CN107642511B - Direct-drive electrohydraulic servo die forging hammer control system - Google Patents
Direct-drive electrohydraulic servo die forging hammer control system Download PDFInfo
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- CN107642511B CN107642511B CN201710985213.8A CN201710985213A CN107642511B CN 107642511 B CN107642511 B CN 107642511B CN 201710985213 A CN201710985213 A CN 201710985213A CN 107642511 B CN107642511 B CN 107642511B
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- 238000005242 forging Methods 0.000 title claims abstract description 24
- 238000010009 beating Methods 0.000 claims abstract description 11
- 238000004146 energy storage Methods 0.000 claims description 27
- 238000006073 displacement reaction Methods 0.000 claims description 8
- 230000005611 electricity Effects 0.000 claims description 4
- 239000007788 liquid Substances 0.000 claims 1
- 238000013461 design Methods 0.000 abstract description 4
- 238000012423 maintenance Methods 0.000 abstract description 2
- 239000003921 oil Substances 0.000 description 53
- 239000010720 hydraulic oil Substances 0.000 description 13
- 238000000034 method Methods 0.000 description 12
- 230000008569 process Effects 0.000 description 8
- 230000009471 action Effects 0.000 description 6
- 230000001276 controlling effect Effects 0.000 description 3
- 238000011161 development Methods 0.000 description 3
- 230000001105 regulatory effect Effects 0.000 description 3
- 238000005299 abrasion Methods 0.000 description 2
- 238000001914 filtration Methods 0.000 description 2
- 230000010354 integration Effects 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 238000010248 power generation Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 239000003990 capacitor Substances 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 239000000284 extract Substances 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000011160 research Methods 0.000 description 1
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Abstract
The utility model provides a direct-drive type electrohydraulic servo die forging hammer control system, includes the oil tank, the power component, control element and the pneumatic cylinder that communicate in proper order and form the closed loop, and wherein the pneumatic cylinder includes rodless cavity and has the pole chamber, is provided with the piston in the pole intracavity, and piston and die forging hammer's tup fixed connection, control element includes pilot valve system and direction valve system, and wherein the direction valve system includes the stage of beating direction valves and carries and beat stage direction valves, and the pilot valve system is used for controlling power element is linked together with the stage of beating direction valves or carries and beat stage direction valves. The invention provides a direct-drive electrohydraulic servo die forging hammer control system which has the advantages of high energy efficiency, controllable striking parameters, stable performance, simple hydraulic circuit structure, easy realization of integrated and modularized design, realization of connection without a hydraulic pipeline, reduction of failure rate, reduction of maintenance difficulty and improvement of reliability of the forging hammer.
Description
Technical Field
The invention relates to the technical field of metal plastic forming forging hydraulic equipment, in particular to a direct-drive electrohydraulic servo die forging hammer control system.
Background
The die forging hammer always plays a role of non-grindability in the development of pressure machining in the forging industry, and the die forging hammer is subjected to the development courses of a mechanical hammer, a steam-air hammer, an air hammer and an electro-hydraulic hammer. Because the forging piece forged on the hammer has high forming speed and good metal fluidity, the formed forging piece has higher quality and is continuously used in the mechanical industry. At present, the electric hydraulic hammer is widely used, the traditional electric hydraulic hammer hydraulic system is complex, the loop connection is inconvenient, and the electric hydraulic hammer comprises a striking valve, so that the heating of the system is high, an independent cooling link is required to be designed, the structural complexity and the manufacturing cost are increased, the energy consumption of the system is overlarge, and the efficiency is low. In addition, the traditional hydraulic forging hammer is not very outstanding in the aspect of system control, and there is still room for development and research on the control of the speed and stability of the drop hammer and the lifting hammer.
The direct drive volume control system is also called a direct drive electrohydraulic servo system or an electrohydraulic hybrid executing device. The alternating current variable frequency volume speed regulating loop combines the double advantages of the flexibility of alternating current speed regulation and the large hydraulic output, and has the advantages of wide speed regulating range, high resolution, good energy saving performance, strong anti-pollution capability, easy realization of computer control and the like. The combination of the direct drive volume control system with the die hammer is an effective method for achieving efficient control of the die hammer.
