CN1986332A - Directly driven volume controlled electro-hydraulic servo rotating-vane helm - Google Patents
Directly driven volume controlled electro-hydraulic servo rotating-vane helm Download PDFInfo
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- CN1986332A CN1986332A CN 200510127358 CN200510127358A CN1986332A CN 1986332 A CN1986332 A CN 1986332A CN 200510127358 CN200510127358 CN 200510127358 CN 200510127358 A CN200510127358 A CN 200510127358A CN 1986332 A CN1986332 A CN 1986332A
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Abstract
The present invention is directly driven volume controlled electro-hydraulic servo rotating vane helm, and belongs to the field of electro-hydraulic servo technology. Technologically, the electro-hydraulic servo system of the present invention features the use of AC servo motor, rather than electro-hydraulic servo valve. The present invention has an AC servo motor to drive through coupling the bidirectional constant displacement hydraulic pump, and the pump to provide the rotating vane helm with oil to constitute one closed hydraulic loop. The present invention has the features of the direct connection of directly driven electro-hydraulic servo pump and the rotating vane helm, one integrated valve block with four kinds of valves and the sealed pressure oil tank.
Description
The invention belongs to the electro-hydraulic servo technology in hydraulic technique and the control technology.
The present invention relates to the electrohydraulic servo device without electrohydraulic servo valve, power element is the rotary-vane steering gear peculiar to vessel of rotary blade type HM Hydraulic Motor form.
At present, known electrohydraulic servo device is by the general electrical motor 47 among Fig. 9, Hydraulic Pump (quantitative or variable) 48, and control presssure is formed with by pass valve 49, the electrohydraulic servo valve 50 and the power element hydraulic actuating cylinder 10a that accept servocontrol instruction usefulness.Electrohydraulic servo valve 50 is key elements of system, and the direction of power element 10a, speed are controlled by servovalve 50 entirely.Pressure in the system is set up by by pass valve 49 according to the load of 10a.This traditional electrohydraulic servo device is made up of open circuit.Oil in the hydraulic circuit all will pass through fuel tank 51.This system, no matter whether power element 10a moves, electrical motor 47 is turning round always, the pressure in the system can carry out off-load by by pass valve 49.The advantage of the electrohydraulic servo system of Fig. 9 is, the response of electrohydraulic servo valve is fast, precision is high, but that the unsurmountable shortcoming of this system is power consumption is big, and efficient is low, and contamination resistance is very weak, maintenance difficult, and cost is high.
In order to solve the shortcoming of Fig. 9 system, the present invention is designed to Fig. 1, Fig. 2 system.This is to drive two-way fix-displacement pump 3 by AC servomotor 1 by shaft coupling 2, and pump and power element rotary-vane steering gear 10 constitute the hydraulic closed loop.The Fill valve 4 that is connected in parallel in the loop is communicated with seal-off pressure oil tank 8, Fill valve 4 malleation (greater than a barometric pressure) repairing in hydraulic circuit at any time.The power element rotary-vane steering gear 10 needed startups of this system and stopping, positive and negative break-in, the speed speed, level of torque is controlled by AC servomotor 1 entirely, promptly accepts the AC servomotor that is of servocontrol instruction.
Fig. 3 is the control principle figure of direct drive type volume control alternating current fluid servo system.Fig. 3 is made up of two big squares.A bulk of 21 controllers of forming by control basal plate 15 and servo-driver 16 21; Another bulk 22 is by AC servomotor 1, motor speed measuring coder 17, bidirectional hydraulic oil pump 3, pressure sensor 18, the directly driven volume controlled electro-hydraulic servo cylinder system 22 that hydraulic ram 10a and displacement pickup 19 thereof are formed.Control basal plate 15 energized C and accept servocontrol instruction D among the figure.When control command D input was arranged, hydraulic ram 10a promptly had action.When hydraulic ram 10a did not work, when promptly controller 21 was not exported, at this moment motor was with regard to stall, and this is the key point of the remarkable saves energy of native system.
The present invention is formed with hydraulic schematic diagram Fig. 1 and steering wheel External view Fig. 2 of the directly driven volume controlled electro-hydraulic servo rotary-vane steering gear of innovative significance in the groundwork that adopts Figure 10 and Fig. 3, compares with Fig. 9 prior art reaching to have following tangible advantage under the situation of effect same:
(1) power greatly reduces, and is 1/2～1/5 of original technology;
(2) energy consumption greatly reduces, and is 1/10 of original technology;
(3) efficient greatly improves, and can reach 80～90%, is 3 times of original technology;
(4) closed circuit, it is little to take up room, and is 1/5 of original technology, and driving medium (hydraulic oil) volume is 1/20 of original technology open circuit;
(5) quality of whole steering wheel is 1/2～1/5 of original technology;
(6) cost is 1/2～1/3 of original technology;
(7) to compare noise little with original technology, and waste oil seldom is beneficial to environmental protection;
Technical scheme of the present invention is by Fig. 1, and two parts constitute among Fig. 2.
A) directly driven volume controlled electro-hydraulic servo pumping plant.
