CN111421871A - Closed type electro-hydraulic control system of hydraulic motor driven press machine - Google Patents
Closed type electro-hydraulic control system of hydraulic motor driven press machine Download PDFInfo
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- CN111421871A CN111421871A CN202010435809.2A CN202010435809A CN111421871A CN 111421871 A CN111421871 A CN 111421871A CN 202010435809 A CN202010435809 A CN 202010435809A CN 111421871 A CN111421871 A CN 111421871A
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- 230000001502 supplementing effect Effects 0.000 claims abstract description 65
- 238000003825 pressing Methods 0.000 claims abstract description 30
- 230000001105 regulatory effect Effects 0.000 claims abstract description 17
- 238000000034 method Methods 0.000 claims abstract description 14
- 230000005540 biological transmission Effects 0.000 claims abstract description 10
- 239000003921 oil Substances 0.000 claims description 172
- 238000006073 displacement reaction Methods 0.000 claims description 19
- 230000001276 controlling effect Effects 0.000 claims description 12
- 239000010720 hydraulic oil Substances 0.000 claims description 11
- 239000013589 supplement Substances 0.000 claims description 11
- 238000001514 detection method Methods 0.000 claims description 9
- 239000000725 suspension Substances 0.000 claims 1
- 230000009347 mechanical transmission Effects 0.000 abstract description 3
- 208000006011 Stroke Diseases 0.000 description 5
- 238000004146 energy storage Methods 0.000 description 2
- 230000005484 gravity Effects 0.000 description 2
- 238000005381 potential energy Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
- B30B1/32—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by plungers under fluid pressure
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
- B30B15/16—Control arrangements for fluid-driven presses
- B30B15/18—Control arrangements for fluid-driven presses controlling the reciprocating motion of the ram
- B30B15/20—Control arrangements for fluid-driven presses controlling the reciprocating motion of the ram controlling the speed of the ram, e.g. the speed of the approach, pressing or return strokes
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- Mechanical Engineering (AREA)
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- Press Drives And Press Lines (AREA)
Abstract
The invention discloses a closed electrohydraulic control system of a hydraulic motor driven press, which mainly comprises: the hydraulic control system comprises an electro-hydraulic proportional variable hydraulic motor, an electro-hydraulic proportional variable pump, an oil supplementing pressure regulating valve, a hovering electromagnetic valve, a hovering safety valve, a pressing safety valve, a first oil supplementing one-way valve, a second oil supplementing one-way valve, a first electromagnetic ball valve, a second electromagnetic ball valve, a balance safety valve, a balance accumulator group, a first pressure sensor, a second pressure sensor, a third pressure sensor, a motor and the like. The invention simplifies the electrohydraulic system of the pump control motor hydraulic transmission and the gear rack mechanical transmission hybrid driving press, has high working efficiency, can automatically and steplessly adjust parameters such as pressing force, pressing speed and the like, and has excellent process flexibility.
Description
Technical Field
The invention relates to an electro-hydraulic control system, in particular to a closed electro-hydraulic control system, and particularly relates to a closed electro-hydraulic control system of a hydraulic motor driven press.
Background
The press machine can be divided into a hydraulic press and a mechanical press according to the transmission mode. The transmission mechanism of the hydraulic machine has large power-volume ratio, is easy to realize linear transmission, stepless speed regulation, pressure regulation and maintenance and the like, but the hydraulic machine has lower working efficiency and a system of the high-speed hydraulic machine is very complex; the mechanical press has high working efficiency, but can not output constant pressing force within a large stroke range, and the flexible adjustment of parameters and the long-time pressure maintaining performance of the mechanical press can be realized only by a very complex structure and a system. It is one of the development directions in the art of press technology to combine hydraulic drive with mechanical drive to develop a new hybrid drive mode with both advantages.
Disclosure of Invention
The invention aims to provide a closed type electro-hydraulic control system of a hydraulic motor driven press, which has the advantages of simple system hardware composition, hydraulic transmission and mechanical transmission, high working efficiency and easiness in realizing flexible adjustment of process parameters.
