil return line arranges respectively pressure compensator, finish bidirectional speed control by pressure compensator and proportional direction valve, the required pressure under the negative load behavior is provided simultaneously; Thereby solved the negative load bidirectional speed control problem of large inertia.
In order to solve the problems of the technologies described above, the invention provides a kind of hydraulic system that adopts two pressure compensator independence speed governing, this hydraulic system comprises oil purifier, relief valve, metering pump, pressure compensator I, pressure compensator II, proportional reversing valve, shuttle valve, one-way valve and reversing motor;
Before the oil inlet P 2 of proportional direction valve, the pressure compensator I is set, behind proportional direction valve oil outlet B4, the pressure compensator II is set;
The filler opening A1 of oil purifier leads to fuel tank, the filler opening A2 of the logical metering pump of the oil outlet B1 of oil purifier; The oil outlet B2 of metering pump is connected with the oil inlet P 1 of relief valve, the filler opening A3 of pressure compensator I respectively; The oil outlet T1 of relief valve communicates with fuel tank, the oil inlet P 2 of the logical proportional direction valve of the oil outlet B3 of pressure compensator I, the oil return inlet T 2 logical fuel tanks of proportional direction valve; The oil outlet A4 of proportional direction valve communicates with the filler opening A5 of shuttle valve and the filler opening A8 of reversing motor respectively, the oil outlet B4 of proportional direction valve communicates with the filler opening B5 of shuttle valve, the filler opening A7 of one-way valve and the oil outlet B6 of pressure compensator II respectively, the oil outlet C2 of shuttle valve communicates with the control port C1 of pressure compensator I, the oil outlet B8 of reversing motor communicates with the oil outlet B7 of one-way valve, the filler opening A6 of pressure compensator II respectively, and the control port C3 of pressure compensator II leads to fuel tank.
Improvement as the hydraulic system of the two pressure compensator independence speed governing of employing of the present invention: adopt pressure is higher among the oil outlet A4 of shuttle valve feedback proportional direction valve and the oil outlet B4 pressure oil to the pilot pressure hydraulic fluid port C1 of pressure compensator I.
Further improvement as the hydraulic system of the two pressure compensator independence speed governing of employing of the present invention: the set pressure value of pressure compensator I is greater than the set pressure of pressure compensator II; Thereby guarantee under different industry controls, to have respectively different pressure compensators to work.That is, when industry control one (industry control A as described in Figure 2), the pressure compensator I works; When operating mode two (industry control B as described in Figure 2), the pressure compensator II works.
In the present invention, set pressure value that must can not setting pressure compensator I is less than the set pressure value of pressure compensator II, otherwise, all only have the pressure compensator I at operating mode A and operating mode B and work.
In the present invention, all component (oil purifier, relief valve, metering pump, pressure compensator I, pressure compensator II, proportional reversing valve, shuttle valve, one-way valve and reversing motor) are conventional products, all can obtain by commercial form.
Hydraulic system of the present invention is arranged as respectively after and before the valve (described valve is proportional direction valve) by two pressure compensators and realizes the adjusting of final controlling element speed.
The present invention compares with technical background, has following beneficial effect:
1), adopts the controlling technology of velocity that two pressure compensators are set in oil circuit, under two different operating modes such as Fig. 2, the pressure compensator that works is also different, has realized the stability of the negative load bidirectional speed governing of large inertia, strengthens the adaptive capacity to load.
2), adopt the scheme of adding the opposite one-way valve of through-flow direction in the bypass of pressure compensator II, thereby make the pressure compensator II under operating mode B shown in Figure 2, realize the final controlling element speed governing providing back pressure for system on the other hand on the one hand.When final controlling element was operated in operating mode A, one-way valve worked, and this moment, the pressure compensator II was inoperative.
3), adopt the scheme that before the proportional direction valve filler opening, increases the pressure compensator I, control-oil pressure to take from the maximum pressure of two oil outlet A4, B4 of the proportional direction valve of shuttle valve feedback.Thereby the control of the speed when realizing that the final controlling element load is identical with moving direction.
