CN101691877A - Servo motor control-based multi-pump combination controlled hydraulic power system - Google Patents
Servo motor control-based multi-pump combination controlled hydraulic power system Download PDFInfo
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- CN101691877A CN101691877A CN200910192111A CN200910192111A CN101691877A CN 101691877 A CN101691877 A CN 101691877A CN 200910192111 A CN200910192111 A CN 200910192111A CN 200910192111 A CN200910192111 A CN 200910192111A CN 101691877 A CN101691877 A CN 101691877A
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Abstract
The invention provides a servo motor control-based multi-pump combination controlled hydraulic power system. The system comprises a host controller, at least two servo pumps, an oil pipe and an oil tank, wherein branch oil pipelines of all the servo pumps are connected together to form a main oil pipeline of the system; one of all the servo pumps is the main servo pump; the oil pipeline of the main servo pump forms a master control branch oil pipeline of the system; Each branch oil pipeline of all the servo pumps is connected with a check valve in serial before entering the main oil pipeline of the system; two ends of the check valve of the main servo pump are connected with main pressure controllers in parallel; the main pressure controller comprises a cartridge valve and a pressure difference orifice; an oil inlet cavity and a control valve of the cartridge valve and two ends of the pressure difference orifice are connected with two ends of the oil outlet and the oil inlet of the check valve of the main servo pump in parallel respectively; and an oil return cavity of the cartridge valve is connected to the oil tank. The system has low energy consumption of pressure maintenance, high pressure release speed and small impact of pressure release or load discharge on the oil pump and a servo drive system.
Description
[technical field]
The present invention relates to a kind of hydraulic power system, particularly a kind of many pumps composite control hydraulic power system that is used for injection machine based on actuating motor control.
[background technique]
We know, the working procedure of injection machine generally is divided into locked mode, injection, pressurize, cooling, plasticizing, die sinking and the stage such as ejects, the different stages needs hydraulic system that the hydraulic oil of different pressures and flow is provided, so hydraulic oil generally all will experience the cyclic process of pressurization, pressurize and pressure release.
Along with deepening continuously of energy-conserving and environment-protective consciousness, people have proposed more and more higher requirement to the energy consumption and the control accuracy of traditional injection moulding machine.The appearance of driven by servomotor oil pump control technique is the progress of liquid electricity in conjunction with the revolution of control technique.It not only can energy-conservation significantly 30%-70%, and has the control accuracy height, good stability, and advantage such as noise is low once release, has promptly obtained fast development in industries such as injection machines, becomes the main direction that injection machine energy-saving is from now on transformed.
Present driven by servomotor hydraulic pump control system (hereinafter to be referred as servopump) as shown in Figure 1, by actuating motor 212, motor servo driver 211, hydraulic-pressure pump 213, Detecting element (pressure transducer 215, encoder 214) composition such as, rotating speed by control actuating motor 212 and moment of torsion are realized the control to flow rate of hydraulic system and pressure; Make hydraulic system step-down or drain charge by control actuating motor 212 antiports, have flow pressure control accuracy height, response is fast, advantages such as good energy-conserving effect.
Yet be limited by the restriction of actuating motor and actuator power and oil pump capacity, often need to adopt many servopumps to jointly control the requirement that just can reach big flow for the large-tonnage injection machine.For this reason, also there is company to work out a kind of many actuating motor oil pump combined control systems that adopt special-purpose simultaneous controlling and driving device, this control system makes many actuating motor oil pumps have identical flow pressure instruction in everything by the simultaneous controlling and driving device of special use, realizes synchronous flow (speed) control and pressure control.But there is following defective in this system: system pressure control is finished jointly by many pumps, has a large amount of unnecessary energy consumptions during pressurize.Though this is because single pump pressurize is enough to satisfy the pressurization needs, but for large-tonnage hydraulic injection molding machine system, the hydraulic oil volume is big by compression in hydraulic jack and the pipeline, the compression energy height, separately by the drain charge scarce capacity of a servopump to satisfy in the utmost point requirement that step-down or drain charge compression energy discharge in the short time, therefore have to adopt many servopump synchronization motions to realize pressurize, the control of drain charge equal pressure, but this problem of bringing is that the pressurize energy consumption is big, pressure release speed is slow, and the oil that refluxes when step-down or drain charge is big to the impact of oil pump and servo drive system, can shorten the working life of oil pump and controller; Many the long-time load operations of servopump also can produce a very large impact its overload capacity.Actuating motor is operated under the low-speed big state, and its mechanical efficiency is also very low.
