CN112324731A - Efficient hydraulic control system and control method thereof - Google Patents
Efficient hydraulic control system and control method thereof Download PDFInfo
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- CN112324731A CN112324731A CN202011121520.XA CN202011121520A CN112324731A CN 112324731 A CN112324731 A CN 112324731A CN 202011121520 A CN202011121520 A CN 202011121520A CN 112324731 A CN112324731 A CN 112324731A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B9/00—Presses specially adapted for particular purposes
- B30B9/32—Presses specially adapted for particular purposes for consolidating scrap metal or for compacting used cars
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/20—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors controlling several interacting or sequentially-operating members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/75—Control of speed of the output member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/78—Control of multiple output members
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a high-efficiency hydraulic control system, which comprises an oil pump, an oil tank, a main cartridge valve, a quick valve, a pressure transmitter, a main cylinder and a side cylinder, wherein the quick valve is provided with a tenth electromagnet switch YV 10; the rear cavity pipeline of the main cylinder is connected to a first liquid inlet and outlet of a quick valve, and a second liquid inlet and outlet pipeline of the quick valve is connected to the front cavity of the side cylinder; the pressure transmitter is arranged on a liquid outlet pipeline of the oil pump; the reason why this hydraulic system is faster than before is that: the return stroke of the main cylinder and the return stroke of the side cylinder are simultaneously powered, so that the power-on and power-off time of electromagnetism and the reflecting time of a valve during independent action are reduced; and secondly, when the main cylinder returns, oil in the rear cavity enters the front cavity of the side cylinder to push the return of the side cylinder, so that the utilization rate of the oil from the oil pump is improved.
Description
Technical Field
The invention relates to the field of waste metal recovery, in particular to a large-scale efficient hydraulic control system for a machine for compressing waste metal and a control method thereof.
Background
At present, most of the packing machines are used in the market, the main cylinder and the side cylinders are independently and sequentially operated, and the operation mode needs more conversion time due to more operations. Therefore, a hydraulic system which is faster and more reasonable is needed to improve the working speed and increase the efficiency.
Disclosure of Invention
Aiming at the problems in the prior art, the invention provides an efficient hydraulic control system and a control method thereof, and aims to reduce the action conversion link, improve the return speed of a main pressure cylinder and a side pressure cylinder and improve the working efficiency.
The technical scheme of the invention is as follows: a high-efficiency hydraulic control system comprises an oil pump, an oil tank, a main cartridge valve, a quick valve provided with a tenth electromagnet switch YV10, a pressure transmitter, a main cylinder and a side cylinder;
the main cartridge valve comprises an overflow valve provided with a first solenoid switch YV1, a second cartridge valve provided with a second solenoid switch YV2, a third cartridge valve provided with a third solenoid switch YV3, a fourth cartridge valve provided with a fourth solenoid switch YV4, a fifth cartridge valve provided with a fifth solenoid switch YV5, a sixth cartridge valve provided with a sixth solenoid switch YV6, a seventh cartridge valve provided with a seventh solenoid switch YV7, an eighth cartridge valve provided with an eighth solenoid switch YV8 and a ninth cartridge valve provided with a ninth solenoid switch YV 9;
a liquid inlet pipeline of the oil pump is connected with a liquid outlet of the oil tank, and a liquid outlet pipeline of the oil pump is divided into five paths and is respectively connected with a first liquid inlet and a first liquid outlet of an overflow valve, a sixth cartridge valve, a seventh cartridge valve, an eighth cartridge valve and a ninth cartridge valve; a liquid inlet pipeline of the oil tank is divided into five paths and is respectively connected with a second liquid inlet and a second liquid outlet of the overflow valve, the second cartridge valve, the third cartridge valve, the fourth cartridge valve and the fifth cartridge valve;
a first liquid inlet and outlet of the second cartridge valve and a second liquid inlet and outlet of the sixth cartridge valve are connected to the rear cavity of the side cylinder through pipelines;
the first liquid inlet and outlet of the third cartridge valve and the second liquid inlet and outlet of the seventh cartridge valve are connected to the front cavity of the side cylinder through pipelines;
the first liquid inlet and outlet of the fourth cartridge valve and the second liquid inlet and outlet of the eighth cartridge valve are connected to the rear cavity of the main cylinder through pipelines;
the first liquid inlet and outlet of the fifth cartridge valve and the second liquid inlet and outlet of the ninth cartridge valve are connected to the front cavity of the main cylinder through pipelines;
the rear cavity pipeline of the main cylinder is connected to a first liquid inlet and outlet of a quick valve, and a second liquid inlet and outlet pipeline of the quick valve is connected to the front cavity of the side cylinder;
the pressure transmitter is arranged on a liquid outlet pipeline of the oil pump.
