CN203362711U - Hydraulic cylinder control system conducting direct driving type servo pump control electro-hydraulic combination driving - Google Patents
Hydraulic cylinder control system conducting direct driving type servo pump control electro-hydraulic combination driving Download PDFInfo
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- CN203362711U CN203362711U CN2013203512784U CN201320351278U CN203362711U CN 203362711 U CN203362711 U CN 203362711U CN 2013203512784 U CN2013203512784 U CN 2013203512784U CN 201320351278 U CN201320351278 U CN 201320351278U CN 203362711 U CN203362711 U CN 203362711U
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Abstract
Provided is a hydraulic cylinder control system conducting direct driving type servo pump control electro-hydraulic combination driving. The hydraulic cylinder control system comprises a servo motor driving module, a pump control module and an auxiliary oil way module. A servo driver controls a servo motor to drive a bidirectional pump to produce hydraulic energy, two oil ways of the bidirectional pump are connected with a rod cavity and a non-rod cavity of a hydraulic cylinder respectively, an oil tank is used for compensating oil and leaking the oil when flow of the rod cavity and the non-rod cavity is imbalanced, and positive and negative rotating directions of the servo motor control the movement direction of a piston rod of the hydraulic cylinder. The hydraulic cylinder control system conducting direct driving type servo pump control electro-hydraulic combination driving can effectively solve the problem of flow asymmetry in a pump control hydraulic control system, reduce circulation oil liquid amount of the system and pressure loss produced by oil liquid flowing, and the whole system is compact, easily achieves integration, and greatly reduces pressure loss and heating of a electro-hydraulic servo system caused by pressure difference flow characteristics of a proportional valve or servo valve.
Description
Technical field
The utility model belongs to technical field of motors, relates to electrohydraulic servo system, for the oil hydraulic cylinder of a kind of directly driving type servo-pump control electricity liquid combination drive is controlled system.
Background technique
When current electrohydraulic servo system is worked, must, by the valve of a series of various functions, particularly need Proportional valve, servovalve etc. to control pressure, flow velocity, the flow direction of working liquid body, thereby make each oil hydraulic cylinder complete due action according to technological requirement.The defect such as simultaneously, unavoidably have complex structure, energy consumption is large, heating value is serious, noise is high, vibration is large, the requirement of fluid filter precision is high, restriction loss is large.
The pump control hydraulic control system, be the pump control by original control mode by the revolutionary change of valve control, and by original throttle grverning principle, energy loss is large, the shortcomings such as system is easily generated heat, and efficiency is low are abandoned, and take full advantage of volumetric speed control, energy-conserving and environment-protective, synchronization accuracy is high, and response is fast.Due to double-acting hydraulic cylinder Area comparison large (can reach 12:1), upper and lower cavity oil extraction and oil-feed flow differ greatly, and pump is controlled because of its volume, thereby determined that oil absorption and oil drain quantity equate, so and the flow nonsymmetry of generation becomes pump control system control problem urgently to be resolved hurrily.
Domestic each colleges and universities carry out respectively the fundamental research of pump control system in applications such as boats and ships and energy-conserving elevators at present.Current pump prosecutor case adopts single or two Pilot operated check valves or adopts double pump to control the flow imbalance problem that solves pump control asymmetrical cylinder.Wherein Pilot operated check valve control implementation is that the unbalanced chamber of oil hydraulic cylinder flow directly is connected with fuel tank, by system pressure, automatically controls it from the fuel tank repairing or to the fuel tank oil extraction.For to fuel tank oil extraction side, on the one hand, fluid quick non-loaded mobile produced the extra pressure loss and heating; On the other hand, fuel tank is because required fluid amount will be large enough to hold oil cylinder and move fast the time, thereby the fuel tank volume is difficult to reduce, and the power savings advantages that can't embody the pump control reduces consumption and the consumption of fluid medium.In addition, hydraulic control mode has increased the complexity that system is controlled.