[summary of the invention]
Purpose of the present invention overcomes the deficiencies in the prior art exactly, provides that a kind of pressurize energy consumption is low, pressure release speed is fast and step-down or drain charge the many pump composite control hydraulic power system based on actuating motor control little to the impact of oil pump and servo drive system.
In order to solve the problems of the technologies described above, the present invention is achieved by the following technical solutions:
A kind of many pumps composite control hydraulic power system based on actuating motor control, include console controller, at least 2 servopumps, oil pipe, fuel tank, each branch oil pipe road tandem of all servopumps is in the main oil pipe road of construction system together, wherein: have 1 to be the main servo pump in all servopumps, the master control branch oil pipe road of the oil-piping construction system at main servo pump place, the branch oil pipe road at all servopump places was serially connected with an one-way valve before entering system main oil pipe road, be parallel with master pressure controller at the one-way valve two ends of this main servo pump; Described master pressure controller includes cartridge valve and pressure reduction throttle orifice, the two ends of the oil suction chamber of described cartridge valve and control chamber, pressure reduction throttle orifice are connected in parallel on the oil outlet and the filler opening two ends of the one-way valve of this main servo pump respectively, and the oil back chamber of described cartridge valve leads to fuel tank.
In improvement project to above-mentioned many pumps composite control hydraulic power system of controlling based on actuating motor, on the main oil pipe road of this system, be provided with safety valve, the oil outlet of this safety valve leads to fuel tank.
In improvement project to above-mentioned many pumps composite control hydraulic power system of controlling based on actuating motor, the control chamber of described cartridge valve is connected with guide's safety valve, the oil inlet end of described guide's safety valve is with the end junction of cartridge valve control chamber and be communicated with master control branch oil pipe road, and the oil outlet end of described guide's safety valve leads to fuel tank; Be provided with guide's throttle orifice after the oil inlet end of described guide's safety valve and the junction of cartridge valve control chamber and between the oil inlet end of one-way valve.
In the improvement project to above-mentioned many pumps composite control hydraulic power system of controlling based on actuating motor, described pressure reduction throttle orifice is opened in the main valve plug of this cartridge valve.
In the improvement project to above-mentioned many pumps composite control hydraulic power system of controlling based on actuating motor, described servopump includes motor servo driver, actuating motor, oil hydraulic pump, Detecting element and braking resistor.
In the improvement project to above-mentioned many pumps composite control hydraulic power system of controlling based on actuating motor, described Detecting element includes pressure transducer and encoder, and described oil hydraulic pump is a gear pump.
Compared with prior art, the present invention has following advantage:
1, because native system only needs separate unit float amount servopump (main pump) just can finish pressurize and drain charge action, other servopump this moment (auxilliary pump) can no-load running, therefore can reduce the pressurize energy consumption greatly, this big quality moulding for the moulding of large-tonnage injection machine needs long-time pressurize significant.
2, owing to adopt the cartridge valve of big latus rectum to finish step-down and drain charge as the main pressure valve of master pressure controller, therefore, pressure release is fast, and noise is low, and is little to the impact of activated actuator pump system, can prolong the working life of servopump.
3, can avoid the auxiliary servo pump work in low-speed big (pressurize) running state, can reduce the actuating motor of auxilliary pump and the configuration requirement of driver, thereby reduce cost, improve product competitive ability.