Further, the master cylinder is provided with a first forward stroke switch SQ1 for controlling the maximum forward position of the master cylinder and a first return stroke switch SQ2 for controlling the maximum return position of the master cylinder.
Further, the side cylinder is provided with a second forward stroke switch SQ3 for controlling the side cylinder forward maximum position and a second return stroke switch SQ4 for controlling the side cylinder return maximum position.
Furthermore, the cylinder diameter of the main cylinder is 1.4-3 times of that of the side cylinder.
The invention also provides a high-efficiency hydraulic control method realized by adopting the high-efficiency hydraulic control system, which comprises the following control modes:
the method is characterized in that the method is in an idle load operation mode, an oil pump outputs oil under the driving of a motor and directly returns to an oil tank through an overflow valve, a system is unloaded, and an oil cylinder does not work;
the second mode is that the side cylinder moves forward, the electromagnetic switches YV1, YV6 and YV7 are electrified to open the overflow valve, the sixth cartridge valve and the seventh cartridge valve, oil output by the oil pump enters a rear cavity of the side cylinder through the sixth cartridge valve, and oil in a front cavity of the side cylinder enters a rear cavity of the side cylinder through the seventh cartridge valve and the sixth cartridge valve to form differential rapid forward; when the system pressure reaches the set pressure of the pressure transmitter, a signal is sent, the electromagnet switch YV7 is powered off to close the seventh cartridge valve, the electromagnet switch YV3 is powered on to open the third cartridge valve, oil output by the oil pump enters the rear cavity of the side cylinder through the sixth cartridge valve, oil in the front cavity of the side cylinder enters the oil tank through the third cartridge valve, and the side cylinder moves forwards at a working speed;
the third mode is that the master cylinder moves forward, the electromagnetic switches YV1, YV8 and YV9 are electrified to open the overflow valve, the eighth cartridge valve and the ninth cartridge valve, oil output by the oil pump enters a rear cavity of the master cylinder through the eighth cartridge valve, and oil in a front cavity of the master cylinder enters a rear cavity of the master cylinder through the ninth cartridge valve and the eighth cartridge valve to form differential rapid forward; when the system pressure reaches the set pressure of the pressure transmitter, a signal is sent, the electromagnet switch YV9 is powered off to close the ninth cartridge valve, the electromagnet switch YV5 is powered on to open the fifth cartridge valve, oil output by the oil pump 1 enters a rear cavity of the main cylinder through the eighth cartridge valve, oil in a front cavity of the main cylinder enters an oil tank through the fifth cartridge valve, and the main cylinder moves forwards at a working speed;
the mode IV includes that the main cylinder and the side cylinder return, the electromagnetic switches YV1, YV2, YV9 and YV10 are electrified to open the overflow valve, the second cartridge valve, the ninth cartridge valve and the quick valve, oil output by the oil pump enters a front cavity of the main cylinder through the ninth cartridge valve, oil in a rear cavity of the main cylinder enters a front cavity of the side cylinder through the quick valve, oil in the rear cavity of the side cylinder enters an oil tank through the second cartridge valve, and the main cylinder and the side cylinder return; because the diameter of the main cylinder is far larger than that of the side cylinder, the side cylinder returns to the place in advance and the second return stroke switch SQ4 sends a signal, the electromagnet switches YV2 and YV10 lose power to close the second cartridge valve and the quick valve, the electromagnet switch YV4 is powered on to open the fourth cartridge valve, oil output by the oil pump enters the front cavity of the main cylinder through the ninth cartridge valve, oil in the rear cavity of the main cylinder enters the oil tank through the fourth cartridge valve, the main cylinder returns continuously, and when the second forward stroke switch SQ3 sends a signal, the main cylinder returns to the place. A packet compaction process is completed.