The technical scheme of the invention is as follows:
the invention mainly comprises the following steps: the hydraulic control system comprises an electro-hydraulic proportional variable hydraulic motor, an electro-hydraulic proportional variable pump, an oil supplementing pressure regulating valve, a hovering electromagnetic valve, a hovering safety valve, a pressing safety valve, a first oil supplementing one-way valve, a second oil supplementing one-way valve, a first electromagnetic ball valve, a second electromagnetic ball valve, a balance safety valve, a balance accumulator group, a first pressure sensor, a second pressure sensor, a third pressure sensor, a motor and the like. The output shaft of the electro-hydraulic proportional variable hydraulic motor is coaxially connected with the gear; an oil port A of the electro-hydraulic proportional variable hydraulic motor is communicated with an A port of the electro-hydraulic proportional variable pump, an oil inlet of the pressing safety valve, an oil outlet of the first oil supplementing one-way valve and a detection port of the first pressure sensor; an oil port B of the electro-hydraulic proportional variable hydraulic motor is communicated with an port A of the hovering electromagnetic valve and an oil inlet of the hovering safety valve; the port B of the electro-hydraulic proportional variable pump is communicated with the port P of the hovering electromagnetic valve, an oil outlet of the second oil supplementing one-way valve and a detection port of the second pressure sensor; an oil outlet of the oil supplementing pump is communicated with an oil inlet of the oil supplementing pressure regulating valve, an oil inlet of the first electromagnetic ball valve and an oil inlet of the second electromagnetic ball valve; an oil outlet of the first electromagnetic ball valve is communicated with an oil inlet of the first oil supplementing one-way valve and an oil inlet of the second oil supplementing one-way valve; an oil outlet of the second electromagnetic ball valve is communicated with an oil inlet of the balance safety valve, an oil port of the balance energy accumulator group, a rod cavity of the balance cylinder and a detection port of the third pressure sensor; the rodless cavity of the balance cylinder is communicated with the atmosphere; an oil suction port of the oil supplementing pump, an oil outlet of the oil supplementing pressure regulating valve, an oil outlet of the hovering safety valve, an oil outlet of the pressing safety valve and an oil outlet of the balance safety valve are communicated with the hydraulic oil tank; the motor is coaxially connected with the electro-hydraulic proportional variable pump and the oil replenishing pump.
Further, the invention relates to a closed type electro-hydraulic control system of a hydraulic motor driven press, which is characterized in that: the discharge volume V of the electro-hydraulic proportional variable hydraulic motor can be controlled in a closed loop manner; output flow Q of electro-hydraulic proportional variable pump and pressure difference P of A, B portsABCan be controlled in a closed loop; the rotating speed of the motor can be controlled in a closed loop mode, and the motor can be used as a motor to drag a load and can also be dragged by the load to be in a generator mode; the output torque of the electro-hydraulic proportional variable hydraulic motor and the gear is T, and the transmission ratio of the torque T to the rack output pressing force F is i; the rotating speed of the electro-hydraulic proportional variable hydraulic motor and the gear is n; the above parameters satisfy:
Q=n×V。
F=i×T。
PAB×V=2×π×T。
the control steps of the press machine comprise:
step 1: the hovering electromagnetic valve is electrified, the press machine slide block descends quickly, the gear rotating speed n is high when the press machine slide block descends quickly, the discharge volume V of the electro-hydraulic proportional variable hydraulic motor is reduced and fixed so as to limit the system flow Q, the rotating speed n of the electro-hydraulic proportional variable hydraulic motor is adjusted by controlling the output flow Q of the electro-hydraulic proportional variable pump, and the purpose of controlling the speed of the press machine slide block descending quickly is achieved.