And the double pump control program, only having solved repairing problem and fluid control pressure provides, and the problem of bringing is that system bulk is larger, more powerful, and energy efficiency reduces, and cost performance is not high.
Summary of the invention
Problem to be solved in the utility model is: the pump control hydraulic control system has energy-conserving and environment-protective in theory, synchronization accuracy is high, respond fast advantage, but prior art does not have suitable solution for the flow nonsymmetry problem of pump control hydraulic control system in actual applications, system is controlled complexity, energy efficiency is low, cost performance is not high.
The technical solution of the utility model is: the oil hydraulic cylinder of directly driving type servo-pump control electricity liquid combination drive is controlled system, comprise actuating motor, two-way pump, differential unloading valve, the first one-way valve, the second one-way valve, fuel tank, oil hydraulic cylinder and servo driver, the long-pending ratio of the rod end chamber annular cross-sectional area of oil hydraulic cylinder and piston cross-section is not 1, servo driver connects actuating motor, the output of actuating motor connects two-way pump, two-way pump divides the two-way oil circuit, the first oil circuit is connected to the rodless cavity of oil hydraulic cylinder, the second oil circuit is connected to the rod chamber of oil hydraulic cylinder, described two-way oil circuit separates respectively a branch road and is connected to fuel tank through safety valve, the second oil circuit is through the first one-way valve, unidirectional first oil circuit that is connected to of differential unloading valve, fuel tank connects the hydraulic fluid port B of differential unloading valve, fuel tank is also by unidirectional second oil circuit that is connected to of the second one-way valve.
Further, be respectively equipped with pressure transducer on described two-way oil circuit.
Further, the piston rod correspondence of oil hydraulic cylinder is provided with displacement transducer.
The utility model is controlled actuating motor by servo driver and is directly driven two-way pump to produce hydraulic energy, the pressure of realization to oil hydraulic cylinder, flow, the compound control of direction, the two-way oil circuit of two-way pump is rod chamber and the rodless cavity of connecting fluid cylinder pressure respectively, repairing and draining when fuel tank is used for rod chamber and rodless cavity flow imbalance, controlled the piston rod movement direction of oil hydraulic cylinder by the positive and reverse steering of actuating motor: during the actuating motor forward, drive two-way pump by the fluid sucking-off of the oil of oil hydraulic cylinder rod chamber and fuel tank, flow to the first oil circuit by the second oil circuit, the final rodless cavity that flows into, piston rod is stretched out, during the actuating motor reversion, drive two-way pump by the sucking-off of the oil of oil hydraulic cylinder rodless cavity, fluid flows to the second oil circuit by the first oil circuit, finally flows into rod chamber and fuel tank, and piston rod is return.
The utility model can effectively reduce the circulation fluid amount of system, and device simple in structure is few, can shorten the route of fluid circulation, thereby reduces the pressure loss that fluid flows and produces, and makes whole system compacter and easily realize that integrated and effective minimizing generates heat; When oil hydraulic cylinder is stretched out fast, repairing is more timely, responds sooner, effectively avoids the cavitation erosion problem of the empty and oil hydraulic cylinder of the suction of pump, extends component life, the speed of response of raising pump.In addition, adopt the volume control of two-way pump greatly to reduce the pressure loss and the heating brought because of the throttling control differential pressure flow characteristic of Proportional valve or servovalve.
The utility model, by differential unloading valve, when hydraulic cylinder piston rod stretches out, can form differential circuit on the one hand, improves hydraulic cylinder speed and response; On the other hand, when hydraulic cylinder piston rod is retracted, the flow imbalance that the difference of oil hydraulic cylinder two chamber oil-feeds and oil drain quantity causes, unnecessary fluid will be by differential unloading valve off-load to fuel tank.
The accompanying drawing explanation
Fig. 1 is structural representation of the present utility model.
Embodiment
Below by a specific embodiment, enforcement of the present utility model is described.