4), the set pressure value of pressure compensator I is greater than the set pressure value of pressure compensator II, thereby the pressure compensator II is worked under operating mode B, rely on the pressure compensator II that back pressure is provided, and in the speed regulation process, the valve port of pressure compensator I is played the speed governing effect that can't afford to drive.
Description of drawings
Below in conjunction with accompanying drawing the specific embodiment of the present invention is described in further detail.
Fig. 1 is structure principle chart of the present invention;
Among Fig. 1: 1, oil purifier, 2, relief valve, 3, metering pump, 4, the pressure compensator I, 5, proportional reversing valve, 6, shuttle valve, 7, the pressure compensator II, 8, one-way valve, 9, reversing motor;
Fig. 2 is the operating mode schematic diagram that the present invention is directed to, and load is large inertia load, and the direction of load is constant all the time, and operating mode A represents that load direction is opposite with the sense of rotation of reversing motor, and operating mode B represents that load direction is identical with the sense of rotation of reversing motor.
Embodiment
Embodiment 1, a kind of hydraulic system that adopts two pressure compensator independence speed governing as described in Figure 1, comprise oil purifier 1, relief valve 2, metering pump 3, pressure compensator I 4, pressure compensator II 7, proportional reversing valve 5, shuttle valve 6, one-way valve 8 and reversing motor 9.
The filler opening A1 of oil purifier 1 leads to fuel tank, and the filler opening A2 of the logical metering pump 3 of the oil outlet B1 of oil purifier 1, the oil outlet B2 of metering pump 3 lead to respectively the oil inlet P 1 of relief valve 2 and the filler opening A3 of pressure compensator 4 I, and the oil outlet T1 of relief valve 2 communicates with fuel tank.The oil inlet P 2 of the logical proportional direction valve 5 of the oil outlet B3 of pressure compensator I 4, the oil return inlet T 2 logical fuel tanks of proportional direction valve 5, the oil outlet A4 of proportional direction valve 5 respectively with the filler opening A5 of shuttle valve 6, the filler opening A8 of reversing motor 9 communicates, the oil outlet B4 of proportional direction valve 5 respectively with the filler opening B5 of shuttle valve 6, the filler opening A7 of one-way valve 8, the oil outlet B6 of pressure compensator II 7 communicates, the oil outlet C2 of shuttle valve 6 communicates with the control port C1 of pressure compensator I 4, the oil outlet B8 of reversing motor 9 respectively with the oil outlet B7 of one-way valve 8, the filler opening A6 of pressure compensator 7 II communicates, and the control port C3 of pressure compensator II 7 leads to fuel tank.
The remarks explanation: above-mentioned fuel tank all refers to same fuel tank, shows 2 fuel tanks in Fig. 1, only is because the convenience of drawing.
Working procedure of the present invention is as follows:
Industry control one,
Be under the large inertia load in system, proportional direction valve 5 left side electromagnet get when electric, and proportional direction valve 5 is operated in left position, and this moment, the operating mode of hydraulic work system was operating mode A shown in Figure 2.Hydraulic oil enters oil purifier 1 from the filler opening A1 of fuel tank by oil purifier 1 and filters, and the hydraulic oil after the filtration enters in the metering pump 3 by the oil outlet B1 of oil purifier 1, the filler opening A2 of metering pump 3 successively, the oil outlet B2 output high pressure liquid force feed of metering pump 3.
The high-pressure and hydraulic oil content that flows out from the oil outlet B2 of metering pump 3 becomes two-part:
A part enters in the pressure compensator I 4 by the filler opening A3 of pressure compensator I 4, and pressure compensator I 4 provides corresponding compensatory pressure according to its oil outlet B3 with the pressure reduction of control port C1.
Another part enters to relief valve 2 by the oil inlet P 1 of relief valve 2, plays the effect of safe overflow, and the hydraulic oil in the relief valve 2 is back to fuel tank by the oil outlet T1 of relief valve 2.
