CN111379753A - Full-hydraulic constant-power closed driving system of toothed roll crusher - Google Patents
Full-hydraulic constant-power closed driving system of toothed roll crusher Download PDFInfo
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- CN111379753A CN111379753A CN201811623530.6A CN201811623530A CN111379753A CN 111379753 A CN111379753 A CN 111379753A CN 201811623530 A CN201811623530 A CN 201811623530A CN 111379753 A CN111379753 A CN 111379753A
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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
- F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
- B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
- B02C4/00—Crushing or disintegrating by roller mills
- B02C4/02—Crushing or disintegrating by roller mills with two or more rollers
- B02C4/08—Crushing or disintegrating by roller mills with two or more rollers with co-operating corrugated or toothed crushing-rollers
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
- B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
- B02C4/00—Crushing or disintegrating by roller mills
- B02C4/28—Details
- B02C4/42—Driving mechanisms; Roller speed control
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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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/041—Removal or measurement of solid or liquid contamination, e.g. filtering
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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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/08—Servomotor systems incorporating electrically operated control means
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- General Engineering & Computer Science (AREA)
- Food Science & Technology (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention belongs to the technical field of a toothed roll crusher, and particularly relates to a full-hydraulic constant-power closed driving system of the toothed roll crusher, which comprises a control module and a hydraulic system, wherein the hydraulic system comprises two groups of main oil ways, two groups of control oil ways and one group of oil supplementing oil way which are of the same structure, the main oil way comprises a bidirectional variable plunger pump, an A, B oil port of the bidirectional variable plunger pump is respectively connected with a C, D oil port of a hydraulic motor, and A, B oil ways of the main oil way are respectively provided with a pressure sensor; the hydraulic system transmits a pressure signal generated by an operating load to the control module through the pressure sensor, the control module controls the servo variable assembly to act on the servo variable oil cylinder to realize the displacement change of the bidirectional variable plunger pump, and the hydraulic system works according to a constant power control program set by the control module. The invention operates under constant power, and the tooth roller can automatically change the crushing speed and the crushing strength according to the crushing load, thereby achieving the purposes of saving energy and improving the production efficiency.
Description
Technical Field
The invention relates to a full-hydraulic constant-power closed driving system of a toothed roll crusher, belonging to the technical field of toothed roll crushers.
Background
The toothed roller crusher is mainly applied to crushing of mine coal and calcium carbonate. The toothed roller crusher is provided with different crushing teeth, and can be used for crushing various materials in the industries of industrial garbage, household garbage, construction garbage and ceramics.
The toothed roller crusher has a double-toothed roller crushing structure and a multi-toothed roller crushing structure. For a double-geared roller crusher, two toothed rollers rotate relatively, crushing teeth arranged on a double shaft rotate in a staggered mode, and materials entering the double-geared roller crusher are crushed. The main machine of the double-tooth roller crusher mainly takes a motor as a power source, the motor is connected to a torque-limiting type hydraulic coupler, the torque-limiting type hydraulic coupler is connected with a gearbox, and the gearbox is connected with a double-tooth roller shaft for rotary crushing. The double-tooth roller is arranged on the frame, and the double shaft is supported by a self-aligning bearing arranged in the frame. When the motor is electrified and started, the double-tooth rollers rotate in the frame in opposite directions, materials enter from the feeding hole and fall on the double-tooth rollers, the materials are crushed through the staggered occlusion of the roller teeth, and the crushed materials fall on the material conveyor below the frame under the self-gravity. The crushed materials are sent to a stock ground through a conveyor and sent to the next working procedure.
At present, a main machine of the double-geared roller crusher is driven by a motor. A control system is composed of a rotating speed sensor, a control module and the like through an external power supply. When materials which are difficult to crush enter the crusher, the sensor sends out signals, and the control module sends out signals to control the motor to automatically stop working after the set program authentication. However, the existing motor-driven toothed roller crushers comprise the following disadvantages:
1. the motor can not frequently rotate forward and backward in the running process of the equipment. When the gear roller type crusher enters materials which are difficult to crush, the materials which are difficult to crush can not be repeatedly crushed through positive and negative rotation, and the cavity can not be cleaned through automatic reverse rotation.