4, do not need special actuating motor simultaneous controller, can reduce purchase cost.
5, because the load of actuating motor plugging reduces greatly, can reduce the allocating power of braking resistor.
6, except that the control that is applicable to many arbitrarily group servopumps requires, can also be used in the drain charge loop of the large and small double amount plunger pump of driven by servomotor.
The present invention is described in further detail below in conjunction with accompanying drawing and embodiment:
[description of drawings]
Fig. 1 is present driven by servomotor hydraulic pump control system structural representation;
Fig. 2 is the entire system structural representation of the embodiment of the invention one;
Fig. 3 is the partial structurtes schematic representation (at the master pressure controller place) of the embodiment of the invention two;
Fig. 4 is the partial structurtes schematic representation (at the master pressure controller place) of the embodiment of the invention three;
Fig. 5 is the partial structurtes schematic representation (at the master pressure controller place) of the embodiment of the invention four;
Fig. 6 is the partial structurtes schematic representation (at the master pressure controller place) of the embodiment of the invention five;
[embodiment]
The present invention is a kind of many pumps composite control hydraulic power system based on actuating motor control, as shown in Figure 2, include console controller 1, at least 2 servopumps (3 servopumps being arranged) at present embodiment, oil pipe 10, fuel tank 6, each branch oil pipe road tandem of all servopumps is in the main oil pipe road P0 of construction system together, in all servopumps (as shown in Figure 3), there is 1 to be main servo pump 21, the master control branch oil pipe road P1 of the oil-piping construction system at main servo pump 21 places, the branch oil pipe road P1 at all servopump places, P2, P3 was serially connected with an one-way valve 31 respectively before entering the main oil pipe road P0 of system, 32,33, one-way valve 31 two ends on this main servo pump 21 are parallel with master pressure controller, described master pressure controller includes cartridge valve 4 and pressure reduction throttle orifice 5, the oil suction chamber A of described cartridge valve 4 and control chamber X, the two ends of pressure reduction throttle orifice 5 are connected in parallel on the oil outlet and the filler opening two ends of one-way valve 31 respectively, and the oil back chamber B of described cartridge valve 4 leads to fuel tank 6.Include motor servo driver 211, actuating motor 212, oil hydraulic pump 213, Detecting element, braking resistor 216 at the servopump described in this system, described Detecting element includes pressure transducer 215, encoder 214, and described oil hydraulic pump 213 is gear pump or quantitative plunger pump (basic identical with existing servopump structure).The present invention finishes flow (speed) control jointly by many servopumps; And with the pilot pressure of separate unit servopump (main servo pump 21) as guide's pilot pressure, form the pressure closed loop control system jointly with master pressure controller (hydraulic cartridge valve 4 and pressure reduction throttle orifice 5), realize the accurate control of system pressure in different operating processes such as pressurization, pressurize, decompression or drain charges.Its basic functional principle is as shown in Figure 2:
System is when doing flow (speed) control, this system sends the same traffic of setting by console controller 1 and instructs to each motor servo driver 211, make each actuating motor 212 by the rotating speed forward running of setting, thereby drive each servopump 213 hydraulic oil through the oil outlet end output target flow (speed) of one-way valve 31,32,33 from branch oil pipe road P1, P2, P3 separately, and the detection feedback signal of the encoder 214 by each servopump, the rotating speed of each actuating motor 212 of closed loop control, thus reach the purpose of accuracy-control system flow (speed).