CN203548373U - Servo hydraulic system - Google Patents

Servo hydraulic system Download PDF

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Publication number
CN203548373U
CN203548373U CN201320601942.6U CN201320601942U CN203548373U CN 203548373 U CN203548373 U CN 203548373U CN 201320601942 U CN201320601942 U CN 201320601942U CN 203548373 U CN203548373 U CN 203548373U
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CN
China
Prior art keywords
valve
hydraulic
oil
oil hydraulic
hydraulic pump
Prior art date
Application number
CN201320601942.6U
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Chinese (zh)
Inventor
朱飞
冉洋
陈康
龚勇
林正
丁文兵
于今
杨金华
杨昌林
Original Assignee
重庆市科学技术研究院
重庆朗正科技有限公司
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Priority to CN201320601942.6U priority Critical patent/CN203548373U/en
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Publication of CN203548373U publication Critical patent/CN203548373U/en

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Abstract

The utility model discloses a servo hydraulic system, which comprises a servo motor (1), a hydraulic pump (2), an oil tank (3), a proportional valve (4) and a hydraulic cylinder (5), wherein an energy accumulator (6) is arranged between the hydraulic pump (2) and the P end of the proportional valve (4), the energy accumulator (6) is connected to an oil inlet pipeline through a bypass pipe (17), an oil return pipeline between the T end of the proportional valve (4) and the oil tank (3) is connected to a balance valve (7) in series. According to the servo hydraulic system, the energy accumulator and the balance valve are respectively arranged on the oil inlet pipeline and the oil outlet pipeline, so that the pressure in the hydraulic cylinder is stabilized, a piston in the hydraulic cylinder is enabled to move at a constant speed in a progress process and a return process, the reliability is good and the output power is durable, so that the working efficiency of a welder is effectively improved, and the service life of a hydraulic pump is prolonged.

Description

Servo hydraulic system

Technical field

The utility model relates to hydraulic system, particularly a kind of servo hydraulic system that is applicable to friction-welding machine.

Background technique

The welding process of friction-welding machine is mainly to realize needed repeatedly pressurization in welding by the work of master cylinder, and the F.F. of worktable and slow-motion, and the performance that offers the hydraulic system of master cylinder operation power directly has influence on the quality of weld parts.The working principle of existing friction-welding machine hydraulic system is: by driven by motor oil hydraulic pump, for system is by pressure and flow, by the break-make of solenoid valve and solenoid valve and the adjustment of relief valve and relief valve, realize friction pressure and upsetting force again, fast forward speed can only lean on the oil pump flow of preliminary election to realize, immutable; The speed of process and backhaul is regulated by series flow control valve, controls master cylinder realization advance or retreat by solenoid directional control valve.Above system needs motor ceaselessly to turn round in the course of the work and in production preparation, produces at work a large amount of heats and consumes a large amount of energy simultaneously.Due to hydraulic system constantly oil temperature rise, and multiple hydraulic element participation work, therefore causes pressure and the instability of flow of whole system, has also affected welding quality simultaneously.

Model utility content

Technical problem to be solved in the utility model is to provide a kind of servo hydraulic system that keeps steady pressure.

The technical solution of the utility model is as follows:

A kind of servo hydraulic system, comprise actuating motor (1), oil hydraulic pump (2), fuel tank (3), Proportional valve (4) and oil hydraulic cylinder (5), described actuating motor (1) is connected with oil hydraulic pump (2), the P end of described Proportional valve (4) is by after in-line tandem hydraulic pump (2), be connected to fuel tank (3), the T end of this Proportional valve (4) is connected to fuel tank (3) by return line, the A end of described Proportional valve (4) is connected after the second hydraulic lock (13) by pipeline, be connected with the rodless cavity of oil hydraulic cylinder (5), the B end of solenoid directional control valve (4) is connected after the 3rd hydraulic lock (14) by pipeline, be connected with the rod chamber of oil hydraulic cylinder (5), between the P of described oil hydraulic pump (2) and solenoid directional control valve (4) end, be provided with accumulator (6), this accumulator (6) is connected with in-line by bypass tube (17), on the return line between the T of described Proportional valve (4) end and fuel tank (3), be in series with equilibrium valve (7).