2. The motor cannot switch the crushing speed according to the load. The alternating current motor runs at a constant rotating speed, and the rotating speed cannot be automatically adjusted according to the crushing force.
3. The motor-driven toothed roller crusher has a constant crushing force, and the crushing force cannot be automatically selected according to the difficulty of crushing materials, so that the production efficiency is low and the energy consumption is high.
Disclosure of Invention
According to the defects in the prior art, the technical problems to be solved by the invention are as follows: the full-hydraulic constant-power closed driving system of the toothed roller crusher can automatically change the rotation speed and the crushing strength to crush according to crushing load, and achieves the purposes of saving energy, reducing consumption and improving production efficiency.
The full-hydraulic constant-power closed driving system of the toothed roller crusher comprises a control module and a hydraulic system, wherein the hydraulic system comprises two groups of main oil ways, two groups of control oil ways and one group of oil supplementing oil ways which are identical in structure, the main oil ways comprise bidirectional variable plunger pumps, A, B oil ports of the bidirectional variable plunger pumps are respectively connected with C, D oil ports of a hydraulic motor, and A, B oil ways of the main oil ways are respectively provided with a pressure sensor; the oil supplementing oil way comprises an oil supplementing control pump, an oil inlet of the oil supplementing control pump is connected with the oil tank, an oil outlet of the oil supplementing control pump is connected with an oil inlet of the first one-way valve, and an oil outlet of the first one-way valve is connected with the A, B oil way of the main oil way; the control oil path comprises a two-position four-way electromagnetic valve, an oil inlet of the two-position four-way electromagnetic valve is connected with an oil outlet of the oil supplementing control pump, an oil outlet of the two-position four-way electromagnetic valve is connected with an oil inlet of the servo variable assembly, an oil outlet of the servo variable assembly is connected with an oil tank, a working oil port of the servo variable assembly is respectively connected with a rod cavity and a rodless cavity of the servo variable oil cylinder, a piston rod of the servo variable oil cylinder is connected with a mechanical feedback connecting rod, and the mechanical feedback connecting rod is respectively connected with a valve core of the servo variable assembly and a; the hydraulic system transmits a pressure signal generated by an operating load to the control module through the pressure sensor, the control module controls the servo variable assembly to act on the servo variable oil cylinder to realize the displacement change of the bidirectional variable plunger pump, and the hydraulic system works according to a constant power control program set by the control module.
When the bidirectional variable plunger pump and the oil supplementing control pump are started, no control signal is input, the two-position four-way electromagnetic valve is not powered, the valve position is in the lower position, the servo variable assembly is not powered, the valve position is in the middle position, the inclination angle of a swash plate of the bidirectional variable plunger pump is 0, no discharge capacity exists during idle running, the hydraulic motor does not rotate, and the gear roller does not work.
When a control signal is input, the two-position four-way electromagnetic valve is electrified, the valve position is at the upper position, the control oil path is conducted, the servo variable assembly is electrified, the valve core of the servo variable assembly moves to cause the piston rod of the servo variable oil cylinder to move, and the piston rod of the servo variable oil cylinder controls the mechanical feedback connecting rod to determine the inclination angle of the swash plate of the bidirectional variable plunger pump, so that the displacement and the oil supply direction of the bidirectional variable plunger pump are controlled to change. The change of the swing angle position of the swash plate of the bidirectional variable plunger pump feeds back signals to the servo variable assembly through the mechanical feedback connecting rod, namely the servo variable assembly is controlled by double functions of control signals of the control module and feedback signals of the mechanical feedback connecting rod. The servo variable assembly is composed of two three-position three-way control valve cores and a pair of proportional electromagnets arranged on two sides of the three-position three-way control valve cores, the proportional electromagnets convert input electric signals into thrust to act on the valve cores, the valve cores move to enable pressure oil to enter one side of a piston cavity of the servo variable oil cylinder, the opening degree proportion of the valve cores corresponds to the pressure acting on one side of the servo piston cavity, pistons of the double-acting servo variable oil cylinder drive a swash plate to change in angle under the action of differential pressure on two sides, and therefore stepless change of the pump between positive maximum displacement and negative maximum displacement is achieved.