The invention also provides a packaging machine adopting the high-efficiency hydraulic control system.
The invention has the beneficial effects that: this baling press's hydraulic system is faster than originally, and the reason lies in: the return stroke of the main cylinder and the return stroke of the side cylinder are simultaneously powered, so that the power-on and power-off time of electromagnetism and the reflecting time of a valve during independent action are reduced; and secondly, when the main cylinder returns, oil in the rear cavity enters the front cavity of the side cylinder to push the return of the side cylinder, so that the utilization rate of the oil from the oil pump is improved.
Drawings
Fig. 1 is a schematic structural diagram of a high-efficiency hydraulic control system.
In the figure: the system comprises an oil pump 1, an oil tank 2, a main cartridge valve 3, a quick valve 4, a pressure transmitter 5, a main cylinder 6, a side cylinder 7, an overflow valve 31, a second cartridge valve 32, a third cartridge valve 33, a fourth cartridge valve 34, a fifth cartridge valve 35, a sixth cartridge valve 36, a seventh cartridge valve 37, an eighth cartridge valve 38 and a ninth cartridge valve 39.
Detailed Description
The invention is further described below with reference to the accompanying drawings.
As shown in fig. 1, a high-efficiency hydraulic control system comprises an oil pump 1, an oil tank 2, a main cartridge valve 3, a quick valve 4 provided with a tenth solenoid switch YV10, a pressure transmitter 5, a main cylinder 6 and a side cylinder 7. The master cylinder 6 is provided with a first forward stroke switch SQ1 for controlling the maximum forward position of the master cylinder and a first return stroke switch SQ2 for controlling the maximum return position of the master cylinder. The side cylinder 7 is provided with a second forward stroke switch SQ3 for controlling the maximum forward position of the side cylinder and a second return stroke switch SQ4 for controlling the maximum return position of the side cylinder. The cylinder diameter of the main cylinder 6 can be 1.4-3 times of that of the side cylinder 7.
The main cartridge valve 3 comprises a relief valve 31 having a first solenoid switch YV1, a second cartridge valve 32 having a second solenoid switch YV2, a third cartridge valve 33 having a third solenoid switch YV3, a fourth cartridge valve 34 having a fourth solenoid switch YV4, a fifth cartridge valve 35 having a fifth solenoid switch YV5, a sixth cartridge valve 36 having a sixth solenoid switch YV6, a seventh cartridge valve 37 having a seventh solenoid switch YV7, an eighth cartridge valve 38 having an eighth solenoid switch YV8, and a ninth cartridge valve 39 having a ninth solenoid switch YV 9.
The liquid inlet pipeline of the oil pump 1 is connected with the liquid outlet of the oil tank 2, and the liquid outlet pipeline of the oil pump 1 is divided into five paths and is respectively connected with the first liquid inlets and the first liquid outlets of the overflow valve 31, the sixth cartridge valve 36, the seventh cartridge valve 37, the eighth cartridge valve 38 and the ninth cartridge valve 39. And a liquid inlet pipeline of the oil tank 2 is divided into five paths and is respectively connected with second liquid inlets and outlets of an overflow valve 31, a second cartridge valve 32, a third cartridge valve 33, a fourth cartridge valve 34 and a fifth cartridge valve 35.
The first liquid inlet and outlet of the second cartridge valve 32 and the second liquid inlet and outlet of the sixth cartridge valve 36 are connected to the rear cavity of the side cylinder 7 through pipelines.
The first liquid inlet and outlet of the third cartridge valve 33 and the second liquid inlet and outlet of the seventh cartridge valve 37 are both connected to the front cavity of the side cylinder 7 through pipelines.
The first fluid inlet and outlet of the fourth cartridge valve 34 and the second fluid inlet and outlet of the eighth cartridge valve 38 are both connected to the rear chamber of the master cylinder 6 through pipelines.
