CN208634147U - A kind of driving motor directly drives the hydraulic energy-saving system of pump control cylinder with differential effect - Google Patents
A kind of driving motor directly drives the hydraulic energy-saving system of pump control cylinder with differential effect Download PDFInfo
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- CN208634147U CN208634147U CN201821034213.6U CN201821034213U CN208634147U CN 208634147 U CN208634147 U CN 208634147U CN 201821034213 U CN201821034213 U CN 201821034213U CN 208634147 U CN208634147 U CN 208634147U
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Abstract
The utility model provides the hydraulic energy-saving system that a kind of driving motor directly drives pump control cylinder with differential effect, the driver is given by the controller input signal, revolving speed by driving motor described in the driver control and direction again, and then control the flow of the bidirectional hydraulic pump, the final control realized to the hydraulic cylinder.The utility model determines the revolving speed of driving motor according to different operating conditions, and hydraulic fluid flow rate size, avoids hydraulic system restriction loss and spill losses needed for adjusting, system effectiveness is high, and revolving speed is adjustable, and working efficiency not only can be improved, electric energy can also be saved, noise is reduced；Differential connection is used simultaneously, when so that installed power being connected than the no differential in traditional technology, is significantly reduced, and realizes high-speed smooth operation, to improve production efficiency.
Description
Technical field
The utility model relates to mechanical production devices field, especially a kind of high-efficient, the operation is stable and energy-efficient processing
Mechanical hydraulic system.
Background technique
Numerical control machining machine, such as pressure forming machine, bending machine, riveting machine etc., in each course of work, to hydraulic pressure system
The pressure provided of uniting and speed is not also identical.Traditional numerical control machining machine hydraulic system is to determine the phase asynchronous of revolving speed by one
The Metering Flow Control Circuits that motor and a quantitative hydraulic pump are constituted, but in the entire circulation of lathe, including standby mode,
The still lasting output oil liquid of hydraulic pump is through overflow valve oil return box, and in each circulation, when only F.F., work are into return, and system
Useful work is just exported, remaining hydraulic oil all passes through electric proportional pressure control valve and flows back to fuel tank.These traditional processing equipments exist
Following disadvantage:
One, existing processing equipment uses common threephase asynchronous, and revolving speed is basically unchanged, and cannot achieve on-demand fortune
Turn；
Two, the reversal valve of existing numerical control hydraulic system is electric proportional reversing valve, and digital control system will export analog signal
The openings of sizes for controlling electric proportional reversing valve, controls the synchronization accuracy of processing, and the size being open in this way certainly will will cause throttling, produces
Raw unnecessary energy loss causes oil temperature to increase and accelerates；
Three, existing processing equipment hydraulic system, in fast lower operating condition, by under self weight fastly, speed can also be further
Optimization improves；
Therefore, these traditional processing equipment low efficiencys, energy consumption is high, noise is big, not environmentally, and hydraulic oil temperature significantly rises
High and then influence hydraulic oil and the service life to hydraulic system.
On the other hand, the Electrical hydrostatic actuator of Serve Motor Control is because it is in the efficiency of traditional servo valves and flexibility side
The advantage in face and attract attention.But with the raising of required power, the size of servo motor must be increased accordingly, so not
Only increased costs, and precision and dynamic response reduce.
Utility model content
The technical problems to be solved in the utility model is to provide the hydraulic section that a kind of driving motor directly drives pump control cylinder with differential effect
Energy system, revolving speed is adjustable and avoids hydraulic system restriction loss and spill losses, high-speed smooth operation is realized, to improve
Production efficiency.