When the toothed roll crusher crushes hard objects or objects difficult to crush, the torque on the toothed roll is increased, the pressure on the main oil way is increased, the pressure sensor transmits a pressure signal to the control module, the control module sends a control signal to control the valve core stroke of the servo variable assembly in cooperation with a feedback signal of the mechanical feedback connecting rod, the piston rod stroke of the servo variable oil cylinder is changed, the inclined angle of the swash plate of the bidirectional variable plunger pump is reduced, the pump displacement is reduced, the pressure is increased, the speed of the hydraulic motor is reduced, and the output torque is increased.
If the hard objects or the objects which are difficult to crush still cannot be crushed or are stuck, the control module sends out control signals to control the valve core of the servo variable assembly to move, so that the stroke of a piston rod of the servo variable oil cylinder is changed, the inclination angle of a swash plate of the bidirectional variable plunger pump is reversed, the oil supply direction of the pump is reversed, the hydraulic motor is reversed, and the function of automatically reversing and cleaning the cavity is realized.
When the pressure sensor detects that the load is increased, namely the pressure of an oil way is increased, the control module sends out a control signal to control the pump displacement of the bidirectional variable plunger pump to be reduced and the pump pressure to be increased, and when the pressure sensor detects that the load is reduced, namely the pressure of the oil way is reduced, the control module sends out a control signal to control the pump displacement of the bidirectional variable plunger pump to be increased and the pump pressure to be reduced, so that the rotating speed and the crushing torque of a hydraulic motor of the system under constant power are changed along with the load, in the process, the product of the displacement of the bidirectional variable plunger pump and the pump pressure is a certain value (N is P Q/612 η), and the hydraulic system works according to a constant power control program set by the control module.
The full-hydraulic constant-power closed driving system of the toothed roll crusher further comprises a first high-pressure overflow valve, wherein an oil inlet of the first high-pressure overflow valve is connected with an A, B oil way of the main oil way, and an overflow port of the first high-pressure overflow valve is connected with an oil inlet of a first check valve. When the system meets the trouble, first high-pressure overflow valve transships the overflow, and first check valve is opened, and the oil circuit forms promptly: the circulation of the bidirectional variable plunger pump, the first high-pressure overflow valve, the first check valve and the bidirectional variable plunger pump avoids the overhigh pressure of a main oil way and protects the safety of mechanical, hydraulic and electrical systems.
The full-hydraulic constant-power closed driving system of the toothed roller crusher also comprises a second one-way valve and a second high-pressure overflow valve (whether the second one-way valve and the second high-pressure overflow valve are high or not), wherein the second one-way valve and the second high-pressure overflow valve are arranged on the main oil way and close to a hydraulic motor, the oil outlet of the second one-way valve and the oil inlet of the second high-pressure overflow valve are connected with the A, B oil way of the main oil way, and the overflow port of the second high-pressure overflow valve is connected with the oil inlet of the second one-way valve. If the hydraulic pipeline between the hydraulic pump and the hydraulic motor is too long, the second high-pressure overflow valve and the second check valve which are close to the hydraulic motor side in the A, B oil way can play a role in relieving impact.
The full-hydraulic constant-power closed driving system of the toothed roller crusher further comprises a shuttle valve and a back pressure valve, wherein an oil inlet of the shuttle valve is connected with an A, B oil way of a main oil way, an oil outlet of the shuttle valve is connected with an oil inlet of the back pressure valve, and an oil outlet of the back pressure valve is connected with an oil tank. The pressure oil of the oil supply control pump is replaced by hot oil at the low-pressure end of the system through a shuttle valve and a back pressure valve while supplying oil to the low-pressure oil path.
According to the full-hydraulic constant-power closed driving system of the toothed roller crusher, the oil outlet of the shell pipeline of the hydraulic motor is connected with the oil tank, hot oil is taken away, the hydraulic motor is cooled, the motor can be flushed, impurities in oil are taken away, and the service life of the motor is prolonged and protected.