Step 2: the hovering electromagnetic valve is electrified, and the discharge volume V of the electro-hydraulic proportional variable hydraulic motor is adjusted to be P according to the required pressing force FAB/(2×π×F/i)，PABThe system is set to work pressure, at the moment, the displacement V is increased, the rotating speed n is reduced, the electro-hydraulic proportional variable hydraulic motor can output enough torque, and the system is communicated with a hydraulic motorAnd (3) the pressing speed of the sliding block is adjusted by controlling the output flow Q of the electro-hydraulic proportional variable pump, in the step, oil output from the port A of the electro-hydraulic proportional variable pump enters the port A of the electro-hydraulic proportional variable hydraulic motor, oil discharged from the port B of the electro-hydraulic proportional variable hydraulic motor enters the port B of the electro-hydraulic proportional variable pump through a hovering electromagnetic valve, the rotating speed of the motor is controlled to be constant, and the electro-hydraulic proportional variable pump and the oil supplementing pump are dragged.
And step 3: the hovering electromagnetic valve is electrified, the slide block of the press machine presses the workpiece to the set working pressure, the rotating speed of the motor is reduced, and P isABThe holding of the pressing force F is realized by closed-loop regulation of an electro-hydraulic proportional variable pump.
And 4, step 4: the hovering electromagnetic valve is electrified, the discharge volume V of the electro-hydraulic proportional variable hydraulic motor is gradually reduced to a certain fixed value, and then the P is gradually reduced through the electro-hydraulic proportional variable pumpABAnd when the speed is adjusted to 0, the rotation speed of the motor is adjusted to 0.
And 5: the method comprises the following steps that a hovering electromagnetic valve is powered off, an electro-hydraulic proportional variable pump reversely outputs flow Q, at the moment, the discharge capacity V of an electro-hydraulic proportional variable hydraulic motor is smaller, the gear rotating speed n is higher, a press slide block achieves quick return, the return speed of the slide block is adjusted by controlling the output flow Q of the electro-hydraulic proportional variable pump, in the step, oil output from a port B of the electro-hydraulic proportional variable pump enters an oil port B of the electro-hydraulic proportional variable hydraulic motor through the hovering electromagnetic valve, oil discharged from an oil port A of the electro-hydraulic proportional variable hydraulic motor enters a port A of the electro-hydraulic proportional variable pump, the rotating speed of a motor is controlled to be constant, and the electro-hydraulic.
Step 6: when the electromagnetic valve is suspended and the power is off, the discharge volume V of the electro-hydraulic proportional variable hydraulic motor is adjusted to the maximum value, the rotation speed of the motor is adjusted to 0, the output flow Q of the electro-hydraulic proportional variable pump is 0, and the press slide block is suspended.
In the processes of the steps 1 to 6, the first electromagnetic ball valve and the second electromagnetic ball valve are powered off, the oil supplementing pump injects hydraulic oil into the low-pressure side of the closed system through the first oil supplementing one-way valve or the second oil supplementing one-way valve so as to supplement the leakage hydraulic oil in the working process and simultaneously exchange heat and cool, and the oil supplementing pressure is set through the oil supplementing pressure regulating valve.
And 7: if the pressure of the oil in the balanced accumulator group is lower than a set value, the first electromagnetic ball valve and the second electromagnetic ball valve are electrified, the oil supplementing pressure of the balanced system is set through an oil supplementing pressure regulating valve, and an oil supplementing pump supplements pressure oil for the balanced accumulator group; at the moment, the hovering electromagnetic valve is powered off, the rotation speed of the motor is adjusted to 0, the output flow Q of the electro-hydraulic proportional variable pump is 0, the displacement V of the electro-hydraulic proportional variable hydraulic motor is adjusted to the maximum value, and the press slide block hovers.
The invention has the following beneficial effects:
1. according to the invention, the hydraulic transmission of the pump control motor is combined with the mechanical transmission of the gear rack, so that the hybrid driving of the press is realized, the high-frequency secondary stroke can be completed, and the technological parameters of the press are easy to flexibly adjust.
2. The hydraulic transmission part of the invention is a closed pump control motor, adopts a mode that an electro-hydraulic proportional variable pump is matched with an electro-hydraulic proportional variable hydraulic motor, has wide adjustment range of pressing speed, has various matching modes of pressing force and pressing speed, and greatly simplifies the hardware of a hydraulic system.
3. The balance cylinder for balancing the weight of the sliding block assembly is configured, so that the energy is recycled, the useless power consumption is reduced, and the operation process of the press is stable and the impact is small; further cooperate hydraulic pump and motor that the discharge capacity is adjustable, the press possesses the energy consumption management flexibility.
