CN112623643B - Tensioning system of belt conveyor - Google Patents
Tensioning system of belt conveyor Download PDFInfo
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- CN112623643B CN112623643B CN202110102679.5A CN202110102679A CN112623643B CN 112623643 B CN112623643 B CN 112623643B CN 202110102679 A CN202110102679 A CN 202110102679A CN 112623643 B CN112623643 B CN 112623643B
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
- B65G—TRANSPORT OR STORAGE DEVICES, e.g. CONVEYORS FOR LOADING OR TIPPING, SHOP CONVEYOR SYSTEMS OR PNEUMATIC TUBE CONVEYORS
- B65G23/00—Driving gear for endless conveyors; Belt- or chain-tensioning arrangements
- B65G23/44—Belt or chain tensioning arrangements
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
- B65G—TRANSPORT OR STORAGE DEVICES, e.g. CONVEYORS FOR LOADING OR TIPPING, SHOP CONVEYOR SYSTEMS OR PNEUMATIC TUBE CONVEYORS
- B65G43/00—Control devices, e.g. for safety, warning or fault-correcting
Abstract
The invention discloses a tensioning system of a belt conveyor, and belongs to the technical field of belt conveyors. The constant pressure pump and the emergency pump are isolated by the check valve and then communicated to the two-position three-way valve I, the mechanical three-position four-way valve and the two-position three-way valve III; the two-position three-way valve I is connected with a speed regulating valve, a two-position two-way proportional valve I and a two-position two-way proportional valve II; the speed regulating valve is connected with a hydraulic control two-position two-way valve II, and the hydraulic control two-position two-way valve II is connected to a first oil inlet of the duplex balance valve II; the two-position two-way proportional valve I is connected with a pressure compensator I, and the pressure compensator I is connected with a first two-position three-way valve II and a second two-position three-way valve II respectively. The invention adopts a form of utilizing the proportional valve and the pressure compensator to improve the controllability of the composite action of the winch system and the tensioning oil cylinder; the overflow pressure of the electric proportional overflow valve is controlled in real time, so that the impact of a winch system is reduced in real time, and the stability of the system is improved; the oil is supplemented to the system in real time through the back pressure, and a cavity of the winch motor is prevented from being sucked to be empty under the action of the load.
Description
Technical Field
The invention relates to the technical field of belt conveyors, in particular to a tensioning system of a belt conveyor.
Background
The long-distance belt conveyor has the advantages of high automation degree, small environmental pollution, low transportation cost and the like, and is widely applied to various fields such as coal mining and the like. Because the conveying belt of the conveyor is a viscoelastic body, most of the energy stored or released by the adhesive tape during the starting and stopping processes of the conveyor forms great stress fluctuation in the adhesive tape, and the stress fluctuation can change the tension and the flexibility of the conveying belt. When the tension is reduced to a certain value in the using process, the conveying belt can be slipped and can not work normally. In addition, the elastic deformation and plastic deformation of the adhesive tape can cause the adhesive tape to become loose, thereby causing serious accidents such as material scattering, coal accumulation, adhesive tape damage and the like, and even causing fire when the friction is serious. These accidents not only affect efficient production, but also bring hidden danger to coal mine safety.
Therefore, the tensioning device is indispensable in the belt conveyor, and the function of the tensioning device is mainly to provide enough tension of the conveying belt at the separation point of the driving roller, compensate the change of the elongation of the conveying belt during plastic deformation and transition working conditions, ensure the tension of the minimum tension point of the bearing branch of the conveying belt, and meet the sag condition of the conveying belt, thereby ensuring that the driving roller has enough friction traction force and realizing the normal operation of belt conveying. The requirement on the tensioning system is high due to the long conveying distance and the large conveying capacity of the belt conveyor.