(this and existing speed control mode basic identical).System's pressurize is when doing pressure control, and system sends pressure instruction for main servo pump 21 by 1 of console controller, and auxiliary servo pump 22,23 is not worked.At this moment under the non-return effect of one-way valve 32 and 33, auxiliary servo pump each oil circuit P2, P3 and main oil pipe road P0 isolate, make system pressure only be subjected to the control of main servo pump 21 and master pressure controller, oil among the main oil pipe road P0 auxiliary servo pump 22,23 that can not reflux, thereby auxiliary servo pump 22,23 has been avoided long-time load operation and has been significantly reduced in the system hydraulic oil to the impact of activated actuator pump system.The motor servo driver 211 of main servo pump 21 is after the instruction of receiving console controller 1: if command pressure is greater than real system pressure (detected pressures of pressure transducer) at this moment, export than high pulling torque by the actuating motor 212 of control main servo pump 21 so, make the command pressure of the oil hydraulic pump 213 output settings of main servo pump 21, the pressure of the oil hydraulic pump 213 of main servo pump 21 outlet at this moment raises, and pressure oil enters the main oil pipe road P0 of system through pressure reduction throttle orifice 5 and one-way valve 31 and makes system pressure be increased to setting pressure to finish compression motion.Before and after this process, the pressure of cartridge valve 4 control chamber X is higher than the pressure of oil suction chamber A, and under the effect of pressure oil and spring force, cartridge valve 4 is in closed condition.If command pressure is less than real system pressure, the moment of torsion that the output of main servo pump 21 backward rotation is less, oil hydraulic pump 213 outlet pressures of main servo pump 21 are reduced, oil hydraulic pump 213 outlet pressures of main servo pump 21 are less than system pressure at this moment, pressure oil flows to master control branch oil pipe road P1 through pressure reduction throttle orifice 5 from main oil pipe road P0, at this moment because the effect of pressure reduction throttle orifice 5 makes the pressure of oil hydraulic pump 213 outlets of main oil pipe road P0 and main servo pump 21, having produced pressure at pressure reduction throttle orifice 5 two ends falls, at this moment the pressure of cartridge valve 4 oil suction chamber A is higher than the pressure of control chamber X, when the pressure difference of the pressure of cartridge valve 4 oil suction chamber A and control chamber X overcomes the spring force of cartridge valve 4 main valve plugs, cartridge valve 4 is opened, components of system as directed pressure oil flows back to fuel tank 6 from the oil suction chamber A of cartridge valve 4 through oil back chamber B, makes system pressure be reduced to new setting pressure and finishes the decompression action.In pressurization or decompression, the detection feedback signal update the system pressure instruction of pressure transducer 215 is realized the system pressure closed loop control.Therefore, guide's pilot pressure (command pressure) of the output that master pressure controller (hydraulic cartridge valve 4 and pressure reduction throttle orifice 5) can dynamic following main servo pump, thus realize numerical scale closed loop control to system pressure.
System's pressurize is when doing pressure control, and system sends the instruction that quits work for the motor driver 211 of each auxiliary servo pump 22,23 by console controller 1, and each auxiliary servo motor 212 is shut down, and each auxiliary servo pump 22,23 is not worked; 1 of console controller sends pressure instruction for main servo pump 21 and finishes the pressurize action by main servo pump 21.Equally at this moment, under the non-return effect of one-way valve 32 and 33, oil circuit P2, P3 and the main oil pipe road P0 of each auxiliary servo pump 22,23 isolate, the drain charge of auxiliary servo pump, pressure is near zero, thereby same, auxiliary servo pump 22,23 has been avoided long-time load operation and has been significantly reduced in the system hydraulic oil to the impact of activated actuator pump system.
After pressurize is finished, during the system drain charge, same system sends the zero pressure instruction for main servo pump 21 by console controller 1, other auxiliary servo pump 22,23 do not work, actuating motor 212 by control main servo pump 21 makes the oil hydraulic pump 213 backward rotation output zero pressure of main servo pump 21 finish guide's drain charge, opening fully of control cartridge valve 4 main valve plugs falls in the pressure of pressure reduction throttle orifice 5 front and back, so, the pressure oil of the big flow of system flows back to fuel tank 6 from the oil suction chamber A of cartridge valve 4 through oil back chamber B, make system finish the drain charge action in the short time, thereby avoided the impact of drain charge each servopump at the utmost point.