The full-hydraulic constant-power closed driving system of the toothed roll crusher also comprises an oil absorption filter for filtering impurities entering the system, and the oil supplementing control pump is connected with an oil tank through the oil absorption filter.
The full-hydraulic constant-power closed driving system of the toothed roll crusher further comprises an oil supplementing overflow valve, wherein an oil inlet of the oil supplementing overflow valve is connected with an oil outlet of an oil supplementing control pump, and an overflow port of the oil supplementing overflow valve is connected with an oil tank to protect an oil supplementing oil way.
The full-hydraulic constant-power closed driving system of the toothed roll crusher also comprises a gas isolation type energy accumulator, wherein an oil inlet of the gas isolation type energy accumulator is connected with an oil outlet of an oil supplementing control pump, and the gas isolation type energy accumulator plays roles in storing energy, absorbing hydraulic impact and eliminating pulsation.
The full-hydraulic constant-power closed driving system of the toothed roller crusher further comprises a pipeline filter, various impurities in a hydraulic pipeline are filtered, an oil inlet of the pipeline filter is connected with an oil outlet of the two-position four-way electromagnetic valve, and an oil outlet of the pipeline filter is connected with an oil inlet of the servo variable assembly.
The bidirectional variable plunger pump and the oil supplementing control pump are driven by a motor.
Compared with the prior art, the invention has the beneficial effects that:
the full-hydraulic constant-power closed driving system of the toothed roller crusher can replace a motor driving system, a motor runs under constant power, and the toothed roller can automatically change the crushing speed and the crushing strength according to the crushing load, so that the aims of saving energy and improving the production efficiency are fulfilled. When hard objects or objects which are difficult to crush are stuck, the system controls the hydraulic motor to automatically change the positive direction and the negative direction to perform repeated crushing. When the system meets the situation that the materials cannot be crushed, the system can make judgment and alarm and automatically stop, so that the electric, mechanical and hydraulic systems are protected, the crusher is intelligentized, and the purposes of energy conservation and high efficiency are achieved.
Drawings
FIG. 1 is a schematic diagram of a hydraulic system of the present invention;
FIG. 2 is a flow chart of the working principle of the present invention;
FIG. 3 is a front view of the mechanical structure of the present invention;
FIG. 4 is a top view of the mechanical structure of the present invention;
FIG. 5 is a schematic view of the toothed roll turning of the present invention.
In the figure: 1. a two-way variable displacement plunger pump; 2. an oil supply control pump; 3. a motor; 4. a first high-pressure relief valve; 5. a first check valve; 6. a shuttle valve; 7. a hydraulic motor; 8. a back pressure valve; 9. an oil tank; 10. a pressure sensor; 11. an oil absorption filter; 12. a gas-isolated accumulator; 13. an oil-supplementing overflow valve; 14. a line filter; 15. a two-position four-way solenoid valve; 16. a servo variable assembly; 17. a servo variable cylinder; 18. a mechanical feedback link; 19. a second one-way valve; 20. a second high-pressure relief valve;
21. a speed reducer; 22. a base; 23. an end plate; 24. a toothed roller; 25. side plates.
Detailed Description
The invention is further described below with reference to examples:
example (b):
as shown in figures 1-5, the full-hydraulic constant-power closed driving system of the gear roller crusher comprises a control module and a hydraulic system, wherein the hydraulic system comprises two groups of main oil ways, two groups of control oil ways and a group of oil supplementing oil ways which are identical in structure, each main oil way comprises a bidirectional variable plunger pump 1, a A, B oil port of each bidirectional variable plunger pump 1 is connected with a C, D oil port of a hydraulic motor 7, pressure sensors 10 are arranged on A, B oil ways of the main oil ways respectively, each oil supplementing oil way comprises an oil supplementing control pump 2, an oil inlet of each oil supplementing control pump 2 is connected with an oil tank 9, an oil outlet of each oil supplementing control pump 2 is connected with an oil inlet of a first one-way valve 5, an oil outlet of each first one-way valve 5 is connected with a A, B oil way of the main oil ways, each control oil way comprises a two-position four-way electromagnetic valve 15, an oil inlet of each two-position four-way electromagnetic valve 15 is connected with an oil outlet of each oil supplementing control pump 2, an oil outlet of each two-position four-way electromagnetic valve 15 is connected with an oil inlet of a servo variable assembly 16, a working oil inlet of each servo variable assembly 16, working oil port of each servo variable assembly 16 is connected with an oil cylinder 17, a servo variable plunger pump 18 is connected with a servo variable control rod cavity of a servo variable plunger rod control cylinder working control module, a servo variable plunger rod control pump 18, a servo variable control pump 18 and a servo variable control rod control module, a servo variable plunger pump 17, a servo variable control rod control cylinder 19, the servo variable control system is connected with a servo variable plunger rod control module, a servo variable control cylinder 1 and a servo variable plunger pump, the servo variable plunger pump 19, the.