As Fig. 1, oil hydraulic cylinder control system of the present utility model comprises actuating motor 1, two-way pump 2, differential unloading valve 3, the first one-way valve 4, the second one-way valve 6, fuel tank 9, oil hydraulic cylinder 10 and servo driver 13, wherein the long-pending ratio of the rod end chamber annular cross-sectional area of oil hydraulic cylinder 10 and piston cross-section is not 1, the structure of control system is: servo driver 13 connects actuating motor 1, the output of actuating motor 1 connects two-way pump 2, 2 minutes two-way oil circuits of two-way pump, the first oil circuit is connected to the rodless cavity of oil hydraulic cylinder 10, the second oil circuit is connected to the rod chamber of oil hydraulic cylinder 10, described two-way oil circuit separates respectively a branch road through safety valve 7, 8 are connected to fuel tank 9, safety valve is for guaranteeing that the oil pressure of two-way oil circuit is normal, the second oil circuit is through the first one-way valve 4, unidirectional first oil circuit that is connected to of differential unloading valve 3, fuel tank 9 connects the hydraulic fluid port B of differential unloading valve 3, fuel tank 9 is also by unidirectional second oil circuit that is connected to of the second one-way valve 6.
Wherein, be respectively equipped with pressure transducer on the two-way oil circuit, control system for oil hydraulic cylinder the pressure closed loop of oil hydraulic cylinder is controlled, the piston rod correspondence of oil hydraulic cylinder 10 is provided with displacement transducer 11, controls system for oil hydraulic cylinder the position closed loop of hydraulic cylinder piston rod is controlled.
The utility model control system comprises driven by servomotor module, pump control cylinder module and auxiliary oil way module, and wherein motor drive module comprises actuating motor 1 and servo driver 13, the control that servo driver 13 completes the actuating motor rotating speed and turns to; Pump control cylinder module is comprised of two-way pump 2 and oil hydraulic cylinder 10, by controlling flow, pressure, the speed that turns to control oil hydraulic cylinder 10, displacement and the direction of two-way pump 2; The auxiliary oil way module plays overload protection and limitation function; comprise that differential unloading valve 3, the first one-way valve 4, the second one-way valve 6 and 9, two one-way valves of fuel tank mainly solve repairing and the draining problem of the asymmetric piston of oil hydraulic cylinder 10 when the cylinder volume is controlled the flow imbalance.For example, for vertically arranged oil hydraulic cylinder, when piston moves downward, be piston rod while stretching out, the discharge capacity of low pressure oil is less than person who lives in exile's amount of high pressure oil, and the oil drain quantity of oil hydraulic cylinder 10 rod chambers is less than the oil inlet quantity of rodless cavity, occur that low pressure oil is for shortage of oil, the loop oil pressure reduces, and the second one-way valve 6 is opened automatically, by the mode by fuel tank 9 oil suctions to the low tension loop repairing; Otherwise, when piston moves upward, when piston rod is return, the hydraulic oil discharge of rodless cavity is greater than person who lives in exile's amount of rod chamber, now differential unloading valve 3 is opened, and carries out emptying, makes the inflow and outflow hydraulic pressure oil mass of two-way pump 2 keep balance.Displacement signal from displacement transducer 11 is sent into servo driver after treatment, according to the state-driven actuating motor of piston rod, reaches the purpose of the compound control of pressure flow.
The utility model to the control of the direction of hydraulic pressure, flow and oil hydraulic cylinder by the actuating motor positive and reverse steering with and closed loop control mode realize.Wherein, the first one-way valve 4 only guarantees when oil hydraulic cylinder 10 piston rods stretch out, and the fluid that rod chamber is discharged is unidirectional enters oil hydraulic cylinder 10 rodless cavities, and rodless cavity fluid can not flow into rod chamber.