The utility model is realized in this way: a kind of driving motor directly drives the hydraulic energy-saving system of pump control cylinder with differential effect, including
Hydraulic cylinder, the first control valve, the second control valve, the first check valve, second one-way valve, driving motor, driver, bidirectional hydraulic
Pump, accumulator and controller；
The hydraulic cylinder includes cylinder body, piston and piston rod, and one end of the piston rod is fixedly connected on the piston, institute
It states piston air-tightness to be slidably connected in the cylinder body, and the cylinder interior is divided into first chamber and by the piston
Two chambers；
First control valve includes first interface and second interface；
Second control valve includes third interface and the 4th interface；
The bidirectional hydraulic pump includes first port, second port, drain tap and driving end；The first port, institute
State the outlet of the first check valve, the first interface it is in parallel after be connected to the first chamber；The second port, described second
The second chamber is connected to after the outlet of check valve, the second interface are in parallel；The entrance of first check valve and described
The accumulator is connected to after the entrance of second one-way valve is in parallel；The third interface is connected to first port and first list
To between the outlet of valve, the accumulator is connected to after the drain tap and the 4th interface parallel connection；The driving end connection
In the output end of the driving motor, the driving motor is connected to the driver, the driver, the first control valve,
Two control valves are communicatively coupled to the controller respectively.
Further, first control valve is two-position two-way solenoid valve or bi-bit bi-pass inserted valve.
Further, the driving motor is servo motor, and the driver is servo-driver.
Further, second control valve is two-position two-way solenoid valve or bi-bit bi-pass inserted valve.
It further, further include third control valve and the 4th control valve, the third control valve includes the 5th interface and the
Six interfaces, the 4th control valve include the 7th interface and the 8th interface；5th interface is parallel to first check valve
Outlet and first port, be connected to the first chamber after the 6th interface, first interface are in parallel；7th interface is simultaneously
It is coupled to the outlet and second port of the second one-way valve, is connected to after the 8th interface and second interface parallel connection described
Second chamber；The third control valve and the 4th control valve are also communicatively coupled to the controller respectively.
Further, the third control valve is two-position two-way solenoid valve or bi-bit bi-pass inserted valve.
Further, the 4th control valve is two-position two-way solenoid valve or bi-bit bi-pass inserted valve.
Further, it further include pressure switch, the pressure switch is parallel to the first interface, and the pressure
Relay is also communicatively coupled to the controller.
The utility model have the advantages that the utility model by the controller input signal to the driver,
Revolving speed by driving motor described in the driver control and direction again, and then the flow of the bidirectional hydraulic pump is controlled, most
The control to the hydraulic cylinder is realized eventually.The utility model determines the revolving speed of driving motor according to different operating conditions, needed for adjusting
Hydraulic fluid flow rate size, avoids hydraulic system restriction loss and spill losses, and system effectiveness is high, and revolving speed is adjustable, not only can be with
Working efficiency is improved, electric energy can also be saved, reduces noise；Differential connection is used simultaneously, so that installed power compares traditional technology
In no differential connection when, significantly reduce, and realize high-speed smooth operation, to improve production efficiency.
Detailed description of the invention
The utility model is further described in conjunction with the embodiments with reference to the accompanying drawings.
Fig. 1 is the schematic diagram of hydraulic energy-saving system described in the utility model.
Oil circuit schematic diagram when Fig. 2 is F.F. described in the utility model.
Fig. 3 be work described in the utility model into when oil circuit schematic diagram.
Oil circuit schematic diagram when Fig. 4 is rewind described in the utility model.
Fig. 5 is the displacement versus time relation schematic diagram of piston rod described in the utility model.
Fig. 6 is load force-length velocity relation schematic diagram after piston rod described in the utility model is connected to load.
Fig. 7 is the effect diagram that hydraulic energy-saving system described in the utility model is mounted on industrial machinery arm.
In figure: 1, hydraulic energy-saving system；10, hydraulic cylinder；101, cylinder body；102, piston；103, piston rod；104, the first chamber
Room；105, second chamber；11, the first control valve；111, first interface；112, second interface；12, the second control valve；121,
Three interfaces；122, the 4th interface；13, the first check valve；14, second one-way valve；15, driving motor；16, driver；17, two-way
Hydraulic pump；171, first port；172, second port；173, drain tap；174, end is driven；18, accumulator；19, controller；
20, third control valve；201, the 5th interface；202, the 6th interface；21, the 4th control valve；211, the 7th interface；212, it the 8th connects
Mouthful；22, pressure switch.