Disclosure of Invention
In order to solve the defects in the prior art, the invention provides the direct-drive electrohydraulic servo die forging hammer control system which has the advantages of high energy efficiency, controllable striking parameters and stable performance, and the hydraulic circuit has a simple structure, is easy to realize integrated and modularized design, realizes connection without a hydraulic pipeline, reduces the failure rate, lightens the difficulty of maintenance and improves the reliability of the forging hammer.
In order to achieve the above purpose, the invention adopts the following specific scheme:
the utility model provides a direct-drive type electrohydraulic servo die forging hammer control system, includes the oil tank, the power component, control element and the pneumatic cylinder that communicate in proper order and form the closed loop, and wherein the pneumatic cylinder includes rodless cavity and has the pole chamber, is provided with the piston in the pole intracavity, and piston and die forging hammer's tup fixed connection, control element includes pilot valve system and direction valve system, and wherein the direction valve system includes the stage of beating direction valves and carries and beat stage direction valves, and the pilot valve system is used for controlling power element is linked together with the stage of beating direction valves or carries and beat stage direction valves.
The striking stage direction valve group comprises a first cartridge valve and a third cartridge valve, the first cartridge valve and the third cartridge valve are two-way cartridge valves, the A1 end of the first cartridge valve is communicated with the rod cavity, the B1 end of the first cartridge valve is communicated with the oil tank, the A3 end of the third cartridge valve is communicated with the pressure end of the power element, and the B3 end of the third cartridge valve is communicated with the rodless cavity.
The direction valve group in the lifting and hammering stage comprises a second cartridge valve and a fourth cartridge valve, the second cartridge valve and the fourth cartridge valve are two-way cartridge valves, the A2 end of the second cartridge valve is communicated with the pressure end of the power element, the B2 end of the second cartridge valve is communicated with the rod cavity, the A4 end of the fourth cartridge valve is communicated with the rodless cavity, and the B4 end of the fourth cartridge valve is communicated with the oil tank.
The pilot valve system comprises a first reversing valve, a second reversing valve, a third reversing valve and a fourth reversing valve, wherein the first reversing valve, the second reversing valve, the third reversing valve and the fourth reversing valve are two-position three-way electromagnetic reversing valves, oil inlets of the first reversing valve, the second reversing valve, the third reversing valve and the fourth reversing valve are all communicated with a pressure end of a power element, a control oil port of the first reversing valve is communicated with a C1 end of the first cartridge valve, an oil return port of the first reversing valve is communicated with the oil tank, a control oil port of the second reversing valve is communicated with a C2 end of the second cartridge valve, an oil return port of the second reversing valve is communicated with the oil tank, a control oil port of the third reversing valve is communicated with a C3 end of the third cartridge valve, an oil return port of the third reversing valve is communicated with a C4 end of the fourth cartridge valve, and an oil return port of the fourth reversing valve is communicated with a C4 end of the oil tank.
A first pilot overflow valve is arranged between the end B3 of the third cartridge valve and the end A4 of the fourth cartridge valve and the rodless cavity, and a second pilot overflow valve is arranged between the end A1 of the first cartridge valve and the end B2 of the second cartridge valve and the rod cavity.
The oil tank is also communicated with a hydraulic motor, the hydraulic motor is in driving connection with a generator, and the generator is also electrically connected with an energy storage indirect converter.
The energy storage indirect converter comprises an energy storage device, and the energy storage device is further electrically connected with an external power supply device.
The power element comprises a constant delivery pump and a servo motor, wherein the oil inlet end of the constant delivery pump is communicated with the oil tank, the oil supply port of the constant delivery pump is communicated with the control element, and the servo motor is electrically connected with the energy storage indirect converter.
The device also comprises a controller and an acquisition element which are electrically connected, wherein the acquisition element comprises a first pressure sensor for acquiring the oil pressure in the rodless cavity, a second pressure sensor for acquiring the oil pressure in the rod cavity and a displacement sensor for detecting the moving distance of the piston, and the controller is electrically connected with the energy storage indirect converter.