Concrete control below by working principle explanation the utility model to oil hydraulic cylinder 10:
At first stretching out of piston rod be described, while stretching out due to piston rod, the oil mass that oil hydraulic cylinder 10 rod chambers (loculus) are discharged is less than the required oil mass of rodless cavity (large chamber), therefore must repairing.Piston rod stretches out and comprises following two kinds of patterns:
Piston rod stretches out fast: actuating motor 1 drives two-way pump 2 forwards, the fluid of fuel tank 9 flows through the second one-way valve 6, entered the oil sucting cavity of two-way pump 2 by the second oil circuit, entered again the rodless cavity of oil hydraulic cylinder 10 by the first oil circuit, now differential unloading valve 3 one sides obtain electric, hydraulic fluid port P connects to hydraulic fluid port A, the oil that rod chamber is discharged directly supplements oil mass to oil hydraulic cylinder 10 rodless cavities through the first one-way valve 4 and differential unloading valve 3, form differential circuit, by the oil-feed of described two road direction rodless cavities, realize stretching out fast of piston rod; Wherein, rod chamber has the second oil circuit to be communicated with two-way pump in theory, when stretching out fast, the fluid that rodless cavity needs is greater than rod chamber, so also need to repairing from fuel tank, because differential unloading valve is opened, here regarding rod chamber fluid as taps into into rodless cavity through the first one-way valve 4, differential unloading valve 3 fast directs, form differential circuit, two-way pump 2 sucks another part fluid from fuel tank 9 and supplies with rodless cavity as repairing simultaneously, two paths are realized the quick oil feeding of rodless cavity, make rodless cavity fluid promote fast piston rod and stretch out.
Piston rod stretches out at a slow speed: actuating motor 1 drives two-way pump 2 forwards, differential unloading valve 3 must not be electric, keep the Median Function locking, the hydraulic fluid port Close All, the second one-way valve 6 is opened, the fluid that fluid in fuel tank 9 is discharged with oil hydraulic cylinder 10 rod chambers through the second one-way valve 6 flows into the oil sucting cavity of two-way pump 2 together with the second oil circuit, and the oil-discharging cavity output fluid of two-way pump 2 is to oil hydraulic cylinder 10 rodless cavities, and piston rod stretches out.With the pattern of stretching out fast, compare, fluid only has a path, road, all passes through two-way pump 2 and the first oil circuit flows into rodless cavity again, and speed is slower than quick mode.
While stretching out due to piston rod, enter the oil that comprises the rod chamber discharge of rodless cavity and repairing two-part of fuel tank 9, therefore, when piston rod is return, the oil mass that rodless cavity (large chamber) is discharged is greater than the required oil mass of rod chamber (loculus), therefore needs draining:
Piston rod is return: actuating motor 1 drives two-way pump 2 reversions, the fluid of oil hydraulic cylinder 10 rodless cavities flows to the oil sucting cavity of two-way pump 2 through the first oil circuit, flow into oil hydraulic cylinder 10 rod chambers by the second oil circuit again, the drive piston rod is return, now differential unloading valve 3 one sides obtain electric, hydraulic fluid port P connects to hydraulic fluid port B, a part of fluid of rodless cavity simultaneously by the hydraulic fluid port B earial drainage of differential unloading valve 3 to fuel tank 9.
When wherein piston rod is return, by the rotating speed to actuating motor 1, control, control the fluid changes in flow rate that two-way pump 2 is discharged, realize oil hydraulic cylinder 10 piston rods are return the control of speed.
The utility model can effectively solve the flow nonsymmetry problem in the pump control hydraulic control system, is applicable to the oil hydraulic cylinder of vertical or other non-horizontal mounting structure forms.