Hydraulic oil in the pressure compensator I 4 is after the oil outlet B3 outflow of pressure compensator 4 I, and the oil inlet P 2 of passing ratio directional control valve 5 enters in the proportional direction valve 5; At this moment, the oil inlet P 2 of proportional direction valve 5 communicates with oil outlet B4, and oil return inlet T 2 and the oil outlet A4 of proportional direction valve 5 communicate.Make reversing motor 9 be operated in operating mode A.Simultaneously because the oil outlet B4 of proportional direction valve 5 is high pressure, the filler opening B5 of shuttle valve 6 communicates with oil outlet C2, the control port C1 of pressure compensator I 4 communicates with the oil outlet C2 of shuttle valve 6, under the effect of pressure compensator I 4, guarantee that the oil inlet P 2 of proportional direction valve 5 and the pressure reduction of oil outlet B4 are the pressore setting (that is, making the pressure reduction of the oil inlet P 2 of proportional direction valve 5 and the pressure reduction of oil outlet B4=pressure compensator I 4 oil outlet B3 and control port C1) of pressure compensator I 4.The flow that proportional direction valve 5 passes through is only relevant with the valve port opening of proportional direction valve 5.From the oil outlet B4 stable output flow of proportional direction valve 5, thereby the speed that realizes operating mode A is steadily controlled.
The hydraulic oil that flows out from the oil outlet B4 of proportional direction valve 5 is divided into 2 parts:
First portion such as epimere are described by the control port C1 of shuttle valve 6 to pressure compensator I 4, thereby realize the compensatory pressure control of pressure compensator I 4.
The oil outlet B6 of the logical pressure compensator II 7 of another part and the filler opening A7 of one-way valve 8 because the oil outlet B4 of proportional direction valve 5 is output as high pressure oil, and can not flow to filler opening A6 by oil outlet B6 at pressure compensator II 7 interior hydraulic oil; Therefore, hydraulic oil can only enter from the filler opening A7 of one-way valve 8 in the one-way valve 8 and then flow out from oil outlet B7, plays the one-way conduction effect.
The high pressure liquid force feed that flows out from the oil outlet B7 of one-way valve 8 enters the oil outlet B8 of reversing motor 9, drives reversing motor 9 rotations.Low-pressure hydraulic oil flows out oil outlet A4 and the oil return inlet T 2 backflow fuel tanks of process proportional direction valve 5 from the filler opening A8 of reversing motor 9.
Under this industry control, the sense of rotation of load is opposite with the sense of rotation of reversing motor 9; Thereby realize the velocity-stabilization control (shown in the operating mode A among Fig. 2) of operating mode one.
Industry control two,
Be under the large inertia load in system, proportional direction valve 5 the right electromagnet get when electric, and proportional direction valve 5 is operated in right position, and this moment, the operating mode of hydraulic work system was operating mode B shown in Figure 2.Hydraulic oil enters oil purifier 1 from the filler opening A1 of fuel tank by oil purifier 1 and filters, and the hydraulic oil after the filtration enters in the metering pump 3 by the oil outlet B1 of oil purifier 1, the filler opening A2 of metering pump 3 successively, the oil outlet B2 output high pressure liquid force feed of metering pump 3.
The high-pressure and hydraulic oil content that flows out from the oil outlet B2 of metering pump 3 becomes two-part:
A part enters in the pressure compensator I 4 by the filler opening A3 of pressure compensator I 4, and pressure compensator I 4 provides corresponding compensatory pressure according to its oil outlet B3 with the pressure reduction of control port C1.
Another part enters to relief valve 2 by the oil inlet P 1 of relief valve 2, plays the effect of safe overflow, and the hydraulic oil in the relief valve 2 is back to fuel tank by the oil outlet T1 of relief valve 2.
Hydraulic oil in the pressure compensator I 4 is after the oil outlet B3 outflow of pressure compensator I 4, and the oil inlet P 2 of passing ratio directional control valve 5 enters in the proportional direction valve 5; At this moment, the oil inlet P 2 of proportional direction valve 5 communicates with oil outlet A4, and oil return inlet T 2 and the oil outlet B4 of proportional direction valve 5 communicate.Make reversing motor 9 be operated in operating mode B.Simultaneously because the oil outlet A4 of proportional direction valve 5 is high pressure, the filler opening A5 of shuttle valve 6 communicates with oil outlet C2, the control port C1 of pressure compensator I 4 communicates with the oil outlet C2 of shuttle valve 6, under the effect of pressure compensator I 4, the oil inlet P 2 that guarantees proportional direction valve 5 and the pressure reduction of oil outlet A4 are no more than the pressore setting (that is, making the set pressure value of the pressure reduction of the oil inlet P 2 of proportional direction valve 5 and the pressure reduction of oil outlet A4=pressure compensator I 4 oil outlet B3 and control port C1≤pressure compensator I 4) of pressure compensator I 4.