The electro-hydraulic servo pumping plant is by Fig. 2, and AC servomotor 1 among Fig. 1, plunging joint 2, and coupling box 2a, bidirectional hydraulic pump 3, integrated valve block 9, seal-off pressure oil tank 8 is formed.
After AC servomotor 1 energized among Fig. 1, when accepting the servo instruction of control rotary-vane steering gear action, electrical motor can be realized the action of start and stop, speed, forward and reverse, level of torque, by the two-way quantitative hydraulic pump 3 of plunging joint 2 direct drives.The electrical motor variable-ratio, break-in becomes torque and limit torque, and thus, the flow size of Hydraulic Pump, direction of the traffic, flow pressure size realize control by electrical motor entirely.
Hydraulic Pump goes to drive velocity of rotation, direction and the level of torque of rotary-vane steering gear with the state of flow size, direction, pressure size.Include integrated valve block 9 and seal-off pressure oil tank 8 in the electro-hydraulic servo pumping plant of Fig. 1.In valve piece 9, be integrated with Fill valve 4, two-way hydraulic control one-way valve (hydraulic lock) 5, safety valve 6 and bypass valve 7.Fill valve 4 is connected with oil tank 8, and 4 and 8 effects in hydraulic circuit are to guarantee malleation repairing in hydraulic circuit, in case produce cavitation erosion and noise.The effect of hydraulic lock 5 is to prevent to run rudder when shutting down, and should keep motionless when promptly rudder blade is subjected to sea beat, and the existence of hydraulic lock 5 is arranged, and the oil circuit in the steering wheel 10 is then by choke-out.Parts in the damage steering gear system are equipped with safety valve 6 again in valve piece 9 in order to prevent the sea beat rudder blade from crossing strong again, and when shock pressure was excessive, safety valve 6 was off-load, so that the protection rudder is a device.Bypass valve 7 is hand valves, generally speaking need not.When needing high-low pressure two chambeies (epitrochoidal chamber and oil back chamber), steering wheel is communicated with, so that, just bypass valve 7 is opened to the steering wheel maintenance with when adjusting.
Fig. 1 of prior art Figure 10 and innovation, Fig. 2 compares, and following difference is arranged on the electro-hydraulic servo pumping plant:
(1) innovative design of the present invention also produces, adjusts the integrated valve block 9 that can normally move.Fill valve 4 wherein, two-way hydraulic control one-way valve 5, safety valve 6,7 four kinds of valves of bypass valve.After once adjusting assembling, do not adjust again in total system in service needs.Fig. 7, Fig. 8 is the integrated package schematic appearance, among the figure, safe valve opening 39, through hole 40 is with oil tank intercommunicating pore 41, bypass valve opening 42, repairing valve opening 43, hydraulic pressure lockhole 44, with oil pump intercommunicating pore 45, with rotary-vane steering gear intercommunicating pore 46.
(2) Fill valve 4 is innovation designs and produces in the valve piece 9, but adjusts normal operation, simple in structure, reliable operation, the Fill valve adjusted again of not needing in service.Fig. 4 is its structure principle chart.Among Fig. 4, the O mouth is communicated with oil tank 8, and A, B mouth are communicated with hydraulic main circuit, in the turnover steering wheel 10.
(3) the seal-off pressure oil tank 8 among Fig. 1, but in invention innovative design and the element that has produced normal operation, and Fig. 5 is its structure principle chart.Among Fig. 5, tank body 25, air chamber 26, grease chamber 28, inflation inlet 27, the oil inlet and outlet 29 of oil tank (being connected) with the hole 49 of integrated valve block 9.
B) rotary-vane steering gear.
Fig. 1, among Fig. 2 rotary-vane steering gear 10 be by housing and rotor 11 and up and down end cap constitute.The moving blade 12 of rotor 11 is divided into four parts with the stator block 13 that is fixed on the housing with the cavity volume of steering wheel.Every two relative oil pockets are one group, interconnect by the duct on the rotor 11.These two groups of oil pockets are according to the variation of the direction of coming about, epitrochoidal chamber (high pressure chest) and oil back chamber (low-pressure cavity) alternate each other.On moving blade 12 and the stator block 13 sealing is arranged.
The hermetically-sealed construction that is sealed with innovative design among the present invention on moving blade 12 and the stator block 13.38 are the pressure valve of innovative design among Fig. 6, respectively adorn two on each moving blade 12 and the stator block 13, and are communicated with relatively.When a side of moving blade 12 and stator fast 13 is in operating pressure (high pressure), steel ball 37 compression springs 30, pressure oil enters in each seal groove through through hole 31,34, and sealing band is pressed on shell inner surface and the end cap face, to keep the oil pocket sealing.Through hole 32 is communicated with the pressure valve on opposite, and when a lateral pressure valve is worked (high pressure), the pressure valve of opposite side is just compressed steel ball by the pressure oil that through hole 32 is come.Along with the change of steering wheel rotation direction, the pressure valve alternation of both sides.The bottom of each sealing band among Fig. 6 in the seal groove 35 all studs with a plurality of springs, when shutting down, relies on these springs that sealing band is pressed on the sealing surface always, sealing when keeping shutting down.