The beneficial effects are that:
1. the invention utilizes the servo motor to drive the quantitative pump, and changes the flow and pressure of quantitative output by controlling the rotating speed of the quantitative pump through the servo motor, thereby realizing the flow regulation of the system and achieving the purpose of energy saving;
2. when the forging hammer stops working, the servo motor and the pump also stop, and no efficiency loss and no idle running loss of the operation of the prime motor (mainly the motor) exist;
3. the four high-flow cartridge valves and the four two-position three-way electromagnetic reversing valves are matched for use, the direction valve group in the striking stage and the direction valve group in the beating stage are not interfered with each other, and the switching speed is high;
4. in the striking or hammer lifting process, the hydraulic oil of the oil return tank always passes through the hydraulic motor to drive the hydraulic motor to rotate, the mechanical energy is converted into electric energy by the generator, the energy generated by the generator is continuously conveyed to the energy storage indirect converter, and can be used for supplying power to the servo motor and the controller for the next action, so that the energy is recycled, and the energy utilization rate is improved;
5. the hydraulic accumulator part which is indispensable in the traditional electro-hydraulic hammer is omitted, the installation space is saved, and the structure is more compact;
6. the oil inlet path and the oil return path are respectively provided with a pressure sensor, the pressure sensors feed back signals to the controller, and the controller outputs control signals to the servo driver to control the motor to rotate so as to form pressure closed-loop control on the two oil paths; the piston rod of the hydraulic cylinder is correspondingly provided with a displacement sensor, the displacement sensor feeds back a signal to the controller, and the controller outputs a control signal to the servo driver to control the motor to rotate, so that closed-loop control on the position of the piston rod is formed;
7. the system integration level is high, the modularized design can be realized, and the pipeline connection is greatly reduced, so that the flow loss is reduced, and the influence of pipeline dynamics on a hydraulic system is greatly eliminated;
8. the quantitative pump with low price and high reliability can be selected, so that the requirements on hydraulic oil and filtering are reduced, the abrasion of the pump and the noise of a system are reduced, and the service life and the reliability of the system are improved.
Drawings
FIG. 1 is a schematic view of the overall structure of the present invention;
FIG. 2 is a flow chart of the stored energy indirect conversion process of the present invention.
Reference numerals: 1. the hydraulic energy storage device comprises a constant displacement pump, 2, a servo motor, 3, a hydraulic motor, 4, a generator, 501, a first cartridge valve, 502, a second cartridge valve, 503, a third cartridge valve, 504, a fourth cartridge valve, 601, a first reversing valve, 602, a second reversing valve, 603, a third reversing valve, 604, a fourth reversing valve, 701, a first electromagnet, 702, a second electromagnet, 703, a third electromagnet, 704, a fourth electromagnet, 801, a first pilot overflow valve, 802, a second pilot overflow valve, 9, a hydraulic cylinder, 901, a rodless cavity, 902, a rod cavity, 903, a piston, 10, a hammer, 11, an oil tank, 12, a displacement sensor, 13, a first pressure sensor, 14, a second pressure sensor, 15, a controller, 16 and an energy storage indirect converter.
Detailed Description
Embodiments of the present invention will be described in detail below with reference to the drawings.
As shown in fig. 1, a direct-drive electrohydraulic servo die forging hammer control system comprises an oil tank 11, a power element, a control element and a hydraulic cylinder 9 which are sequentially communicated and form a closed loop, wherein the hydraulic cylinder 9 comprises a rodless cavity 901 and a rod cavity 902, a piston 903 is arranged in the rod cavity 902, the piston 903 is fixedly connected with a hammer head 10 of the die forging hammer, the control element comprises a pilot valve system and a directional valve system, the directional valve system comprises a striking stage directional valve group and a beating stage directional valve group, and the pilot valve system is used for controlling the power element to be communicated with the striking stage directional valve group or the beating stage directional valve group.
The power element comprises a constant delivery pump 1 and a servo motor 2, wherein the oil inlet end of the constant delivery pump 1 is communicated with an oil tank 11, the oil supply port of the constant delivery pump 1 is communicated with the control element, and the servo motor 2 is electrically connected with the energy storage indirect converter. The servo motor 2 is utilized to drive the constant delivery pump 1, and the rotation speed of the constant delivery pump 1 is controlled by the servo motor 2 to change the pressure and flow output by the constant delivery pump, so that the system flow is regulated to achieve the purpose of energy conservation.