The first fluid inlet and outlet of the fifth cartridge valve 35 and the second fluid inlet and outlet of the ninth cartridge valve 39 are both connected to the front cavity of the master cylinder 6 through pipelines.
The rear cavity pipeline of the main cylinder 6 is connected to a first liquid inlet and outlet of the quick valve 4, and a second liquid inlet and outlet pipeline of the quick valve 4 is connected to the front cavity of the side cylinder 7.
And the pressure transmitter 5 is arranged on a liquid outlet pipeline of the oil pump 1.
The hydraulic system of the packer aims to reduce the action conversion link, improve the return speed of the main pressure cylinder and the side pressure cylinder and improve the working efficiency. The working principle of the hydraulic system is as follows:
in the first mode, the oil pump 1 is driven by a motor to output oil and directly return the oil to the oil tank 2 through the overflow valve 31, the system is unloaded, and the oil cylinder does not work.
In the second mode, when the side cylinder 7 moves forward, the electromagnet switches YV1, YV6 and YV7 are electrified to open the overflow valve 31, the sixth cartridge valve 36 and the seventh cartridge valve 37, oil output by the oil pump 1 enters a rear cavity of the side cylinder 7 through the sixth cartridge valve 36, oil in a front cavity of the side cylinder 7 enters the rear cavity of the side cylinder 7 through the seventh cartridge valve 37 and the sixth cartridge valve 36, and differential rapid forward movement is formed; when the system pressure reaches the set pressure of the pressure transmitter 5, a signal is sent, the electromagnet switch YV7 is powered off to close the seventh cartridge valve 37, the electromagnet switch YV3 is powered on to open the third cartridge valve 33, oil output by the oil pump 1 enters the rear cavity of the side cylinder 7 through the sixth cartridge valve 36, oil in the front cavity of the side cylinder 7 enters the oil tank 2 through the third cartridge valve 33, and the side cylinder moves forward at a high speed;
the third mode is that the master cylinder 6 moves forward, the electromagnet switches YV1, YV8 and YV9 are electrified to open the overflow valve 31, the eighth cartridge valve 38 and the ninth cartridge valve 39, oil output by the oil pump 1 enters a rear cavity of the master cylinder 6 through the eighth cartridge valve 38, oil in a front cavity of the master cylinder 6 enters the rear cavity of the master cylinder 6 through the ninth cartridge valve 39 and the eighth cartridge valve 38, and differential rapid forward movement is formed; when the system pressure reaches the set pressure of the pressure transmitter 5, a signal is sent, the electromagnet switch YV9 is powered off to close the ninth cartridge valve 39, the electromagnet switch YV5 is powered on to open the fifth cartridge valve 35, oil output by the oil pump 1 enters the rear cavity of the main cylinder 6 through the eighth cartridge valve 38, oil in the front cavity of the main cylinder 6 enters the oil tank 2 through the fifth cartridge valve 35, and the main cylinder 6 moves forwards at a high speed;
the mode IV includes that the main cylinder and the side cylinder return, the electromagnetic switches YV1, YV2, YV9 and YV10 are electrified to open the overflow valve 31, the second cartridge valve 32, the ninth cartridge valve 39 and the quick valve 4, oil output by the oil pump 1 enters a front cavity of the main cylinder 6 through the ninth cartridge valve 39, oil in a rear cavity of the main cylinder 6 enters a front cavity of the side cylinder 7 through the quick valve 4, oil in a rear cavity of the side cylinder 7 enters the oil tank 2 through the second cartridge valve 32, and the main cylinder and the side cylinder return; because the diameter of the master cylinder is far larger than that of the side cylinder, the side cylinder returns to the place in advance and the second return stroke switch SQ4 sends a signal, the electromagnet switches YV2 and YV10 lose power to close the second cartridge valve 32 and the quick valve 4, the electromagnet switch YV4 is powered on to open the fourth cartridge valve 34, oil output by the oil pump 1 enters the front cavity of the master cylinder 6 through the ninth cartridge valve 39, oil in the rear cavity of the master cylinder 6 enters the oil tank 2 through the fourth cartridge valve 34, the master cylinder returns continuously, and when the second forward stroke switch SQ3 sends a signal, the master cylinder returns to the place. A packet compaction process is completed.