Specific embodiment
It please refers to shown in Fig. 1 to Fig. 7, the utility model provides the hydraulic energy-saving that a kind of driving motor directly drives pump control cylinder with differential effect
System, including hydraulic cylinder 10, the first control valve 11, the second control valve 12, the first check valve 13, second one-way valve 14, driving electricity
Machine 15, driver 16, bidirectional hydraulic pump 17, accumulator 18 and controller 19；
The hydraulic cylinder 10 includes cylinder body 101, piston 102 and piston rod 103, and one end of the piston rod 103 is fixed to be connected
It is connected to the piston 102,102 air-tightness of piston is slidably connected in the cylinder body 101, and the piston 102 will
It is divided into first chamber 104 and second chamber 105 inside the cylinder body 101；Due to the presence of the piston rod 103, so that described
First chamber 104 and second chamber 105 are unsymmetric structure, so that the hydraulic cylinder 10 is asymmetrical cylinder 10, i.e.,
The hydraulic cylinder 10 is differential hydro cylinder 10；
First control valve 11 includes first interface 111 and second interface 112；
Second control valve 12 includes third interface 121 and the 4th interface 122；
The bidirectional hydraulic pump 17 includes first port 171, second port 172, drain tap 173 and driving end 174；Institute
The first chamber is connected to after stating first port 171, the outlet of first check valve 13,111 parallel connection of the first interface
104；Described is connected to after the second port 172, the outlet of the second one-way valve 14,112 parallel connection of the second interface
Two chambers 105；The accumulation of energy is connected to after the entrance of first check valve 13 and the entrance of the second one-way valve 14 are in parallel
Device 18；The third interface 121 is connected between first port 171 and the outlet of first check valve 13, the drain tap
17 and 122 parallel connection of the 4th interface after be connected to the accumulator 18；The driving end 174 is connected to the driving motor 15
Output end, the driving motor 15 is connected to the driver 16, the driver 16, the control of the first control valve 11, second
Valve 12 is communicatively coupled to the controller 19 respectively.
In a specific embodiment, the bidirectional hydraulic pump 17 is two-way quantitative pump 17, can also both be made as pump
For motor use.The piston rod 103 is connected to load, and described by setting close to switch or electrical travel switch in advance
The stroke of piston rod 103, and the trip Switch Communication is connected to the controller 19.The utility model passes through the controller
19 input signals give the driver 16, then revolving speed and the direction of the driving motor 15 are controlled by the driver 16, into
And the flow of the bidirectional hydraulic pump 17 is controlled, the final control realized to the hydraulic cylinder 10.The utility model is according to difference
Operating condition determines the revolving speed of driving motor 15, and hydraulic fluid flow rate size needed for adjusting avoids flow restriction loss and overflow damage
It loses, system effectiveness is high.It is simultaneously free travel when equipment is started to work, i.e., only needs to overcome 10 resistance of hydraulic cylinder, the piston
Bar 103 quickly stretches out, and first control valve 11 is connected at this time, realizes differential connection, as shown in Fig. 2, differential fast to realize
Into so that not only can also accelerate to glide, realize under the action of pressure oil by under self weight fastly in fast lower operating condition
High-speed smooth operation, to improve production efficiency.And when encountering workpiece, hydraulic energy-saving system 1 described in the utility model
Pressure can increase, the torque of the driving motor will increase, at this time the controller 19 according to the driving motor 15 turn
Square increase judges that load encounters workpiece, and first control valve 11 is closed, so that the hydraulic energy-saving system 1 enters
Work is into operating condition, as shown in figure 3,15 speed of driving motor reduces at this time, realizes the processing of the big power output of low speed, to be done
When, by switching oil circuit close to switch or electrical travel switch, prior snapback, i.e. rewind, as shown in Figure 4.
The utility model uses driving motor 15 and drives two-way quantitative pump 17 to realize the closed system of pump control cylinder, simultaneously
The portability design for realizing power unit, that is, simplify fuel tank and alleviate weight, reduce environmental pollution, can be directly used for machine
The riveting etc. of device hand.
Working efficiency not only can be improved since revolving speed is adjustable in the driving motor 15 that the utility model uses, and can also save
About electric energy reduces noise.
As shown in Figure 5 and Figure 6, when using the fast forward speed of differential connection as rewind speeds, the dress of the utility model
When no differential in machine power ratio traditional technology connects, significantly reduce, for example, installed power halves.It is practical using this at this time
The installed power of novel equipment is only the big person in A point or B point, rather than the product of maximum output power and maximum speed, with
Reduce installed power, reduce 15 size of driving motor, there is better dynamic property and lightweight.