The servo variable assembly 16 is composed of two three-position three-way control valve cores and a pair of proportional electromagnets installed on two sides of the three-position three-way control valve cores, the proportional electromagnets convert input electric signals into thrust to act on the valve cores, the valve cores move to enable pressure oil to enter one side of a piston cavity of the servo variable oil cylinder 17, the opening degree proportion of the valve cores corresponds to the pressure acting on one side of the servo piston cavity, pistons of the double-acting servo variable oil cylinder 17 drive a swash plate to change in angle under the action of differential pressure on two sides, and then stepless change of the pump between positive maximum displacement and negative maximum displacement is achieved.
The embodiment also comprises a first high-pressure overflow valve 4, wherein an oil inlet of the first high-pressure overflow valve 4 is connected with an A, B oil way of the main oil way, and an overflow port of the first high-pressure overflow valve 4 is connected with an oil inlet of the first check valve 5.
The embodiment further comprises a second check valve 19 and a second high-pressure overflow valve 20, the second check valve 19 and the second high-pressure overflow valve 20 are arranged on the main oil path and close to the hydraulic motor 7, an oil outlet of the second check valve 19 and an oil inlet of the second high-pressure overflow valve 20 are connected with an A, B oil path of the main oil path, and an overflow port of the second high-pressure overflow valve 20 is connected with an oil inlet of the second check valve 19.
The embodiment further comprises a shuttle valve 6 and a backpressure valve 8, an oil inlet of the shuttle valve 6 is connected with an A, B oil path of the main oil path, an oil outlet of the shuttle valve 6 is connected with an oil inlet of the backpressure valve 8, and an oil outlet of the backpressure valve 8 is connected with an oil tank 9.
An oil outlet of a shell pipeline of the hydraulic motor 7 is connected with an oil tank 9.
The present embodiment further comprises an oil suction filter 11, and the oil supply control pump 2 is connected with the oil tank 9 through the oil suction filter 11.
The embodiment further comprises an oil supplementing overflow valve 13, an oil inlet of the oil supplementing overflow valve 13 is connected with an oil outlet of the oil supplementing control pump 2, and an overflow port of the oil supplementing overflow valve 13 is connected with the oil tank 9.
The embodiment also comprises a gas isolation type energy accumulator 12, wherein an oil inlet of the gas isolation type energy accumulator 12 is connected with an oil outlet of the oil supplementing control pump 2.
The embodiment further comprises a pipeline filter 14, an oil inlet of the pipeline filter 14 is connected with an oil outlet of the two-position four-way solenoid valve 15, and an oil outlet of the pipeline filter 14 is connected with an oil inlet of the servo variable assembly 16.
The two-way variable plunger pump 1 and the oil supply control pump 2 are driven by a motor 3.
The embodiment also comprises a control module, wherein a pressure sensor 10 arranged in the hydraulic system sends a signal to the control module in the system operation process, and the control module inputs a control signal to the proportional electromagnet according to a set program to realize process control.