Drawings
FIG. 1 is a schematic diagram of an electro-hydraulic system of the present invention.
Fig. 2 is a schematic view of the structure of the hybrid drive press.
In fig. 1: 301-gear, 304-balance cylinder, 801-electro-hydraulic proportional variable hydraulic motor, 802-electro-hydraulic proportional variable pump, 803-oil supplement pump, 804-oil supplement pressure regulating valve, 805-hovering electromagnetic valve, 806-hovering safety valve, 807-pressing safety valve, 808-first oil supplement one-way valve, 809-second oil supplement one-way valve, 810-first electromagnetic ball valve, 811-second electromagnetic ball valve, 812-balance safety valve, 813-balance accumulator group, 814-first pressure sensor, 815-second pressure sensor, 816-third pressure sensor; 817-electric machine.
In fig. 2: 301-gear, 302-rack, 303-catch wheel, 304-balance cylinder, 305-slide block, 306-guide rail, 307-main frame.
Detailed Description
The invention will be further described with reference to the accompanying drawings.
Referring to the attached fig. 1 and 2, the invention comprises: the hydraulic control system comprises an electro-hydraulic proportional variable hydraulic motor 801, an electro-hydraulic proportional variable pump 802, an oil supplementing pump 803, an oil supplementing pressure regulating valve 804, a hovering electromagnetic valve 805, a hovering safety valve 806, a pressing safety valve 807, a first oil supplementing one-way valve 808, a second oil supplementing one-way valve 809, a first electromagnetic ball valve 810, a second electromagnetic ball valve 811, a balance safety valve 812, a balance accumulator group 813, a first pressure sensor 814, a second pressure sensor 815, a third pressure sensor 816, a motor 817 and the like. An output shaft of the electro-hydraulic proportional variable hydraulic motor 801 is coaxially coupled with the gear 301; an oil port A of the electro-hydraulic proportional variable hydraulic motor 801 is communicated with an A port of the electro-hydraulic proportional variable pump 802, an oil inlet of the pressing safety valve 807, an oil outlet of the first oil supplementing check valve 808 and a detection port of the first pressure sensor 814; an oil port B of the electro-hydraulic proportional variable hydraulic motor 801 is communicated with an oil port A of the hovering electromagnetic valve 805 and an oil inlet of the hovering safety valve 806; a port B of the electro-hydraulic proportional variable pump 802 is communicated with a port P of the hovering electromagnetic valve 805, an oil outlet of a second oil supplementing one-way valve 809 and a detection port of a second pressure sensor 815; an oil outlet of the oil supplementing pump 803 is communicated with an oil inlet of the oil supplementing pressure regulating valve 804, an oil inlet of the first electromagnetic ball valve 810 and an oil inlet of the second electromagnetic ball valve 811; an oil outlet of the first electromagnetic ball valve 810 is communicated with an oil inlet of a first oil supplementing one-way valve 808 and an oil inlet of a second oil supplementing one-way valve 809; an oil outlet of the second electromagnetic ball valve 811 is communicated with an oil inlet of the balance safety valve 812, an oil outlet of the balance accumulator group 813, a rod cavity of the balance cylinder 304 and a detection port of the third pressure sensor 816; the rodless cavity of the balancing cylinder 304 is vented to atmosphere; an oil suction port of the oil supplementing pump 803, an oil outlet of the oil supplementing pressure regulating valve 804, an oil outlet of the hovering safety valve 806, an oil outlet of the pressing safety valve 807 and an oil outlet of the balance safety valve 812 are communicated with a hydraulic oil tank; the motor 817 is coaxially connected with the electro-hydraulic proportional variable pump 802 and the oil replenishing pump 803.