Adopt above technological scheme, between the P of oil hydraulic pump and solenoid directional control valve end, be connected an accumulator, this accumulator is connected with in-line by bypass tube, when the pressure of welding machine operation is enough, the unnecessary power of being exported by oil hydraulic pump can not enter oil hydraulic cylinder again, hydraulic oil is back in bypass tube under pressure, and flow in accumulator, form one supplementary power, after meeting, pressure can turn off oil hydraulic pump, by the oil pressure in accumulator, meet the pressure in oil hydraulic cylinder is supplemented and regulated, guarantee the pressure stability of oil hydraulic cylinder, extend the working life of oil hydraulic pump simultaneously, on the return line between the T of described solenoid directional control valve end and fuel tank, be in series with equilibrium valve, when starting oil return in oil hydraulic cylinder, equilibrium valve can be stablized the pressure of reflux liquid force feed, and keeps the uniform motion of piston in hydraulic cylinder, guarantees the working efficiency of welding machine.

In order to prevent the backflow of hydraulic oil at in-line, and the better ftercompction effect guaranteeing to oil hydraulic cylinder, as preferably, on the in-line between the P of described Proportional valve (4) end and bypass tube (17), be in series with the first hydraulic lock (12), on in-line between bypass tube (17) and oil hydraulic pump (2), be in series with one-way valve (8), on described bypass tube (17), be in series with accumulator safety valve group (9).

In order to utilize better hydraulic pressure, prevent that hydraulic pressure fluctuation from becoming large, and better control the runnability between the each assembly of oil hydraulic circuit, as preferably, between described equilibrium valve (7) and fuel tank (3), be provided with relief valve (10), one end of this relief valve (10) is connected on the return line between equilibrium valve (7) and fuel tank (3), the other end of relief valve (10) is divided into two-way, one tunnel is connected on the in-line between oil hydraulic pump (2) and one-way valve (8), another road is connected with the one end of solenoid directional control valve (11), the other end of described solenoid directional control valve (11) is divided into two-way, one tunnel is connected with the first hydraulic lock (12), another Lu Yu tri-hydraulic lock (14) connect, between described solenoid directional control valve (11) and relief valve (10), be in series with reduction valve (15).

Too large in order to prevent the pressure surge of equilibrium valve, simultaneously also for the ease of the opening speed of regulator solution pressure cylinder piston, as preferably, on described equilibrium valve (7), be provided with modulating valve (16).

Beneficial effect: the utility model arranges respectively accumulator and equilibrium valve on in-line and fuel-displaced pipeline, pressure in can stabilizing solution cylinder pressure, and the piston in oil hydraulic cylinder is at the uniform velocity moved in process and backhaul process, good reliability, output power is lasting, can effectively improve welding machine working efficiency, and extend the working life of oil hydraulic pump.

Accompanying drawing explanation

Fig. 1 is structural representation of the present utility model.

In figure, 1, actuating motor; 2, oil hydraulic pump; 3, fuel tank; 4, Proportional valve; 5, oil hydraulic cylinder; 6, accumulator; 7, equilibrium valve; 8, one-way valve; 9, accumulator safety valve group; 10, relief valve; 11, solenoid directional control valve; 12, the first hydraulic lock; 13, the second hydraulic lock; 14, the 3rd hydraulic lock; 15, reduction valve; 16, modulating valve; 17, bypass tube; 18, piston.

Embodiment

Below in conjunction with drawings and Examples, the utility model is described in further detail:

As shown in Figure 1, actuating motor 1 is connected with oil hydraulic pump 2, by actuating motor 1, drives oil hydraulic pump 2 to work.The P end of Proportional valve 4, by after in-line tandem hydraulic pump 2, is connected to fuel tank 3.Between the P of described oil hydraulic pump 2 and Proportional valve 4 end, be provided with accumulator 6, this accumulator 6 is connected with in-line by bypass tube 17, and on bypass tube 17, is in series with accumulator safety valve group 9.On the in-line between the P of described Proportional valve 4 end and bypass tube 17, be in series with the first hydraulic lock 12, on the in-line between bypass tube 17 and oil hydraulic pump 2, be in series with one-way valve 8.The A end of described Proportional valve 4 is connected after the second hydraulic lock 13 by pipeline, is connected with the rodless cavity of oil hydraulic cylinder 5, and the B end of Proportional valve 4 is connected after the 3rd hydraulic lock 14 by pipeline, is connected with the rod chamber of oil hydraulic cylinder 5.

As shown in Figure 1, the T end of Proportional valve 4 is connected to fuel tank 3 by return line, on the return line between the T of described Proportional valve 4 end and fuel tank 3, be in series with equilibrium valve 7, on described equilibrium valve 7, be provided with modulating valve 16, between this equilibrium valve 7 and fuel tank 3, be provided with relief valve 10, one end of this relief valve 10 is connected on the return line between equilibrium valve 7 and fuel tank 3, the other end of relief valve 10 is divided into two-way, one tunnel is connected on the in-line between oil hydraulic pump 2 and one-way valve 8, another road is connected with one end of solenoid directional control valve 11, the other end of described solenoid directional control valve 11 is divided into two-way, one tunnel is connected with the first hydraulic lock 12, another Lu Yu tri-hydraulic lock 14 connect, between described solenoid directional control valve 11 and relief valve 10, be in series with reduction valve 15.