The main machine and the hydraulic pump station of the crusher of the embodiment are arranged on the base 22, the end plate 23 and the side plate 25 are arranged around the double-tooth roller 23 on the main machine, the speed reducer 21 is arranged on one side of the input power of the main machine, the hydraulic motor 7 is arranged on the input shaft side of the speed reducer 21, and the hydraulic motor 7 transmits the power to the tooth roller 23 through the speed reducer 21. The hydraulic motor 7 is driven by pressure oil provided by a hydraulic pump station, and the hydraulic pump station mainly comprises an oil tank 9, a motor 3, a bidirectional variable plunger pump 1 and an oil supplementing control pump 2. The side plate 25 is connected with the base 22 into a whole, and the side plate 25 is provided with a tooth comb which is used for cleaning materials bonded on the double-tooth roller 23.
The working principle or process of the invention is as follows:
a. starting procedure
The motor 3 is started, the two-position four-way valve is not powered, the valve position is in the lower position, the servo variable assembly 16 is not powered, the valve position is in the middle position, the inclination angle of the swash plate of the bidirectional variable plunger pump 1 is in the middle position, no displacement exists during idle running, and the hydraulic motor 7 does not rotate.
The control signal is input, the two-position four-way valve is electrified, the valve position is in the upper position, the servo variable assembly 16 is electrified, electromagnets on two sides of the servo variable assembly 16 repel the valve core, the variable pump supplies oil in the forward direction, and the motor is driven to rotate in the forward direction.
b. Constant power process
When the load is increased, the pressure of the main oil way is increased to reach a first set pressure value P1 which is a preset pressure (120 bar-150 bar) at the beginning of a constant power process, the pressure sensor 10 transmits a pressure signal to the control module to send a control signal, the servo variable assembly 16 is electrified, and electromagnets on two sides of the servo variable assembly 16 attract valve cores to enable the inclination angle of the swash plate of the bidirectional variable plunger pump 1 to be gradually changed towards the middle position, namely the inclination angle is reduced, the pump displacement is gradually reduced, the rotating speed of the hydraulic motor 7 is slowed down, and the torque is increased to adapt to the increase of the load.
When the load is reduced, the pressure of the main oil way is reduced, the pressure sensor 10 transmits a pressure signal to the control module, the servo variable assembly 16 is electrified, electromagnets on two sides of the servo variable assembly 16 repel the valve cores, so that the inclination angle of the swash plate of the variable pump is far away from the neutral position to change, namely the inclination angle is increased, the pump displacement is increased, the rotating speed of the hydraulic motor 7 is increased, and the crushing efficiency is improved.
In this process, the product of the displacement volume and the pump pressure of the bidirectional variable displacement plunger pump 1 is a constant value (N — P × Q/612 η), and the bidirectional variable displacement plunger pump 1 operates at a constant power.
c. Process of positive and negative rotation
When the load continues to increase, the pressure of the main oil way increases, and reaches a second set pressure value P2 (between 350bar and 400bar), a reverse program is started to be executed, the pressure sensor 10 transmits a pressure signal to the control module to send a control signal, the servo variable assembly 16 is powered on, electromagnets on two sides of the servo variable assembly 16 attract valve cores, so that the inclination angle of the swash plate of the bidirectional variable plunger pump 1 undergoes a process of reaching a middle position and reversing, the variable pump is changed from forward oil supply to reverse oil supply, and the motor is driven to rotate reversely.
When the pressure of the main oil way does not reach a third set value P3(400bar) and the reverse rotation frequency does not reach n, the hydraulic motor 7 normally executes the forward rotation and the reverse rotation, namely, executes the forward rotation after the reverse rotation and returns to the constant power process, and the reverse rotation frequency (n is a value) runs according to a set program to achieve the aim of repeated crushing. When the number of times of reversal is greater than n, the system judges that the broken objects are difficult to break, the fault still can not be eliminated through repeated breaking, the servo variable assembly 16 attracts the valve core (the main oil way is in forward circulation at the moment), the inclination angle of the variable pump swash plate tends to neutral (0 degrees) change, the pump discharge capacity is reduced to 0, the bidirectional variable plunger pump 1 and the motor 3 run under the no-load state, the equipment is automatically stopped, and meanwhile, the alarm device is started to give an alarm.