Under the control of native system, can circulate in fact according to actual needs and realize the working procedure of above pressurization, pressurize, decompression or drain charge.In the present embodiment, the auxiliary servo pump has two, can ask the quantity that the auxiliary servo pump is set according to the flow needs when practical application.
Because the branch oil pipe road at all servopump places all was serially connected with an one-way valve (as shown in Figure 2) before entering the main oil pipe road P0 of system in native system; thereby avoided many long-time load operations of servopump, thereby the overload capacity of servopump has been played very big protective action.Again because be provided with master pressure controller and adopt the cartridge valve 4 of big latus rectum to finish step-down and drain charge in the system as main pressure valve, therefore, pressure release is fast, noise is low, add that hydraulic oil is little to the impact of activated actuator pump system in the non-return effect of each one-way valve thereby the system, so just prolonged the working life of servopump.Be the control mode that control step-down or drain charge are closed in the liquid Electricity Federation because native system adopts again, only need separate unit float amount servopump (main servo pump 21) just can finish pressurize and drain charge action, this moment other servopump (auxiliary servo pump 22,23) be in unloaded state, so just reduced the energy consumption of system widely, avoided again and can only could realize pressure control by all servopump synchronization motions to system, can avoid each auxiliary servo pump 22 again, 23 are operated in low-speed big (pressurize) running state, reduced each auxiliary servo pump 22,23 the actuating motor 212 and the configuration requirement of motor servo driver 211, thereby saved resource and cost of production, improved product competitive ability.This big quality moulding for the moulding of large-tonnage injection machine needs long-time pressurize significant.In addition since native system do not need all servopump synchronization motions could realize the pressure control of system thereby do not need special actuating motor simultaneous controller, thereby reduced purchase cost, add because the load of non-return effect actuating motor 212 pluggings of one-way valve 31 reduces greatly, also reduced the allocating power of braking resistor 216.
Hydraulic control part of the present invention can also adopt different structures and Placement to realize.
Embodiment the two, three, four, the 5th shown in Fig. 3,4,5,6, the structure and the Placement of several variations with identical control principle of native system, these embodiments' difference mainly is at the master pressure controller place.
Embodiment two as shown in Figure 3 is the further improvement to embodiment one, is provided with safety valve 7 on the main oil pipe road of this system P0, and the oil outlet of this safety valve 7 leads to fuel tank 6.Control principle after the safety pressure control function that present embodiment is compound, on the main oil pipe road of system P0, be provided with safety valve 7, when the pressure of system surpasses the system pressure safety value, at this moment safety valve 7 is opened, oil power oil flows to fuel tank 6 through safety valve 7 oil outlets, thus the maximum safety pressure power of the system of qualification.
Embodiment four as shown in Figure 5 also is the further improvement to embodiment one, the control chamber X of described cartridge valve 4 is connected with guide's safety valve 9, the oil inlet end of described guide's safety valve 9 is with cartridge valve 4 control chamber X junctions and be communicated with master control branch oil pipe road P1, and the oil outlet end of described guide's safety valve 9 leads to fuel tank 6; Be provided with guide's throttle orifice 8 after the oil inlet end of described guide's safety valve 9 and the cartridge valve 4 control chamber X junctions and between the oil inlet end of one-way valve 31.Control principle after this safety pressure control function that has been compound also, when system pressure reaches the setting pressure of guide's safety valve 9, guide's safety valve 9 is opened, thereby pressure oil falls to guide's safety valve 9 mobile pressure that produce through guide's throttle orifice 8, at this moment the pressure of cartridge valve 4 oil suction chamber A is higher than the pressure of cartridge valve 4 control chamber X, when the pressure difference of the pressure of cartridge valve 4 oil suction chamber A and control chamber X overcomes the spring force of cartridge valve 4 main valve plugs, cartridge valve 4 is opened, thus the maximum safety pressure power of the system of qualification.