Claims (3)
1. the oil hydraulic cylinder of directly driving type servo-pump control electricity liquid combination drive is controlled system, it is characterized in that comprising actuating motor (1), two-way pump (2), differential unloading valve (3), the first one-way valve (4), the second one-way valve (6), fuel tank (9), oil hydraulic cylinder (10) and servo driver (13), the long-pending ratio of the rod end chamber annular cross-sectional area of oil hydraulic cylinder (10) and piston cross-section is not 1, servo driver (13) connects actuating motor (1), the output of actuating motor (1) connects two-way pump (2), two-way pump (2) minute two-way oil circuit, the first oil circuit is connected to the rodless cavity of oil hydraulic cylinder (10), the second oil circuit is connected to the rod chamber of oil hydraulic cylinder (10), described two-way oil circuit separates respectively a branch road and is connected to fuel tank (9) through safety valve, the second oil circuit is through the first one-way valve (4), unidirectional first oil circuit that is connected to of differential unloading valve (3), fuel tank (9) connects the hydraulic fluid port B of differential unloading valve (3), fuel tank (9) is also by unidirectional second oil circuit that is connected to of the second one-way valve (6).
2. the oil hydraulic cylinder of directly driving type servo-pump control electricity liquid according to claim 1 combination drive is controlled system, it is characterized in that being respectively equipped with pressure transducer on described two-way oil circuit.
3. the oil hydraulic cylinder of directly driving type servo-pump control electricity liquid according to claim 1 and 2 combination drive is controlled system, it is characterized in that the piston rod correspondence of oil hydraulic cylinder (10) is provided with displacement transducer (11).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2013203512784U CN203362711U (en) | 2013-06-18 | 2013-06-18 | Hydraulic cylinder control system conducting direct driving type servo pump control electro-hydraulic combination driving |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2013203512784U CN203362711U (en) | 2013-06-18 | 2013-06-18 | Hydraulic cylinder control system conducting direct driving type servo pump control electro-hydraulic combination driving |
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| CN203362711U true CN203362711U (en) | 2013-12-25 |
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| CN2013203512784U Expired - Lifetime CN203362711U (en) | 2013-06-18 | 2013-06-18 | Hydraulic cylinder control system conducting direct driving type servo pump control electro-hydraulic combination driving |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103307060A (en) * | 2013-06-18 | 2013-09-18 | 南京埃尔法电液技术有限公司 | Direct drive type servo pump control electro-hydraulic combined driving hydraulic cylinder control system and control method |
| CN107651005A (en) * | 2017-09-30 | 2018-02-02 | 江苏大学 | The electro-hydraulic mixing servo steering system and its control method of a kind of four-wheel walking machine |
| CN109139584A (en) * | 2018-11-05 | 2019-01-04 | 深圳航天科技创新研究院 | Pump valve multiplex control system and method |
-
2013
- 2013-06-18 CN CN2013203512784U patent/CN203362711U/en not_active Expired - Lifetime
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103307060A (en) * | 2013-06-18 | 2013-09-18 | 南京埃尔法电液技术有限公司 | Direct drive type servo pump control electro-hydraulic combined driving hydraulic cylinder control system and control method |
| CN103307060B (en) * | 2013-06-18 | 2016-02-03 | 南京埃斯顿自动化股份有限公司 | The oil hydraulic cylinder control system of directly driving type servo-pump control electricity liquid combination drive and controlling method |
| CN107651005A (en) * | 2017-09-30 | 2018-02-02 | 江苏大学 | The electro-hydraulic mixing servo steering system and its control method of a kind of four-wheel walking machine |
| CN109139584A (en) * | 2018-11-05 | 2019-01-04 | 深圳航天科技创新研究院 | Pump valve multiplex control system and method |
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| Date | Code | Title | Description |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C41 | Transfer of patent application or patent right or utility model | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20151106 Address after: 211100 Jiangning Economic Development Zone, Jiangsu Province, general Avenue, No. 155, No. Patentee after: NANJING ESTUN AUTOMATION Co. Address before: 211102 No. 178 Yan Hu Road, Jiangning Development Zone, Jiangsu, Nanjing, China Patentee before: Nanjing Alpha Electro-hydraulic Technology Co.,Ltd. Patentee before: NANJING ESTUN AUTOMATION Co. |
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| CX01 | Expiry of patent term |
Granted publication date: 20131225 |
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| CX01 | Expiry of patent term |