The striking stage direction valve group comprises a first cartridge valve 501 and a third cartridge valve 503, wherein the first cartridge valve 501 and the third cartridge valve 503 are two-way cartridge valves, the A1 end of the first cartridge valve 501 is communicated with a rod cavity 902, the B1 end of the first cartridge valve 501 is communicated with an oil tank 11, the A3 end of the third cartridge valve 503 is communicated with the pressure end of a power element, and the B3 end of the third cartridge valve 503 is communicated with a rodless cavity 901. The direction valve group in the hammer stage comprises a second cartridge valve 502 and a fourth cartridge valve 504, the second cartridge valve 502 and the fourth cartridge valve 504 are two-way cartridge valves, the A2 end of the second cartridge valve 502 is communicated with the pressure end of the power element, the B2 end of the second cartridge valve 502 is communicated with the rod cavity 902, the A4 end of the fourth cartridge valve 504 is communicated with the rodless cavity 901, and the B4 end of the fourth cartridge valve 504 is communicated with the oil tank 11. A first pilot relief valve 801 is arranged between the end B3 of the third cartridge valve 503 and the end A4 of the fourth cartridge valve 504 and the rodless cavity 901, a second pilot relief valve 802 is arranged between the end A1 of the first cartridge valve 501 and the end B2 of the second cartridge valve 502 and the rod cavity 902, and the first pilot relief valve 801 and the second pilot relief valve 802 are both used as safety protection valves of an oil path.
The pilot valve system comprises a first reversing valve 601, a second reversing valve 602, a third reversing valve 603 and a fourth reversing valve 604, wherein the first reversing valve 601, the second reversing valve 602, the third reversing valve 603 and the fourth reversing valve 604 are two-position three-way electromagnetic reversing valves, oil inlets of the first reversing valve 601, the second reversing valve 602, the third reversing valve 603 and the fourth reversing valve 604 are all communicated with a pressure end of a power element, a control oil port of the first reversing valve 601 is communicated with a C1 end of the first cartridge valve 501, an oil return port of the first reversing valve 601 is communicated with an oil tank 11, a control oil port of the second reversing valve 602 is communicated with a C2 end of the second cartridge valve 502, an oil return port of the second reversing valve 602 is communicated with the oil tank 11, a control oil port of the third reversing valve 603 is communicated with a C3 end of the third cartridge valve 503, an oil return port of the third reversing valve 603 is communicated with the oil tank 11, and a control oil port of the fourth reversing valve 604 is communicated with a C4 end of the fourth cartridge valve 504, and an oil return port of the fourth reversing valve 604 is communicated with the oil tank 11.
The oil tank 11 is also communicated with a hydraulic motor 3, the hydraulic motor 3 is in driving connection with a generator 4, the generator 4 is also electrically connected with an energy storage indirect converter 16, the energy storage indirect converter 16 comprises an energy storage device, the energy storage device is a super capacitor, and the energy storage device is also electrically connected with an external power supply device.
The hydraulic control device further comprises a controller and a collecting element which are electrically connected, wherein the collecting element comprises a first pressure sensor 13 for collecting the oil pressure in the rodless cavity 901, a second pressure sensor 14 for collecting the oil pressure in the rod cavity 902 and a displacement sensor 12 for detecting the moving distance of the piston 903, and the controller 15 is electrically connected with an energy storage indirect converter 16.
When the hammer 10 works, firstly, the servo motor 2 drives the constant delivery pump 1, the constant delivery pump 1 extracts hydraulic oil from the oil tank 11, the hydraulic oil with the pressure p and the flow q is output, then the hydraulic oil is conveyed to the A2 end of the second cartridge valve 502 and the A3 end of the third cartridge valve 503, the C2 end of the second cartridge valve 502 and the C3 end of the third cartridge valve 503 generate the pressure p through the four reversing valves, and at the moment, the four reversing valves are all in a closed state.
When the hammer 10 performs a striking action, the power element is firstly communicated with the hydraulic cylinder 9 through the striking stage directional valve group by the pilot valve system, and a specific adjustment mode is to supply power to the first electromagnet 701 of the first reversing valve 601 and the third electromagnet 703 of the third reversing valve 603, so that the first reversing valve 601 and the third reversing valve 603 work in a left position, the C1 end of the first cartridge valve 501 and the C3 end of the third cartridge valve 503 are communicated with the oil tank 11, the first cartridge valve 501 and the third cartridge valve 503 are opened, hydraulic oil flows into the rodless cavity 901 from the A3 end of the third cartridge valve 503 through the B3 end, and then pressure is generated on the piston 903, and the piston 903 is pushed to extend and drive the hammer 10 to move downwards for striking. Meanwhile, hydraulic oil originally located in the rod cavity 902 flows to the oil tank 11 sequentially through the end A1 and the end B1 of the first cartridge valve 501, and in the flowing process, the hydraulic oil firstly enters the hydraulic motor 3 to drive the hydraulic motor 3 to act, then the hydraulic motor 3 drives the generator 4 to generate electricity, and electric energy generated by the generator 4 is stored in the energy storage indirect converter 16. After the striking operation is completed, the first electromagnet 701 and the third electromagnet 703 are deenergized, and the first direction valve 601 and the third direction valve 603 are closed.