Above-described as Fig. 2,3,5 illustrated embodiments one, two, four in, described pressure reduction throttle orifice 5 also can be opened in the main valve plug of this cartridge valve 4, at this moment the control chamber X of cartridge valve 4 is communicated with by pressure reduction throttle orifice 5 and cartridge valve 4 oil suction chamber A.Embodiment three, five shown in Fig. 4,6 is opened in situation in the main valve plug of this cartridge valve 4 to the pressure reduction throttle orifice 5 among the embodiment two, four shown in Fig. 3,5, and their correspondences have identical control principle and function.
Native system can also be used in the drain charge loop of the large and small double amount plunger pump of driven by servomotor except that the control that is applicable to many arbitrarily group servopumps requires.
Native system does not limit to and is used for injection machine, can be used for other field that needs are realized identical control principle and function yet.
Claims (6)
1. many pumps composite control hydraulic power system based on actuating motor control, include console controller (1), at least 2 servopumps, oil pipe (10), fuel tank (6), each branch oil pipe road tandem of all servopumps is in the main oil pipe road (P0) of construction system together, it is characterized in that: have 1 to be main servo pump (21) in all servopumps, the master control branch oil pipe road (P1) of the oil-piping construction system at main servo pump (21) place, the branch oil pipe road at all servopump places is serially connected with an one-way valve before entering system main oil pipe road (P0), is parallel with master pressure controller at one-way valve (31) two ends of this main servo pump (21); Described master pressure controller includes cartridge valve (4) and pressure reduction throttle orifice (5), the two ends of the oil suction chamber (A) of described cartridge valve (4) and control chamber (X), pressure reduction throttle orifice (5) are connected in parallel on the oil outlet and the filler opening two ends of the one-way valve (31) of this main servo pump (21) respectively, and the oil back chamber (B) of described cartridge valve (4) leads to fuel tank (6).
2. the many pumps composite control hydraulic power system based on actuating motor control according to claim 1, it is characterized in that: be provided with safety valve (7) on this main oil pipe road (P0), the oil outlet of this safety valve (7) leads to fuel tank (6).
3. the many pumps composite control hydraulic power system based on actuating motor control according to claim 1, it is characterized in that: the control chamber (X) of described cartridge valve (4) is connected with guide's safety valve (9), the oil inlet end of described guide's safety valve (9) is with cartridge valve (4) control chamber (X) end junction and be communicated with master control branch oil pipe road (P1), and the oil outlet end of described guide's safety valve (9) leads to fuel tank (6); Be provided with guide's throttle orifice (8) after the oil inlet end of described guide's safety valve (9) and cartridge valve (4) control chamber (X) junction and between the oil inlet end of one-way valve (31).
4. according to claim 1,2 or 3 described many pumps composite control hydraulic power systems based on actuating motor control, it is characterized in that: described pressure reduction throttle orifice (5) is opened in the main valve plug of this cartridge valve (4).
5. according to claim 1,2 or 3 described many pumps composite control hydraulic power systems based on actuating motor control, it is characterized in that: described servopump includes motor servo driver (211), actuating motor (212), oil hydraulic pump (213), Detecting element and braking resistor (216).
6. the many pumps composite control hydraulic power system based on actuating motor control according to claim 5, it is characterized in that: described Detecting element includes pressure transducer (215) and encoder (214), and described oil hydraulic pump (213) is a gear pump.