The displacement V of the electro-hydraulic proportional variable hydraulic motor 801 can be controlled in a closed loop manner; output of electro-hydraulic proportional variable pump 802Flow rate Q and pressure difference P at port A, BABCan be controlled in a closed loop; the rotating speed of the motor 817 can be controlled in a closed loop mode, and can be used as a motor to drag a load or dragged by the load to be in a generator mode; the output torque of the electro-hydraulic proportional variable hydraulic motor 801 and the gear 301 is T, and the transmission ratio of the torque T to the output pressing force F of the rack 302 is i; the rotating speeds of the electro-hydraulic proportional variable hydraulic motor 801 and the gear 301 are n; the above parameters satisfy:
Q=n×V。
F=i×T。
PAB×V=2×π×T。
the working principle of the invention is illustrated by taking a single working cycle of a press as an example:
1. press ram quick-down
The hovering solenoid valve 805 is electrified, the press machine slide block 305 moves downwards in an accelerated manner under the action of gravity, the rack 302 drives the gear 301 to rotate so as to drive the coaxial electro-hydraulic proportional variable hydraulic motor 801 to rotate forwards, oil discharged from an oil port B of the electro-hydraulic proportional variable hydraulic motor 801 enters an oil port B of the electro-hydraulic proportional variable pump 802 through the hovering solenoid valve 805, oil output from an oil port A of the electro-hydraulic proportional variable pump 802 enters an oil port A of the electro-hydraulic proportional variable hydraulic motor 801, the rotating speed n of the gear 301 is high when the speed is fast, the displacement V of the electro-hydraulic proportional variable hydraulic motor 801 is reduced and fixed so as to limit the system flow Q, the rotating speed n of the electro-hydraulic proportional variable hydraulic motor 801 is adjusted by controlling the output flow Q of the electro-hydraulic proportional variable pump 802, further, the purpose of controlling the fast descending speed of the press ram 305 is achieved, and the rotating speed of the motor 817 is controlled to be constant and is dragged by the electro-hydraulic proportional variable pump 802 to be in a generator mode.
2. Ram feed of press
The hovering electromagnetic valve 805 is electrified, and the displacement V of the electro-hydraulic proportional variable hydraulic motor 801 is adjusted to be P according to the required pressing force FAB/(2×π×F/i)，PABThe working pressure of the system is set, the displacement V is increased and the rotating speed n is reduced, the electro-hydraulic proportional variable hydraulic motor 801 can output enough torque, oil output from the port A of the electro-hydraulic proportional variable pump 802 enters the oil port A of the electro-hydraulic proportional variable hydraulic motor 801, and oil discharged from the oil port B of the electro-hydraulic proportional variable hydraulic motor 801Oil enters a port B of the electro-hydraulic proportional variable pump 802 through the hovering electromagnetic valve 805, the pressing speed of the sliding block 305 is adjusted by controlling the output flow Q of the electro-hydraulic proportional variable pump 802, and the rotating speed of the motor 817 is controlled to be constant to drag the electro-hydraulic proportional variable pump 802 and the oil supplementing pump 803.
3. Pressure maintaining device
When the pressing force reaches a set value, pressure maintaining control can be carried out, the hovering electromagnetic valve 805 is electrified, the rotating speed of the motor 817 is reduced, the displacement V of the electro-hydraulic proportional variable hydraulic motor 801 is kept constant, and P isABThe holding of the pressing force F is realized by closed-loop regulation of the electro-hydraulic proportional variable pump 802, and the pressure holding time is set according to the process requirement.
4. Pressure relief
When the pressure maintaining time reaches a set value, the hovering solenoid valve 805 is energized, the displacement V of the electro-hydraulic proportional variable hydraulic motor 801 is gradually reduced to a certain fixed value, and then the P is gradually reduced by the electro-hydraulic proportional variable pump 802ABAnd (4) adjusting to 0 according to a preset rule, and adjusting the rotation speed of the motor to 0.