d. Overload delay alarm shutdown process
The reverse pressure sensor 10 and the delay time are used for double-action control. In the process of forward and reverse rotation, when the pressure of a main oil way reaches or exceeds a third set value P3(400bar), the forward and reverse rotation of the hydraulic motor 7 is controlled by reverse rotation time, when the reverse rotation time does not reach a set value T (T is a magnitude), the double-tooth roller 23 is in a transient blocking state at the moment, the forward and reverse rotation of the hydraulic motor 7 returns to the process controlled by the reverse rotation pressure, when the reverse rotation time reaches the set value T (T is a magnitude), the double-tooth roller 23 is in a blocking state at the moment, in order to prevent the system from being damaged due to overhigh pressure, the first high-pressure overflow valve 4 and the second high-pressure overflow valve 20 overflow (the set pressure of the first high-pressure overflow valve 4 and the second high-pressure overflow valve 20 is 420bar), the first high-pressure overflow valve 4 and the second high-pressure overflow valve 20 overflow and unload for a certain time T1 (the default value is 3s), the control module sends out a control signal, the inclination angle of the swash plate of the variable displacement pump is changed to be close to the neutral position (0 degrees), the displacement of the pump is reduced to 0, the motor runs in a no-load state, the equipment is automatically stopped, and meanwhile, the alarm device is started to give an alarm.
Claims (10)
1. The utility model provides a full-hydraulic constant power closed actuating system of fluted roller crusher which characterized in that: the hydraulic system comprises two groups of main oil ways, two groups of control oil ways and one group of oil supplementing oil way which are identical in structure, wherein each main oil way comprises a bidirectional variable plunger pump (1), an A, B oil port of the bidirectional variable plunger pump (1) is respectively connected with an C, D oil port of a hydraulic motor (7), and a A, B oil way of each main oil way is respectively provided with a pressure sensor (10); the oil supplementing oil way comprises an oil supplementing control pump (2), an oil inlet of the oil supplementing control pump (2) is connected with an oil tank (9), an oil outlet of the oil supplementing control pump (2) is connected with an oil inlet of the first one-way valve (5), and an oil outlet of the first one-way valve (5) is connected with an A, B oil way of the main oil way; the control oil way comprises a two-position four-way electromagnetic valve (15), an oil inlet of the two-position four-way electromagnetic valve (15) is connected with an oil outlet of the oil supplementing control pump (2), an oil outlet of the two-position four-way electromagnetic valve (15) is connected with an oil inlet of a servo variable assembly (16), an oil outlet of the servo variable assembly (16) is connected with an oil tank (9), working oil ports of the servo variable assembly (16) are respectively connected with a rod cavity and a rodless cavity of a servo variable oil cylinder (17), a piston rod of the servo variable oil cylinder (17) is connected with a mechanical feedback connecting rod (18), and the mechanical feedback connecting rod (18) is respectively connected with a valve core of the servo variable assembly (16) and a swash plate of the bidirectional variable plunger pump (1); the hydraulic system transmits a pressure signal generated by an operation load to the control module through the pressure sensor (10), the control module controls the servo variable assembly (16) to act on the servo variable oil cylinder (17) to change the displacement of the bidirectional variable plunger pump (1), the hydraulic system works according to a constant power control program set by the control module, and the control module can be a PLC control system.
2. The full hydraulic constant power closed drive system of the toothed roll crusher according to claim 1, characterized in that: the oil inlet of the first high-pressure overflow valve (4) is connected with the A, B oil way of the main oil way, and the overflow port of the first high-pressure overflow valve (4) is connected with the oil inlet of the first check valve (5).
3. The full hydraulic constant power closed drive system of the toothed roll crusher according to claim 1, characterized in that: the hydraulic control system is characterized by further comprising a second check valve (19) and a second high-pressure overflow valve (20), wherein the second check valve (19) and the second high-pressure overflow valve (20) are arranged on the main oil path and are close to the hydraulic motor (7), an oil outlet of the second check valve (19) and an oil inlet of the second high-pressure overflow valve (20) are connected with an A, B oil path of the main oil path, and an overflow port of the second high-pressure overflow valve (20) is connected with an oil inlet of the second check valve (19).