The hydraulic system of the packer is faster than the original reason that: the return stroke of the main cylinder and the return stroke of the side cylinder are simultaneously powered, so that the power-on and power-off time of electromagnetism and the reflecting time of a valve during independent action are reduced; and secondly, when the main cylinder returns, oil in the rear cavity enters the front cavity of the side cylinder to push the return of the side cylinder, so that the utilization rate of the oil from the oil pump is improved.
The foregoing is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, various modifications and decorations can be made without departing from the principle of the present invention, and these modifications and decorations should also be regarded as the protection scope of the present invention.
Claims (6)
1. An efficient hydraulic control system, characterized by: the system comprises an oil pump (1), an oil tank (2), a main cartridge valve (3), a quick valve (4) provided with a tenth electromagnet switch YV10, a pressure transmitter (5), a main cylinder (6) and a side cylinder (7);
the main cartridge valve (3) comprises an overflow valve (31) provided with a first solenoid switch YV1, a second cartridge valve (32) provided with a second solenoid switch YV2, a third cartridge valve (33) provided with a third solenoid switch YV3, a fourth cartridge valve (34) provided with a fourth solenoid switch YV4, a fifth cartridge valve (35) provided with a fifth solenoid switch YV5, a sixth cartridge valve (36) provided with a sixth solenoid switch YV6, a seventh cartridge valve (37) provided with a seventh solenoid switch YV7, an eighth cartridge valve (38) provided with an eighth solenoid switch YV8 and a ninth cartridge valve (39) provided with a ninth solenoid switch YV 9;
a liquid inlet pipeline of the oil pump (1) is connected with a liquid outlet of the oil tank (2), a liquid outlet pipeline of the oil pump (1) is divided into five paths and is respectively connected with first liquid inlets and outlets of an overflow valve (31), a sixth cartridge valve (36), a seventh cartridge valve (37), an eighth cartridge valve (38) and a ninth cartridge valve (39); a liquid inlet pipeline of the oil tank (2) is divided into five paths and is respectively connected with a second liquid inlet and a second liquid outlet of an overflow valve (31), a second cartridge valve (32), a third cartridge valve (33), a fourth cartridge valve (34) and a fifth cartridge valve (35);
a first liquid inlet and outlet of the second cartridge valve (32) and a second liquid inlet and outlet of the sixth cartridge valve (36) are connected to a rear cavity of the side cylinder (7) through pipelines;
a first liquid inlet and outlet of the third cartridge valve (33) and a second liquid inlet and outlet of the seventh cartridge valve (37) are connected to a front cavity of the side cylinder (7) through pipelines;
the first liquid inlet and outlet of the fourth cartridge valve (34) and the second liquid inlet and outlet of the eighth cartridge valve (38) are connected to the rear cavity of the main cylinder (6) through pipelines;
the first liquid inlet and outlet of the fifth cartridge valve (35) and the second liquid inlet and outlet of the ninth cartridge valve (39) are connected to the front cavity of the main cylinder (6) through pipelines;
the rear cavity pipeline of the main cylinder (6) is connected to a first liquid inlet and outlet of the quick valve (4), and a second liquid inlet and outlet pipeline of the quick valve (4) is connected to the front cavity of the side cylinder (7);
and the pressure transmitter (5) is arranged on a liquid outlet pipeline of the oil pump (1).
2. A high efficiency hydraulic control system as set forth in claim 1 wherein: the master cylinder (6) is provided with a first forward stroke switch SQ1 for controlling the maximum forward position of the master cylinder and a first return stroke switch SQ2 for controlling the maximum return position of the master cylinder.
3. A high efficiency hydraulic control system as set forth in claim 1 wherein: the side cylinder (7) is provided with a second forward stroke switch SQ3 for controlling the maximum forward position of the side cylinder and a second return stroke switch SQ4 for controlling the maximum return position of the side cylinder.
4. A high efficiency hydraulic control system as set forth in claim 1 wherein: the cylinder diameter of the main cylinder (6) is 1.4-3 times of that of the side cylinder (7).