5. Press ram return stroke
After pressure relief is completed, the hovering solenoid valve 805 is powered off, the electro-hydraulic proportional variable pump 802 reversely outputs the flow Q, oil output from the port B of the electro-hydraulic proportional variable pump 802 enters the oil port B of the electro-hydraulic proportional variable hydraulic motor 801 through the hovering solenoid valve 805, oil discharged from the oil port A of the electro-hydraulic proportional variable hydraulic motor 801 enters the port A of the electro-hydraulic proportional variable pump 802, at the moment, the displacement V of the electro-hydraulic proportional variable hydraulic motor 801 is small, the rotating speed n of the gear 301 is high, the press machine sliding block 305 achieves quick return stroke, the return stroke speed of the sliding block 305 is adjusted by controlling the output flow Q of the electro-hydraulic proportional variable pump 802, the rotating speed of the motor 817 is controlled to be constant, and the electro-hydraulic proportional variable.
6. Press ram hovering
When the hovering electromagnetic valve 805 is powered off, the displacement V of the electro-hydraulic proportional variable hydraulic motor 801 is adjusted to the maximum value, the rotating speed of the motor 817 is adjusted to 0, the output flow Q of the electro-hydraulic proportional variable pump 802 is 0, and the press slide block 305 hovers.
In the above 6 working processes, the first electromagnetic ball valve 810 and the second electromagnetic ball valve 811 are both powered off, the oil supplementing pump 803 injects hydraulic oil into the low-pressure side of the closed system through the first oil supplementing check valve 808 or the second oil supplementing check valve 809 so as to supplement the hydraulic oil leaked in the working process and perform heat exchange and cooling at the same time, and the oil supplementing pressure is set through the oil supplementing pressure regulating valve 804.
7. Oil supplement for balance system
If the oil pressure in the balance accumulator group 813 is lower than a set value, the first electromagnetic ball valve 810 and the second electromagnetic ball valve 811 are electrified, the oil supplementing pressure of the balance system is set through the oil supplementing pressure regulating valve 804, and the oil supplementing pump 803 supplements pressure oil for the balance accumulator group 813; at this time, the hovering solenoid valve 805 is powered off, the rotating speed of the motor 817 is adjusted to 0, the output flow Q of the electro-hydraulic proportional variable pump 802 is 0, the displacement V of the electro-hydraulic proportional variable hydraulic motor 801 is adjusted to the maximum value, and the press slide block 305 hovers.
Part of the gravity of the assembly of the slide block 305 is always counteracted by the force output by the balance cylinder 304 during the operation of the press; when the sliding block 305 moves downwards, hydraulic oil in the rodless cavity of the balance cylinder 304 enters the balance energy accumulator group 813, the pressure in the balance energy accumulator group 813 rises, and gravitational potential energy is converted into hydraulic energy; when the sliding block 305 moves upwards, hydraulic oil in the balance energy storage group 813 enters the rodless cavity of the balance cylinder 304, the pressure in the balance energy storage group 813 is reduced, and hydraulic energy is converted into gravitational potential energy. Because leakage of a hydraulic system cannot be avoided, the pressure in the balance accumulator group 813 is reduced after long-term use, and the balance accumulator group 813 can be pressurized by electrifying the first electromagnetic ball valve 810 and the second electromagnetic ball valve 811.