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Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN102848540A (en) * | 2012-08-06 | 2013-01-02 | 宁波弘讯科技股份有限公司 | Servo control system and method |
| CN102962972A (en) * | 2012-11-16 | 2013-03-13 | 宁波华美达机械制造有限公司 | Hydraulic system of injection molding machine with servo pump |
| CN103629193A (en) * | 2013-11-22 | 2014-03-12 | 江苏兆合电气有限公司 | Device and method for controlling multi-pump hydraulic system |
| CN105020207A (en) * | 2015-06-16 | 2015-11-04 | 中国海洋石油总公司 | Dual-redundancy pressure adjusting device having emergent pressure relief |
| CN107100903A (en) * | 2017-06-29 | 2017-08-29 | 中冶赛迪装备有限公司 | A kind of constant-pressure variable hydraulic power system |
| CN110439882A (en) * | 2018-05-03 | 2019-11-12 | 杭州诺云科技有限公司 | A kind of concentration hydraulic station energy conservation optimizing method and system |
| CN113175448A (en) * | 2021-04-26 | 2021-07-27 | 深圳市科斯腾液压设备有限公司 | Hydraulic device for feeding back output torque of servo motor by utilizing deadweight potential energy |
| CN114251317A (en) * | 2021-11-24 | 2022-03-29 | 中冶赛迪工程技术股份有限公司 | Steel tube rolling mill core rod limiting hydraulic pump control device |
Family Cites Families (3)
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| CN101100105A (en) * | 2007-07-12 | 2008-01-09 | 昌盛达机械(浙江)有限公司 | Injection moulding machine servo energy-saving control system |
| CN101503960B (en) * | 2009-03-02 | 2010-12-08 | 浙江大学 | Multi-pump combined driving shield-tunneling blade disc hydraulic system |
| CN201475067U (en) * | 2009-09-04 | 2010-05-19 | 佛山市顺德区震德塑料机械有限公司 | Multi-pump combined control hydraulic power system based on servo motor control |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN102848540A (en) * | 2012-08-06 | 2013-01-02 | 宁波弘讯科技股份有限公司 | Servo control system and method |
| CN102848540B (en) * | 2012-08-06 | 2015-03-11 | 宁波弘讯科技股份有限公司 | Servo control system and method |
| CN102962972A (en) * | 2012-11-16 | 2013-03-13 | 宁波华美达机械制造有限公司 | Hydraulic system of injection molding machine with servo pump |
| CN102962972B (en) * | 2012-11-16 | 2015-06-17 | 宁波华美达机械制造有限公司 | Hydraulic system of injection molding machine with servo pump |
| CN103629193A (en) * | 2013-11-22 | 2014-03-12 | 江苏兆合电气有限公司 | Device and method for controlling multi-pump hydraulic system |
| CN105020207A (en) * | 2015-06-16 | 2015-11-04 | 中国海洋石油总公司 | Dual-redundancy pressure adjusting device having emergent pressure relief |
| CN107100903A (en) * | 2017-06-29 | 2017-08-29 | 中冶赛迪装备有限公司 | A kind of constant-pressure variable hydraulic power system |
| CN110439882A (en) * | 2018-05-03 | 2019-11-12 | 杭州诺云科技有限公司 | A kind of concentration hydraulic station energy conservation optimizing method and system |
| CN110439882B (en) * | 2018-05-03 | 2020-07-28 | 杭州诺云科技有限公司 | Energy-saving optimization method and system for centralized hydraulic station |
| CN113175448A (en) * | 2021-04-26 | 2021-07-27 | 深圳市科斯腾液压设备有限公司 | Hydraulic device for feeding back output torque of servo motor by utilizing deadweight potential energy |
| CN114251317A (en) * | 2021-11-24 | 2022-03-29 | 中冶赛迪工程技术股份有限公司 | Steel tube rolling mill core rod limiting hydraulic pump control device |
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| CN101691877B (en) | 2012-03-07 |
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Effective date of registration: 20200619 Address after: 528300, No. 76, Shun Xiang Road, Daliang street, Shunde District, Guangdong, Foshan Patentee after: FOSHAN CITY SHUNDE DISTRICT ZHENDE PRECISION MACHINERY Co.,Ltd. Address before: 528300 Guangdong Province, Foshan city Shunde District Daliang Honggang Industrial Zone Patentee before: FOSHAN SHUNDE DISTR CHEN DE PLASTICS MACHINERY Co.,Ltd. |