4. The full hydraulic constant power closed drive system of the toothed roll crusher according to claim 1, characterized in that: the oil inlet of the shuttle valve (6) is connected with the A, B oil way of the main oil way, the oil outlet of the shuttle valve (6) is connected with the oil inlet of the backpressure valve (8), and the oil outlet of the backpressure valve (8) is connected with the oil tank (9).
5. The full hydraulic constant power closed drive system of the toothed roll crusher according to claim 1, characterized in that: an oil outlet of a shell pipeline of the hydraulic motor (7) is connected with an oil tank (9).
6. The full hydraulic constant power closed drive system of the toothed roll crusher according to claim 1, characterized in that: the oil supply control pump (2) is connected with the oil tank (9) through the oil absorption filter (11).
7. The full hydraulic constant power closed drive system of the toothed roll crusher according to claim 1, characterized in that: the oil-supplementing overflow valve (13) is further included, an oil inlet of the oil-supplementing overflow valve (13) is connected with an oil outlet of the oil-supplementing control pump (2), and an overflow port of the oil-supplementing overflow valve (13) is connected with the oil tank (9).
8. The full hydraulic constant power closed drive system of the toothed roll crusher according to claim 1, characterized in that: the oil-filling control system is characterized by further comprising a gas isolation type energy accumulator (12), wherein an oil inlet of the gas isolation type energy accumulator (12) is connected with an oil outlet of the oil-filling control pump (2).
9. The full hydraulic constant power closed drive system of the toothed roll crusher according to claim 1, characterized in that: the servo variable valve is characterized by further comprising a pipeline filter (14), an oil inlet of the pipeline filter (14) is connected with an oil outlet of the two-position four-way electromagnetic valve (15), and an oil outlet of the pipeline filter (14) is connected with an oil inlet of the servo variable assembly (16).
10. The full hydraulic constant power closed drive system of the toothed roll crusher according to claim 1, characterized in that: the bidirectional variable plunger pump (1) and the oil supplement control pump (2) are driven by a motor (3).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811623530.6A CN111379753A (en) | 2018-12-28 | 2018-12-28 | Full-hydraulic constant-power closed driving system of toothed roll crusher |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811623530.6A CN111379753A (en) | 2018-12-28 | 2018-12-28 | Full-hydraulic constant-power closed driving system of toothed roll crusher |
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| Publication Number | Publication Date |
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| CN111379753A true CN111379753A (en) | 2020-07-07 |
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|---|---|---|---|
| CN201811623530.6A Withdrawn CN111379753A (en) | 2018-12-28 | 2018-12-28 | Full-hydraulic constant-power closed driving system of toothed roll crusher |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112774785A (en) * | 2021-01-15 | 2021-05-11 | 深圳市福浩科技有限公司 | But reducing mechanism of automatically regulated dynamics |
| CN113280011A (en) * | 2021-05-11 | 2021-08-20 | 中冶宝钢技术服务有限公司 | Static pressure driving system of vehicle and control method thereof |
| CN113513507A (en) * | 2021-06-25 | 2021-10-19 | 中航力源液压股份有限公司 | Control device for reducing starting torque of electric pump |
-
2018
- 2018-12-28 CN CN201811623530.6A patent/CN111379753A/en not_active Withdrawn
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112774785A (en) * | 2021-01-15 | 2021-05-11 | 深圳市福浩科技有限公司 | But reducing mechanism of automatically regulated dynamics |
| CN112774785B (en) * | 2021-01-15 | 2022-10-25 | 湖南银粉世家建材科技有限公司 | But reducing mechanism of automatically regulated dynamics |
| CN113280011A (en) * | 2021-05-11 | 2021-08-20 | 中冶宝钢技术服务有限公司 | Static pressure driving system of vehicle and control method thereof |
| CN113280011B (en) * | 2021-05-11 | 2022-10-21 | 中冶宝钢技术服务有限公司 | Hydrostatic drive system for vehicle and control method thereof |
| CN113513507A (en) * | 2021-06-25 | 2021-10-19 | 中航力源液压股份有限公司 | Control device for reducing starting torque of electric pump |
| CN113513507B (en) * | 2021-06-25 | 2023-01-03 | 中航力源液压股份有限公司 | Control device for reducing starting torque of electric pump |
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