Claims (2)
1. The utility model provides a closed electric hydraulic control system of hydraulic motor drive press which characterized by: the method mainly comprises the following steps: the hydraulic control system comprises an electro-hydraulic proportional variable hydraulic motor (801), an electro-hydraulic proportional variable pump (802), an oil supplementing pump (803), an oil supplementing pressure regulating valve (804), a hovering electromagnetic valve (805), a hovering safety valve (806), a pressing safety valve (807), a first oil supplementing one-way valve (808), a second oil supplementing one-way valve (809), a first electromagnetic ball valve (810), a second electromagnetic ball valve (811), a balance safety valve (812), a balance accumulator group (813), a first pressure sensor (814), a second pressure sensor (815), a third pressure sensor (816) and a motor (817), wherein an output shaft of the electro-hydraulic proportional variable hydraulic motor (801) is coaxially connected with a gear (301); an oil port A of the electro-hydraulic proportional variable hydraulic motor (801) is communicated with an A port of the electro-hydraulic proportional variable pump (802), an oil inlet of the pressing safety valve (807), an oil outlet of the first oil supplementing one-way valve (808) and a detection port of the first pressure sensor (814); an oil port B of the electro-hydraulic proportional variable hydraulic motor (801) is communicated with an port A of the hovering electromagnetic valve (805) and an oil inlet of the hovering safety valve (806); a port B of the electro-hydraulic proportional variable pump (802) is communicated with a port P of the hovering electromagnetic valve (805), an oil outlet of a second oil supplementing one-way valve (809) and a detection port of a second pressure sensor (815); an oil outlet of the oil supplementing pump (803) is communicated with an oil inlet of the oil supplementing pressure regulating valve (804), an oil inlet of the first electromagnetic ball valve (810) and an oil inlet of the second electromagnetic ball valve (811); an oil outlet of the first electromagnetic ball valve (810) is communicated with an oil inlet of the first oil supplementing one-way valve (808) and an oil inlet of the second oil supplementing one-way valve (809); an oil outlet of the second electromagnetic ball valve (811) is communicated with an oil inlet of a balance safety valve (812), an oil outlet of a balance energy accumulator group (813), a rod cavity of a balance cylinder (304) and a detection port of a third pressure sensor (816); the rodless cavity of the balancing cylinder (304) is communicated with the atmosphere; an oil suction port of the oil supplementing pump (803), an oil outlet of the oil supplementing pressure regulating valve (804), an oil outlet of the hovering safety valve (806), an oil outlet of the pressing safety valve (807), and an oil outlet of the balance safety valve (812) are communicated with a hydraulic oil tank; the motor (817) is coaxially connected with the electro-hydraulic proportional variable pump (802) and the oil supplementing pump (803).
2. The closed electro-hydraulic control system of a hydraulic motor driven press as set forth in claim 1, wherein: the displacement V of the electro-hydraulic proportional variable hydraulic motor (801) can be controlled in a closed loop manner; the output flow Q of the electro-hydraulic proportional variable pump (802) and the pressure difference P of the A, B portABCan be controlled in a closed loop; the rotating speed of the motor (817) can be controlled in a closed loop mode, and can be used as a motor to drag a load or dragged by the load to be in a generator mode; electro-hydraulic proportional variable hydraulic motor (801) and gear (301)The output torque of the gear is T, and the transmission ratio of the torque T to the output pressing force F of the rack (302) is i; the rotating speeds of the electro-hydraulic proportional variable hydraulic motor (801) and the gear (301) are n; the above parameters satisfy:
Q=n×V；
F=i×T；
PAB×V=2×π×T；
the control steps of the press machine comprise:
step 1: the hovering electromagnetic valve (805) is electrified, the press slide block (305) is quickly descended, the rotating speed n of the gear (301) is higher when the press slide block is quickly descended, the displacement V of the electro-hydraulic proportional variable hydraulic motor (801) is reduced and fixed so as to limit the system flow Q, the rotating speed n of the electro-hydraulic proportional variable hydraulic motor (801) is adjusted by controlling the output flow Q of the electro-hydraulic proportional variable pump (802), the purpose of controlling the fast descending speed of the press slide block (305) is further achieved, in the step, oil output from an opening A of the electro-hydraulic proportional variable pump (802) enters an oil opening A of the electro-hydraulic proportional variable hydraulic motor (801), oil discharged from an oil opening B of the electro-hydraulic proportional variable hydraulic motor (801) enters an opening B of the electro-hydraulic proportional variable pump (802) through a hovering electromagnetic valve (805), the rotating speed of a motor (817) is controlled to be constant, and the motor (817) is dragged by the electro-hydraulic proportional variable pump (802) to be in a generator mode;