Working principle of the present utility model is as follows:

During friction-welding machine operation, be divided into successively main tapping process, compress welding and three steps of main tapping backhaul, when the operation first step is main tapping process, by actuating motor 1, drive oil hydraulic pump 2, described oil hydraulic pump 2 is extracted hydraulic oil out from fuel tank 3, hydraulic oil is along in-line successively process one-way valve 8 and the first hydraulic lock 12, through the P of Proportional valve 4 end, enter Proportional valve 4 again, hydraulic oil is entered the rodless cavity of oil hydraulic cylinder 5 through the second hydrovalve 13 by the A end of Proportional valve 4, under hydraulic pressure, piston 18 in oil hydraulic cylinder 5 moves downward, the piston rod of piston 18 lower ends drives main tapping (not marking in figure) also to move down, and arrive operative position, now, oil hydraulic cylinder 5 keeps constant voltage, unnecessary hydraulic oil cannot enter in oil hydraulic cylinder 5, because one-way valve 8 has stoped hydraulic oil backflow, hydraulic oil only has through bypass tube 17 and enters accumulator safety valve group 9, when reaching safety pressure, enter accumulator 6, after accumulator 6 fullchargings, when system oil-way pressure is less than rated pressure, accumulator 6 is mended supply system again.

And then the second step that brings into operation compresses welding, due to the surface of contact impact of welding position, in the main tapping welding process of welding machine, there is the phenomenon of fluctuation up and down, this also makes piston have upper and lower displacement in oil hydraulic cylinder 5, also can there is variation repeatedly in the pressure of rodless cavity and rod chamber, because oil hydraulic pump 2 no longer provides hydraulic oil, because one-way valve 8 has cut off the reflux line of in-line, now, just by accumulator 6, by the first hydraulic lock 12, provide pressure to supplement and regulate, the signal providing by pressure transducer (not marking in figure), so that resize ratio valve 4 valve core opening sizes, adjust the motion of piston 18 simultaneously.

Hydraulic oil in oil hydraulic cylinder 5 rod chambers can through the 3rd hydraulic lock 14 out after through Proportional valve 4, the electric current of the release of 3, three hydraulic lock of the direct oil sump tank of equilibrium valve 7 12,13,14 of flowing through and the locked A by solenoid directional control valve 11 positions, left and right, B, P, tetra-contacts of T is connected to control.

Whole welding process keeps the oil pressure balance in welding process by above oil circuit and relevant control circuit.

After having welded, moving the 3rd step is main tapping backhaul, at this moment the P of Proportional valve 4 end is communicated with B end, A end is connected with T end, actuating motor 1 drives oil hydraulic pump 2 to in-line fuel feeding, hydraulic oil flows out by the B end of Proportional valve 4 rod chamber that enters oil hydraulic cylinder 5 through the 3rd selector valve 14, under pressure, piston 18 moves upward, and drive main tapping to be moved upwards up to standby position, simultaneously, the hydraulic oil of oil hydraulic cylinder 5 interior rodless cavities is through the second hydraulic lock 13, the A-T end of Proportional valve 4, flow into equilibrium valve 7, under the effect of modulating valve 16, hydraulic oil is back to fuel tank 3 with stable pressure.

In mode of execution of the present utility model, undeclared part is consistent with prior art, does not repeat them here.

Claims (4)