Since the hydraulic cylinder 10 is asymmetrical cylinder 10, the utility model uses 13 He of the first check valve
Second one-way valve 14 is combined control, to balance the flow of the first chamber 104 and second chamber 105.Due to described
The effective area of first chamber 104 is greater than the effective area of the second chamber 105, when oil liquid is flowed from the first chamber 104
When to the second chamber 105, it is extra that oil liquid has, and the controller 19 controls second control valve 12 and is connected at this time, extra
Oil liquid flow into the accumulator 18 and stored from second control valve 12；When oil liquid is flowed from the second chamber 105
When to the first chamber 104, the oil liquid in the accumulator 18 is needed to be supplemented at this time, there are two types of situation, situation one, when
When the pressure of first check valve 13 is greater than the pressure of the second one-way valve 14, the second one-way valve 14 is switched on, oil
Liquid flows to the second port 172 through the second one-way valve 14 from the accumulator 18 and carries out oil liquid supplement；Situation two works as institute
State the first check valve 13 pressure be less than the second one-way valve 14 pressure when, first check valve 13 be switched on, oil liquid
It flows out, is supplemented in the first chamber 104, to realize the first chamber 104 and second from first check valve 13
The flow equilibrium of chamber 105 achievees the purpose that accurately to control.And second control valve 12 can also prevent from generating suction when low pressure
Empty phenomenon.
The utility model is adopted instead of external large tank since the accumulator 18 is small in size using the accumulator 18
Reduce installed power with differential F.F., and then reduces motor size, so that the hydraulic-driven module lightweight of pump control cylinder, it can be direct
The end for being mounted on industrial machinery arm carries out the processing such as riveting, as shown in Figure 7.
The utility model can also make full use of the power of driving motor 15, improve the control precision and dynamic property of system,
It is more efficient compared with conventional power system, more energy efficient, the advantages such as hydraulic oil temperature rise is low.
The utility model when the bidirectional hydraulic pump 17 hypertonia when, by the drain tap 173 by oil liquid arrange to
The accumulator 18 carries out pressure release, prevents the shell of the bidirectional hydraulic pump 17 from rupturing, guarantees safety.
In specific implementation, a preferable embodiment: first control valve 11 is two-position two-way solenoid valve 11 or two
Position two-way plug-in valve 11.Two-position two-way solenoid valve 11 is used when small flow, when big flow, using bi-bit bi-pass inserted valve
11。
The driving motor 15 is servo motor 15, and the driver 16 is servo-driver 16.The driving motor 15
It may be implemented to adjust revolving speed using servo motor 15, achieve the purpose that accurately to control, control precision is high.
Second control valve 12 is two-position two-way solenoid valve 12 or bi-bit bi-pass inserted valve 12.It is used when small flow
Two-position two-way solenoid valve 12, when big flow, using bi-bit bi-pass inserted valve 12.
It further include third control valve 20 and the 4th control valve 21, the third control valve 20 includes the 5th interface 201 and the
Six interfaces 202, the 4th control valve 21 include the 7th interface 211 and the 8th interface 212；5th interface 201 is parallel to
The outlet and first port 171 of first check valve 13, are connected to institute after the 6th interface 202,111 parallel connection of first interface
State first chamber 104；7th interface 211 is parallel to the outlet and second port 172 of the second one-way valve 14, and described
The second chamber 105 is connected to after 112 parallel connection of eight interfaces 212 and the second interface；The third control valve 20 and the 4th
Control valve 21 is also communicatively coupled to the controller 19 respectively.It will be described by the third control valve 20, the 4th control valve 21
Hydraulic cylinder 10 locks, and avoids the sliding due to caused by the leakage of bidirectional hydraulic pump 17.
The third control valve 20 is two-position two-way solenoid valve 20 or bi-bit bi-pass inserted valve 20.It is used when small flow
Two-position two-way solenoid valve 20, when big flow, using bi-bit bi-pass inserted valve 20.
4th control valve 21 is two-position two-way solenoid valve 21 or bi-bit bi-pass inserted valve 21.It is used when small flow
Two-position two-way solenoid valve 21, when big flow, using bi-bit bi-pass inserted valve 21.