When the hammer 10 performs the lifting and hammering operation, the pilot valve system firstly enables the power element to be communicated with the hydraulic cylinder 9 through the direction valve group in the lifting and hammering stage, the specific adjustment mode is to supply power to the second electromagnet 702 of the second reversing valve 602 and the fourth electromagnet 704 of the fourth reversing valve 604, so that the second reversing valve 602 and the fourth reversing valve 604 work in the left position, the C2 end of the second cartridge valve 502 and the C4 end of the fourth cartridge valve 504 are communicated with the oil tank 11, the second cartridge valve 502 and the fourth cartridge valve 504 are opened, hydraulic oil flows into the rod cavity 902 through the A2 end and the B2 end of the second cartridge valve 502, and the piston 903 is pushed to reset into the hydraulic cylinder 9, and further the hammer 10 is driven to reset, so that the lifting and hammering operation is completed. Meanwhile, hydraulic oil originally located in the rodless cavity 901 flows to the oil tank 11 sequentially through the end A4 and the end B4 of the fourth cartridge valve 504, and in the flowing process, the hydraulic oil firstly enters the hydraulic motor 3 to drive the hydraulic motor 3 to act, then the hydraulic motor 3 drives the generator 4 to generate electricity, and electric energy generated by the generator 4 is stored in the energy storage indirect converter 16. After the hammer is lifted, the second electromagnet 702 and the fourth electromagnet 704 are powered off, and the second reversing valve 602 and the fourth reversing valve 604 are closed.
The invention adopts four high-flow cartridge valves and four two-position three-way electromagnetic reversing valves to be matched, the directional valve group in the striking stage and the directional valve group in the beating stage are not interfered with each other, and the switching speed is high. After forging is completed, the hammer head 10 is stopped, and the servo motor 2 and the constant delivery pump 1 are stopped, so that no efficiency loss and no idle operation loss of the operation of the prime mover (mainly the motor) are caused.
As shown in fig. 2, the specific process of hydraulic oil driving the generator 4 to generate electricity through the hydraulic motor 3 is as follows: firstly, the generator 4 generates alternating current, then the alternating current is rectified to obtain direct current, the direct current is filtered and stabilized to output stable direct current, finally, the electric energy is stored in the energy storage device, and the stored electric energy is used for supplying power to the controller and the servo motor 2 to prepare for the next action, so that the energy is recycled, and the energy utilization rate is improved. Because the limitation of the power generation efficiency, the power generation amount hardly completely meets the power consumption requirements of the controller and the servo motor 2, so that external power supply equipment is added, the external power supply equipment continuously charges the energy storage device without directly supplying power to the controller and the servo motor 2, and an additional device for switching between the external power supply equipment and the energy storage device is not needed, so that the complexity of the device is reduced.
The system of the invention has high integration level, can realize modularized design, and greatly reduces pipeline connection, thereby reducing flow loss and greatly eliminating the influence of pipeline dynamics on a hydraulic system. And a fixed displacement pump with low price and high reliability can be selected, so that the requirements on hydraulic oil and filtering are reduced, the abrasion of the pump and the noise of a system are reduced, and the service life and the reliability of the system are improved.
It is further noted that relational terms such as first and second, and the like are used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Moreover, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the phrase "comprising one … …" does not exclude the presence of other like elements in a process, method, article, or apparatus that comprises the element.
The previous description of the disclosed embodiments is provided to enable any person skilled in the art to make or use the present invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the invention. Thus, the present invention is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.