The high pressure liquid force feed that flows out from the oil outlet A4 of proportional direction valve 5 enters in the reversing motor 9 from the filler opening A8 of reversing motor 9, thereby drives the action that oil hydraulic motor is finished operating mode B.
Under this industry control, the sense of rotation of load is identical with the sense of rotation of reversing motor 9; Thereby realize the control of the negative load of large inertia.
The hydraulic oil that flows out from the oil outlet B8 of reversing motor 9 flows to the oil outlet B7 of one-way valve 8 and the filler opening A6 of pressure compensator II 7.The one-way conduction effect of one-way valve 8 determines that hydraulic oil can not pass through one-way valve 8, and therefore whole hydraulic oil enter in the pressure compensator II 7 from the filler opening A6 of pressure compensator II 7.Pressure compensator II 7 is according to the pressure difference of the oil return inlet T 2 of the pressure of oil outlet B6 and proportional direction valve 5 pressure that affords redress, and this compensatory pressure also provides large inertia to bear the required back pressure of load behavior B simultaneously.
The hydraulic oil that flows out from pressure compensator II 7 flows in the proportional direction valve 5 from the oil outlet B4 of proportional direction valve 5, because this moment, oil outlet B4 and the oil return inlet T 2 of proportional direction valve 5 communicated, pressure compensator II 7 guarantees that pressure reduction between these two hydraulic fluid ports is not more than its set pressure value (that is, making the set pressure value of the pressure reduction of the oil outlet B4 of proportional direction valve 5 and the pressure reduction of oil return inlet T 2=pressure compensator II 7 oil outlet B6 and control port C3≤pressure compensator II 7).Think that the flow that flows into from proportional direction valve 5 equals the flow that proportional flow control valve 5 flows out owing to can be similar in the system, the valve port of proportional direction valve 5 is approximately symmetrical valve port, and the corresponding flow of any opening amount of valve is only relevant with the set pressure of two pressure compensators (pressure compensator I 4, pressure compensator II 7).The set pressure value of setting pressure compensator II 7 is less than the set pressure value of pressure compensator I 4 at this moment, and flow system flow is just determined by pressure compensator II 7 and proportional direction valve 5 actings in conjunction.Realize the stable speed governing under the operating mode B, pressed for the negative load of large inertia provides simultaneously.
The hydraulic oil backflow fuel tank that is flowed out by the oil return inlet T 2 of proportional direction valve 5.
At last, it is also to be noted that, what more than enumerate only is several specific embodiments of the present invention.Obviously, the invention is not restricted to above embodiment, many distortion can also be arranged.All distortion that those of ordinary skill in the art can directly derive or associate from content disclosed by the invention all should be thought protection scope of the present invention.
Claims (3)
1. adopt the hydraulic system of two pressure compensator independence speed governing, it is characterized in that: described hydraulic system comprises oil purifier (1), relief valve (2), metering pump (3), pressure compensator I (4), pressure compensator II (7), proportional reversing valve (5), shuttle valve (6), one-way valve (8) and reversing motor (9);
Pressure compensator I (4) is set before the oil inlet P 2 of proportional direction valve (5), behind proportional direction valve (5) oil outlet B4, pressure compensator II (7) is set;
The filler opening A1 of oil purifier (1) leads to fuel tank, the filler opening A2 of the logical metering pump (3) of the oil outlet B1 of oil purifier (1); The oil outlet B2 of metering pump (3) is connected with the oil inlet P 1 of relief valve (2), the filler opening A3 of pressure compensator I (4) respectively; The oil outlet T1 of relief valve (2) communicates with fuel tank, the oil inlet P 2 of the logical proportional direction valve (5) of the oil outlet B3 of pressure compensator I (4), the oil return inlet T 2 logical fuel tanks of proportional direction valve (5); The oil outlet A4 of proportional direction valve (5) communicates with the filler opening A5 of shuttle valve (6) and the filler opening A8 of reversing motor (9) respectively, the oil outlet B4 of proportional direction valve (5) respectively with the filler opening B5 of shuttle valve (6), the oil outlet B6 of the filler opening A7 of one-way valve (7) and pressure compensator II (7) communicates, the oil outlet C2 of shuttle valve (6) communicates with the control port C1 of pressure compensator I (4), the oil outlet B8 of reversing motor (9) respectively with the oil outlet B7 of one-way valve (8), the filler opening A6 of pressure compensator II (7) communicates, and the control port C3 of pressure compensator II (7) leads to fuel tank.