5. A high-efficiency hydraulic control method implemented by using the high-efficiency hydraulic control system according to any one of claims 1 to 4, characterized by: the method comprises the following control modes:
the method is characterized in that the method is in an idle load operation mode, an oil pump outputs oil under the driving of a motor and directly returns to an oil tank through an overflow valve, a system is unloaded, and an oil cylinder does not work;
the second mode is that the side cylinder moves forward, the electromagnetic switches YV1, YV6 and YV7 are electrified to open the overflow valve, the sixth cartridge valve and the seventh cartridge valve, oil output by the oil pump enters a rear cavity of the side cylinder through the sixth cartridge valve, and oil in a front cavity of the side cylinder enters a rear cavity of the side cylinder through the seventh cartridge valve and the sixth cartridge valve to form differential rapid forward; when the system pressure reaches the set pressure of the pressure transmitter, a signal is sent, the electromagnet switch YV7 is powered off to close the seventh cartridge valve, the electromagnet switch YV3 is powered on to open the third cartridge valve, oil output by the oil pump enters the rear cavity of the side cylinder through the sixth cartridge valve, oil in the front cavity of the side cylinder enters the oil tank through the third cartridge valve, and the side cylinder moves forwards at a working speed;
the third mode is that the master cylinder moves forward, the electromagnetic switches YV1, YV8 and YV9 are electrified to open the overflow valve, the eighth cartridge valve and the ninth cartridge valve, oil output by the oil pump enters a rear cavity of the master cylinder through the eighth cartridge valve, and oil in a front cavity of the master cylinder enters a rear cavity of the master cylinder through the ninth cartridge valve and the eighth cartridge valve to form differential rapid forward; when the system pressure reaches the set pressure of the pressure transmitter, a signal is sent, the electromagnet switch YV9 is powered off to close the ninth cartridge valve, the electromagnet switch YV5 is powered on to open the fifth cartridge valve, oil output by the oil pump 1 enters a rear cavity of the main cylinder through the eighth cartridge valve, oil in a front cavity of the main cylinder enters an oil tank through the fifth cartridge valve, and the main cylinder moves forwards at a working speed;
the mode IV includes that the main cylinder and the side cylinder return, the electromagnetic switches YV1, YV2, YV9 and YV10 are electrified to open the overflow valve, the second cartridge valve, the ninth cartridge valve and the quick valve, oil output by the oil pump enters a front cavity of the main cylinder through the ninth cartridge valve, oil in a rear cavity of the main cylinder enters a front cavity of the side cylinder through the quick valve, oil in the rear cavity of the side cylinder enters an oil tank through the second cartridge valve, and the main cylinder and the side cylinder return; because the diameter of the main cylinder is far larger than that of the side cylinder, the side cylinder returns to the place in advance and the second return stroke switch SQ4 sends a signal, the electromagnet switches YV2 and YV10 lose power to close the second cartridge valve and the quick valve, the electromagnet switch YV4 is powered on to open the fourth cartridge valve, oil output by the oil pump enters the front cavity of the main cylinder through the ninth cartridge valve, oil in the rear cavity of the main cylinder enters the oil tank through the fourth cartridge valve, the main cylinder returns continuously, and when the second forward stroke switch SQ3 sends a signal, the main cylinder returns to the place.
6. A baler employing the high efficiency hydraulic control system of any one of claims 1 to 4.
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113898621A (en) * | 2021-10-18 | 2022-01-07 | 山东泰丰智能控制股份有限公司 | Stretcher linkage control system |
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| CN109849401A (en) * | 2019-01-24 | 2019-06-07 | 扬力集团股份有限公司 | A kind of energy-saving type hydraulic press and its processing method |
| CN110529443A (en) * | 2019-08-23 | 2019-12-03 | 江苏高德液压机械有限公司 | A kind of hydraulic system of three directions shearing baling press |
| CN110645234A (en) * | 2019-08-23 | 2020-01-03 | 江苏高德液压机械有限公司 | Control method of hydraulic system of three-direction shearing and packaging machine |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113898621A (en) * | 2021-10-18 | 2022-01-07 | 山东泰丰智能控制股份有限公司 | Stretcher linkage control system |
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