Claims (4)
1. The utility model provides a servo die forging hammer control system of direct-drive formula electricity liquid, includes oil tank (11), power component, control element and the pneumatic cylinder (9) that communicate in proper order and form the closed loop, and wherein pneumatic cylinder (9) are including rodless chamber (901) and have pole chamber (902), are provided with piston (903) in have pole chamber (902), and piston (903) and die forging hammer's tup (10) fixed connection, its characterized in that: the control element comprises a pilot valve system and a direction valve system, wherein the direction valve system comprises a striking stage direction valve group and a lifting and beating stage direction valve group, and the pilot valve system is used for controlling the power element to be communicated with the striking stage direction valve group or the lifting and beating stage direction valve group;
the striking stage direction valve group comprises a first cartridge valve (501) and a third cartridge valve (503), the first cartridge valve (501) and the third cartridge valve (503) are two-way cartridge valves, the A1 end of the first cartridge valve (501) is communicated with the rod cavity (902), the B1 end of the first cartridge valve (501) is communicated with the oil tank (11), the A3 end of the third cartridge valve (503) is communicated with the pressure end of the power element, and the B3 end of the third cartridge valve (503) is communicated with the rodless cavity (901);
the direction valve group in the beating stage comprises a second cartridge valve (502) and a fourth cartridge valve (504), the second cartridge valve (502) and the fourth cartridge valve (504) are two-way cartridge valves, the A2 end of the second cartridge valve (502) is communicated with the pressure end of the power element, the B2 end of the second cartridge valve (502) is communicated with the rod cavity (902), the A4 end of the fourth cartridge valve (504) is communicated with the rodless cavity (901), and the B4 end of the fourth cartridge valve (504) is communicated with the oil tank (11);
the oil tank (11) is also communicated with a hydraulic motor (3), the hydraulic motor (3) is in driving connection with a generator (4), and the generator (4) is also electrically connected with an energy storage indirect converter (16);
the device also comprises a controller and a collecting element which are electrically connected, wherein the collecting element comprises a first pressure sensor (13) for collecting the oil pressure in the rodless cavity (901), a second pressure sensor (14) for collecting the oil pressure in the rod cavity (902) and a displacement sensor (12) for detecting the moving distance of the piston (903), and the controller (15) is electrically connected with the energy storage indirect converter (16);
the pilot valve system comprises a first reversing valve (601), a second reversing valve (602), a third reversing valve (603) and a fourth reversing valve (604), wherein the first reversing valve (601), the second reversing valve (602), the third reversing valve (603) and the fourth reversing valve (604) are two-position three-way electromagnetic reversing valves, oil inlets of the first reversing valve (601), the second reversing valve (602), the third reversing valve (603) and the fourth reversing valve (604) are all communicated with a pressure end of a power element, a control oil port of the first reversing valve (601) is communicated with a C1 end of the first cartridge valve (501), an oil return port of the first reversing valve (601) is communicated with a C2 end of the oil tank (11), an oil return port of the second reversing valve (602) is communicated with the C11 end of the oil tank (502), a control oil port of the third reversing valve (603) is communicated with a C3 end of the third cartridge valve (503), an oil return port of the third reversing valve (603) is communicated with a C11 end of the oil tank (604), and an oil return port of the fourth reversing valve (604) is communicated with a C1 end of the oil tank (11).
2. A direct drive electro-hydraulic servo die hammer control system as claimed in claim 1, wherein: a first pilot overflow valve (801) is arranged between the end B3 of the third cartridge valve (503) and the end A4 of the fourth cartridge valve (504) and the rodless cavity (901), and a second pilot overflow valve (802) is arranged between the end A1 of the first cartridge valve (501) and the end B2 of the second cartridge valve (502) and the rod cavity (902).
3. A direct drive electro-hydraulic servo die hammer control system as claimed in claim 1, wherein: the energy storage indirect converter (16) comprises an energy storage device, and the energy storage device is further electrically connected with an external power supply device.
4. A direct drive electro-hydraulic servo die hammer control system as claimed in claim 1, wherein: the power element comprises a constant delivery pump (1) and a servo motor (2), wherein the oil inlet end of the constant delivery pump (1) is communicated with the oil tank (11), the oil supply port of the constant delivery pump (1) is communicated with the control element, and the servo motor (2) is electrically connected with the energy storage indirect converter (16).
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| CN201710985213.8A CN107642511B (en) | 2017-10-20 | 2017-10-20 | Direct-drive electrohydraulic servo die forging hammer control system |
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| CN201710985213.8A CN107642511B (en) | 2017-10-20 | 2017-10-20 | Direct-drive electrohydraulic servo die forging hammer control system |
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