2. the hydraulic system of the two pressure compensator independence speed governing of employing according to claim 1 is characterized in that: adopt pressure is higher among the oil outlet A4 of shuttle valve (6) feedback proportional direction valve (5) and the oil outlet B4 pressure oil to the pilot pressure hydraulic fluid port C1 of pressure compensator I (4).
3. the hydraulic system of the two pressure compensator independence speed governing of employing according to claim 2 is characterized in that:
The set pressure value of pressure compensator I (4) is greater than the set pressure of pressure compensator II (7); Thereby guarantee under different industry controls, to have respectively different pressure compensators to work.
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103953593A (en) * | 2014-05-13 | 2014-07-30 | 南京高精船用设备有限公司 | Hydraulic control device for adjustable pitch side thrusting of ship |
| CN103953619A (en) * | 2014-04-25 | 2014-07-30 | 哈尔滨飞机工业集团有限责任公司 | Variable frequency speed control hoisting device for helicopter |
| CN106315442A (en) * | 2016-08-26 | 2017-01-11 | 武汉船用机械有限责任公司 | Automatic cable arranging hydraulic control system for cable dragging machine |
| CN107905666A (en) * | 2017-11-07 | 2018-04-13 | 宁波汉商液压有限公司 | A kind of hydraulic system for controlling automobile power back door |
| CN109019381A (en) * | 2018-09-14 | 2018-12-18 | 杭州流控机器制造有限公司 | A kind of negative load control loop of the hydraulic motor for elevator winch and its method |
| CN109611391A (en) * | 2018-12-10 | 2019-04-12 | 湖南五新隧道智能装备股份有限公司 | A kind of concrete spraying vehicle spray head swipes motor governing system |
| CN112901568A (en) * | 2021-01-26 | 2021-06-04 | 武汉船用机械有限责任公司 | Variable-pitch hydraulic system of controllable-pitch propeller and application method of variable-pitch hydraulic system |
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Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103953619A (en) * | 2014-04-25 | 2014-07-30 | 哈尔滨飞机工业集团有限责任公司 | Variable frequency speed control hoisting device for helicopter |
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| CN103953593B (en) * | 2014-05-13 | 2016-08-24 | 南京高精船用设备有限公司 | Hydraulic control device is pushed away for boats and ships adjustable pitch side |
| CN106315442A (en) * | 2016-08-26 | 2017-01-11 | 武汉船用机械有限责任公司 | Automatic cable arranging hydraulic control system for cable dragging machine |
| CN107905666A (en) * | 2017-11-07 | 2018-04-13 | 宁波汉商液压有限公司 | A kind of hydraulic system for controlling automobile power back door |
| CN109019381A (en) * | 2018-09-14 | 2018-12-18 | 杭州流控机器制造有限公司 | A kind of negative load control loop of the hydraulic motor for elevator winch and its method |
| CN109611391A (en) * | 2018-12-10 | 2019-04-12 | 湖南五新隧道智能装备股份有限公司 | A kind of concrete spraying vehicle spray head swipes motor governing system |
| CN112901568A (en) * | 2021-01-26 | 2021-06-04 | 武汉船用机械有限责任公司 | Variable-pitch hydraulic system of controllable-pitch propeller and application method of variable-pitch hydraulic system |
| CN112901568B (en) * | 2021-01-26 | 2023-07-21 | 武汉船用机械有限责任公司 | Pitch-variable hydraulic system of pitch-variable propeller and application method thereof |
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Application publication date: 20130206 |