step 2: the hovering electromagnetic valve (805) is electrified, and the displacement V of the electro-hydraulic proportional variable hydraulic motor (801) is adjusted to be P according to the required pressing force FAB/(2×π×F/i)，PABThe method comprises the steps that working pressure is set by a system, at the moment, the displacement V is increased, the rotating speed n is reduced, the electro-hydraulic proportional variable hydraulic motor (801) can output enough torque, the pressing speed of a sliding block (305) is adjusted by controlling the output flow Q of the electro-hydraulic proportional variable pump (802), in the step, oil output from an opening A of the electro-hydraulic proportional variable pump (802) enters an oil opening A of the electro-hydraulic proportional variable hydraulic motor (801), oil discharged from an oil opening B of the electro-hydraulic proportional variable hydraulic motor (801) enters an opening B of the electro-hydraulic proportional variable pump (802) through a hovering electromagnetic valve (805), and the rotating speed of a motor (817) is controlled to be constant to drag the electro-hydraulic proportional variable pump (802) and an oil replenishing pump (803);
and step 3: suspension power failureThe magnetic valve (805) is electrified, the press slide (305) presses the workpiece to set working pressure, the rotating speed of the motor (817) is reduced, and P isABThe holding of the pressing force F is realized by the closed-loop regulation of an electro-hydraulic proportional variable pump (802);
and 4, step 4: the hovering electromagnetic valve (805) is electrified, the displacement V of the electro-hydraulic proportional variable hydraulic motor (801) is gradually reduced to a certain fixed value, and then the P is gradually reduced through the electro-hydraulic proportional variable pump (802)ABAdjusting to 0, and adjusting the rotation speed of the motor (817) to 0;
and 5: the method comprises the following steps that a hovering electromagnetic valve (805) is powered off, an electro-hydraulic proportional variable pump (802) reversely outputs flow Q, at the moment, the displacement V of an electro-hydraulic proportional variable hydraulic motor (801) is small, the rotating speed n of a gear (301) is high, a press slide block (305) achieves quick return, the return speed of the slide block (305) is adjusted by controlling the output flow Q of the electro-hydraulic proportional variable pump (802), in the step, oil output from a port B of the electro-hydraulic proportional variable pump (802) enters an oil port B of the electro-hydraulic proportional variable hydraulic motor (801) through the hovering electromagnetic valve (805), oil discharged from an oil port A of the electro-hydraulic proportional variable hydraulic motor (801) enters a port A of the electro-hydraulic proportional variable pump (802), and the rotating speed of a motor (817) is controlled to be constant to drag the electro-hydraulic proportional variable pump (802);
step 6: when the hovering electromagnetic valve (805) is powered off, the displacement V of the electro-hydraulic proportional variable hydraulic motor (801) is adjusted to the maximum value, the rotation speed of the motor (817) is adjusted to 0, the output flow Q of the electro-hydraulic proportional variable pump (802) is 0, and the press machine sliding block (305) hovers;
in the processes of steps 1 to 6, the first electromagnetic ball valve (810) and the second electromagnetic ball valve (811) are powered off, the oil supplementing pump (803) injects hydraulic oil into the low-pressure side of the closed system through the first oil supplementing one-way valve (808) or the second oil supplementing one-way valve (809) so as to supplement the hydraulic oil leaked in the working process and simultaneously exchange heat and cool, and the oil supplementing pressure is set through the oil supplementing pressure regulating valve (804);
and 7: if the oil pressure in the balance energy accumulator group (813) is lower than a set value, the first electromagnetic ball valve (810) and the second electromagnetic ball valve (811) are electrified, the oil supplementing pressure of a balance system is set through the oil supplementing pressure regulating valve (804), and the oil supplementing pump (803) supplements pressure oil for the balance energy accumulator group (813); at the moment, the hovering electromagnetic valve (805) is powered off, the rotation speed of the motor (817) is adjusted to 0, the output flow Q of the electro-hydraulic proportional variable pump (802) is 0, the displacement V of the electro-hydraulic proportional variable hydraulic motor (801) is adjusted to the maximum value, and the press slide block (305) hovers.
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN117072505A (en) * | 2023-10-18 | 2023-11-17 | 山河智能特种装备有限公司 | Stokehold equipment and energy-saving hydraulic walking closed system thereof |
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| CN117072505A (en) * | 2023-10-18 | 2023-11-17 | 山河智能特种装备有限公司 | Stokehold equipment and energy-saving hydraulic walking closed system thereof |
| CN117072505B (en) * | 2023-10-18 | 2024-02-13 | 山河智能特种装备有限公司 | Stokehold equipment and energy-saving hydraulic walking closed system thereof |
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