Further include pressure switch 22, the pressure switch 22 is parallel to the first interface 111, and the pressure after
Electric appliance 22 is also communicatively coupled to the controller 19.First control valve can be directly measured by the pressure switch 22
The pressure change of pipeline at 11, when the piston rod 103 quickly stretches out, after encountering workpiece, pressure rise, at this time the pressure after
Pressure value variation is fed directly to the controller 19 by electric appliance 22, and the controller 19 closes first control valve 11
It closes, driving motor described in the ratio of precision changed hence into work into operating condition, the pressure value measured as the pressure switch 22
The precision of the variation of 15 torques is higher, so that control is further accurate.
Specific control principle is as follows:
F.F. operating condition, as shown in Fig. 2, first control valve 11 is connected the controller 19, oil liquid is from described at this time
Second chamber 105 flows out, and flows directly into the first chamber 104 by first control valve 11, and described first is unidirectional at this time
Pressure at valve 13 is greater than the pressure at the second one-way valve 14, and the second one-way valve 14 is connected, in the accumulator 18
Oil liquid flow to bidirectional hydraulic pump 17 through the second one-way valve 14, be delivered to described first by bidirectional hydraulic pump 17
In chamber 104, to realize flow equilibrium.
Work is closed as shown in figure 3, the controller 19 controls first control valve 11 into operating condition, and oil liquid is from described the
The outflow of two chambers 105, flows to the bidirectional hydraulic pump 17, and the pressure at first check valve 13 is greater than the second one-way valve
Pressure at 14, the oil liquid in the accumulator 18 converges into the bidirectional hydraulic pump 17 from the second one-way valve 14, by institute
It states bidirectional hydraulic pump 17 oil liquid is delivered in the first chamber 104, to realize flow equilibrium.
Rewind operating condition, as shown in figure 4, first control valve 11 continues to remain turned-off, the controller 19 is by described
Two control valves 12 are opened, and oil liquid is flowed out from the first chamber 104, and a part is delivered to described by bidirectional hydraulic pump 17
Second chamber 105, extra oil liquid flows in the accumulator 18 from second control valve 12, to realize flow equilibrium.
Although those familiar with the art answers the foregoing describe specific embodiment of the present utility model
Working as understanding, we are merely exemplary described specific embodiment, rather than for the limit to the scope of the utility model
Fixed, those skilled in the art modification and variation equivalent made by the spirit according to the utility model all should
Cover in the scope of the claimed protection of the utility model.
Claims (8)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821034213.6U CN208634147U (en) | 2018-07-02 | 2018-07-02 | A kind of driving motor directly drives the hydraulic energy-saving system of pump control cylinder with differential effect |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821034213.6U CN208634147U (en) | 2018-07-02 | 2018-07-02 | A kind of driving motor directly drives the hydraulic energy-saving system of pump control cylinder with differential effect |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN208634147U true CN208634147U (en) | 2019-03-22 |
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ID=65736167
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201821034213.6U Expired - Fee Related CN208634147U (en) | 2018-07-02 | 2018-07-02 | A kind of driving motor directly drives the hydraulic energy-saving system of pump control cylinder with differential effect |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN208634147U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108506286A (en) * | 2018-07-02 | 2018-09-07 | 福建工程学院 | A kind of driving motor directly drives the hydraulic energy-saving system of pump control cylinder with differential effect |
| CN111999065A (en) * | 2020-07-24 | 2020-11-27 | 农业农村部南京农业机械化研究所 | Motor noise vibration test system and test method |
-
2018
- 2018-07-02 CN CN201821034213.6U patent/CN208634147U/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108506286A (en) * | 2018-07-02 | 2018-09-07 | 福建工程学院 | A kind of driving motor directly drives the hydraulic energy-saving system of pump control cylinder with differential effect |
| CN111999065A (en) * | 2020-07-24 | 2020-11-27 | 农业农村部南京农业机械化研究所 | Motor noise vibration test system and test method |
| CN111999065B (en) * | 2020-07-24 | 2022-08-23 | 农业农村部南京农业机械化研究所 | Motor noise vibration test system and test method |
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| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20190322 Termination date: 20190702 |