The rudder stock 14 of ship securely is contained in rotor 11 endoporus, and rotor 11 rotates simultaneously with rudder stock 14.Rudder blade is equipped with in rudder stock 14 bottoms, and rudder blade and rudder stock 14 rotate simultaneously.
Claims (5)
1. the directly driven volume controlled electro-hydraulic servo pump directly is fastened on the body of rotary-vane steering gear, realizes the complete engine set installation structural design scheme of " valveless ", " not having pipe ", " no pumping plant ".
2. according to claim 1, in the directly driven volume controlled electro-hydraulic servo pumping plant, design Fill valve, two-way hydraulic control one-way valve, safety valve, the integrated morphology scheme of the integrated valve block of bypass valve.
3. according to claim 1, the structural design scheme of Fill valve in the directly driven volume controlled electro-hydraulic servo pumping plant.
4. according to claim 1, the structural design scheme of seal-off pressure oil tank in the directly driven volume controlled electro-hydraulic servo pumping plant.
5. according to claim 1, the design of Sealing Structure scheme of moving blade and stator block in the rotary-vane steering gear.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200510127358 CN1986332A (en) | 2005-12-19 | 2005-12-19 | Directly driven volume controlled electro-hydraulic servo rotating-vane helm |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200510127358 CN1986332A (en) | 2005-12-19 | 2005-12-19 | Directly driven volume controlled electro-hydraulic servo rotating-vane helm |
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| Publication Number | Publication Date |
|---|---|
| CN1986332A true CN1986332A (en) | 2007-06-27 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200510127358 Pending CN1986332A (en) | 2005-12-19 | 2005-12-19 | Directly driven volume controlled electro-hydraulic servo rotating-vane helm |
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101328858B (en) * | 2008-08-01 | 2010-10-13 | 哈尔滨工业大学 | Low friction high-pressure blade rotating motor based on self-compensation compound seal technique |
| CN102501961A (en) * | 2011-11-02 | 2012-06-20 | 江苏吉信远望船舶设备有限公司 | Automatic steering engine accelerator for rapid flows of inland rivers |
| CN102556321A (en) * | 2011-12-16 | 2012-07-11 | 华中科技大学 | Floating type spherical rotating vane steering engine |
| CN102588358A (en) * | 2012-02-20 | 2012-07-18 | 北京理工大学 | High-performance energy saving type electro-hydraulic servo control oil line |
| CN106931006A (en) * | 2015-12-29 | 2017-07-07 | 哈尔滨恒誉名翔科技有限公司 | A kind of new steering gear hydraulic system |
| CN108327887A (en) * | 2018-03-21 | 2018-07-27 | 无锡德林防务装备股份有限公司 | Frequency conversion steering engine peculiar to vessel |
| CN110550190A (en) * | 2019-07-25 | 2019-12-10 | 上海航天控制技术研究所 | electric hydrostatic pump-controlled rotary steering engine |
-
2005
- 2005-12-19 CN CN 200510127358 patent/CN1986332A/en active Pending
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101328858B (en) * | 2008-08-01 | 2010-10-13 | 哈尔滨工业大学 | Low friction high-pressure blade rotating motor based on self-compensation compound seal technique |
| CN102501961A (en) * | 2011-11-02 | 2012-06-20 | 江苏吉信远望船舶设备有限公司 | Automatic steering engine accelerator for rapid flows of inland rivers |
| CN102501961B (en) * | 2011-11-02 | 2014-03-19 | 江苏吉信远望船舶设备有限公司 | Automatic steering engine accelerator for rapid flows of inland rivers |
| CN102556321A (en) * | 2011-12-16 | 2012-07-11 | 华中科技大学 | Floating type spherical rotating vane steering engine |
| CN102556321B (en) * | 2011-12-16 | 2014-06-04 | 华中科技大学 | Floating type spherical rotating vane steering engine |
| CN102588358A (en) * | 2012-02-20 | 2012-07-18 | 北京理工大学 | High-performance energy saving type electro-hydraulic servo control oil line |
| CN102588358B (en) * | 2012-02-20 | 2015-01-21 | 北京理工大学 | High-performance energy saving type electro-hydraulic servo control oil line |
| CN106931006A (en) * | 2015-12-29 | 2017-07-07 | 哈尔滨恒誉名翔科技有限公司 | A kind of new steering gear hydraulic system |
| CN108327887A (en) * | 2018-03-21 | 2018-07-27 | 无锡德林防务装备股份有限公司 | Frequency conversion steering engine peculiar to vessel |
| CN110550190A (en) * | 2019-07-25 | 2019-12-10 | 上海航天控制技术研究所 | electric hydrostatic pump-controlled rotary steering engine |
| CN110550190B (en) * | 2019-07-25 | 2023-08-25 | 上海航天控制技术研究所 | Electric hydrostatic pump control rotary steering engine |
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Open date: 20070627 |