1. a servo hydraulic system, comprise actuating motor (1), oil hydraulic pump (2), fuel tank (3), Proportional valve (4) and oil hydraulic cylinder (5), described actuating motor (1) is connected with oil hydraulic pump (2), the P end of described Proportional valve (4) is by after in-line tandem hydraulic pump (2), be connected to fuel tank (3), the T end of this Proportional valve (4) is connected to fuel tank (3) by return line, the A end of described Proportional valve (4) is connected after the second hydraulic lock (13) by pipeline, be connected with the rodless cavity of oil hydraulic cylinder (5), the B end of Proportional valve (4) is connected after the 3rd hydraulic lock (14) by pipeline, be connected with the rod chamber of oil hydraulic cylinder (5), it is characterized in that: between the P of described oil hydraulic pump (2) and solenoid directional control valve (4) end, be provided with accumulator (6), this accumulator (6) is connected with in-line by bypass tube (17), on the return line between the T of described Proportional valve (4) end and fuel tank (3), be in series with equilibrium valve (7).
2. servo hydraulic system according to claim 1, it is characterized in that: on the in-line between the P of described Proportional valve (4) end and bypass tube (17), be in series with the first hydraulic lock (12), on in-line between bypass tube (17) and oil hydraulic pump (2), be in series with one-way valve (8), on described bypass tube (17), be in series with accumulator safety valve group (9).
3. servo hydraulic system according to claim 2, it is characterized in that: between described equilibrium valve (7) and fuel tank (3), be provided with relief valve (10), one end of this relief valve (10) is connected on the return line between equilibrium valve (7) and fuel tank (3), the other end of relief valve (10) is divided into two-way, one tunnel is connected on the in-line between oil hydraulic pump (2) and one-way valve (8), another road is connected with the one end of solenoid directional control valve (11), the other end of described solenoid directional control valve (11) is divided into two-way, one tunnel is connected with the first hydraulic lock (12), another Lu Yu tri-hydraulic lock (14) connect, between described solenoid directional control valve (11) and relief valve (10), be in series with reduction valve (15).
4. servo hydraulic system according to claim 3, is characterized in that: on described equilibrium valve (7), be provided with modulating valve (16).
CN201320601942.6U 2013-09-27 2013-09-27 Servo hydraulic system CN203548373U (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201320601942.6U CN203548373U (en) 2013-09-27 2013-09-27 Servo hydraulic system

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201320601942.6U CN203548373U (en) 2013-09-27 2013-09-27 Servo hydraulic system

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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104006015A (en) * 2014-05-22 2014-08-27 南通东海机床制造有限公司 Pressure maintaining and speed stabilizing hydraulic system of hydraulic machine
CN104089064A (en) * 2014-05-26 2014-10-08 武汉大禹阀门股份有限公司 Photovoltaic hydraulic control device of valve
CN104196778A (en) * 2014-09-22 2014-12-10 北京布鲁斯格环保科技有限公司 Hydraulic servo device
CN106079514A (en) * 2016-08-22 2016-11-09 仪征雄伟机械科技有限公司 A kind of auto parts and components air-bend die stable-pressure device
CN106181018A (en) * 2016-07-14 2016-12-07 西北工业大学 full hydraulic friction stir welding machine and control method thereof
CN106351887A (en) * 2016-10-09 2017-01-25 江苏万达丰重工机械有限公司 Hydraulic driving device
CN107013534A (en) * 2017-04-27 2017-08-04 机械科学研究院哈尔滨焊接研究所 Aero-engine key component inertia friction welder fluid power system
CN109030195A (en) * 2018-08-02 2018-12-18 河北工业大学 Test device for different-thickness part fatigue test
CN109210026A (en) * 2018-08-02 2019-01-15 清华大学 Hydraulic loading system for the load of a variety of load

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104006015A (en) * 2014-05-22 2014-08-27 南通东海机床制造有限公司 Pressure maintaining and speed stabilizing hydraulic system of hydraulic machine
CN104089064A (en) * 2014-05-26 2014-10-08 武汉大禹阀门股份有限公司 Photovoltaic hydraulic control device of valve
CN104196778A (en) * 2014-09-22 2014-12-10 北京布鲁斯格环保科技有限公司 Hydraulic servo device
CN106181018A (en) * 2016-07-14 2016-12-07 西北工业大学 full hydraulic friction stir welding machine and control method thereof
CN106181018B (en) * 2016-07-14 2018-04-03 西北工业大学 Full hydraulic friction stir welding machine and its control method
CN106079514A (en) * 2016-08-22 2016-11-09 仪征雄伟机械科技有限公司 A kind of auto parts and components air-bend die stable-pressure device
CN106351887A (en) * 2016-10-09 2017-01-25 江苏万达丰重工机械有限公司 Hydraulic driving device
CN107013534A (en) * 2017-04-27 2017-08-04 机械科学研究院哈尔滨焊接研究所 Aero-engine key component inertia friction welder fluid power system
CN107013534B (en) * 2017-04-27 2019-10-01 机械科学研究院哈尔滨焊接研究所 Aero-engine key component inertia friction welder fluid power system
CN109030195A (en) * 2018-08-02 2018-12-18 河北工业大学 Test device for different-thickness part fatigue test
CN109210026A (en) * 2018-08-02 2019-01-15 清华大学 Hydraulic loading system for the load of a variety of load

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GR01 Patent grant
C14 Grant of patent or utility model
CF01 Termination of patent right due to non-payment of annual fee

Granted publication date: 20140416

Termination date: 20160927

CF01 Termination of patent right due to non-payment of annual fee