The main working principle of the conveyor tensioning system is as follows: according to the requirement of the conveyor on the tension in the running process, the tension of the belt conveyor in starting, braking and normal running is set according to the calculated and determined parameters of the tension device. In an automatic working state, after a control system receives a signal that the conveyor is allowed to start, the tension of the conveyor belt is adjusted to be a starting tension (generally 1.4-1.5 times of that in normal operation) under the action of a control program, and then the control system sends a signal to start the conveyor; when the speed measuring device detects that the conveyor reaches the normal running speed, the tension of the conveyor belt is automatically adjusted to be the normal running tension; when the control system receives a stop signal, the tension of the conveying belt is automatically adjusted to be the tension at the stop (generally 0.9 time of the tension in normal operation). When the belt conveyor breaks down and needs maintenance and overhaul, the working state of the tensioning device can be adjusted to be a manual working state, the loosening and tensioning of the conveying belt can be manually controlled according to needs, and the tensioning force can be adjusted according to the numerical value displayed by the tension detection device.
The working principle diagram of a hydraulic system of an existing automatic tensioning system is shown in fig. 2, and the working process of the hydraulic system is divided into the following five stages:
2.1 Start-Up phase
When a start button of the tensioning system is pressed by an operator, an electromagnetic valve head Y13 of a two-position two-way valve I13 is electrified to open the system, unloading occurs, a variable pump 11 is started in a no-load mode, the two-position two-way valve I13 recovers to be in a normal Y13 power-off mode, an electric proportional overflow valve 12 adjusts the system pressure to be starting pressure, a three-position four-way valve II 116, Y11a and Y12a of a three-position four-way valve I14 are electrified, Y14 of a two-position three-way valve III 15 is electrified, a winch brake 110 is opened in a brake-releasing mode, and a hydraulic motor 19 rotates forwards and a tensioning rope and charges oil to a tensioning slow oil cylinder 111 at the same time. When the tension reaches the tension required by starting, the brake is closed, the Y14 power-off winch motor stops rotating, the variable pump runs in an idle mode, and meanwhile a signal is sent out to enable the conveyor belt motor to start.
2.2 Start-Up to Normal run phase
When the speed measuring device detects that the conveyor reaches a constant-speed stable operation state, the two-position two-way valve I13 recovers to be in a normal Y13 power-off state, the electric proportional overflow valve sets the system pressure to be in a normal operation pressure, the Y14 of the two-position three-way valve III 15 is powered on, the winch brake is opened in a brake-releasing mode, the Y12b of the three-position four-way valve I14 is powered on, the motor reversely rotates to release the rope, and the tensioning force reaches the tensioning force in a normal operation mode. And (4) closing a winch brake, powering off the electromagnetic valve of the two-position two-way valve II 114, running the hydraulic pump in a no-load mode, and stopping the hydraulic system.
2.3 tension detection and pressure maintaining stage
In the normal operation process of the conveyor, the tension is generally 0.95 times when the tension is lower than a certain value of the tension in normal operation due to leakage of a hydraulic system, reduction of cargo load or looseness of a conveying belt and the like, the two-position two-way valve 13 opens the Y13 to enable the electric system to be unloaded, and the pump is started in an idle load manner; when the Y13 of the two-position two-way valve I13 is powered off, the electric proportional overflow valve sets the system pressure to be the pressure during normal operation, the Y14 of the two-position three-way valve III 15 is powered on, the winch brake is released and opened, the Y12a of the three-position four-way valve I14 is powered on, the motor rotates forwards and tightens the rope, when the tightening force reaches a certain value, the tightening force is generally 1.05 times of the tightening force during normal operation, the winch brake is closed, except that the electromagnetic valves of the two-position two-way valve II 114 are powered off, the hydraulic pump operates in a no-load mode, and the hydraulic system stops working. The above process will be repeated thereafter, keeping the tension substantially constant.
2.4 braking phase
When the conveyor sends a parking signal, the electric proportional overflow valve sets the system pressure to be the parking pressure, the 12b of the three-position four-way valve I14Y is electrified, the winch brake is released and opened, the hydraulic motor reversely rotates to release the rope, and the tension of the conveying belt is adjusted to be the parking tension; the winch brake is closed, the Y13 of the two-position two-way valve I13 is electrified, and the hydraulic pump runs in an idle load mode; all the electromagnetic valves are powered off, and the hydraulic system stops working.
2.5 protection against belt breakage
When the conveyer belt is suddenly broken due to some reason, the tension of the conveyer belt is changed to 0, the electric proportional overflow valve sets the system pressure to be the pressure when the belt is broken, and sends a signal to stop the hydraulic pump, the winch brake is closed, the Y15 of the two-position two-way valve II 114 is electrified to connect the energy accumulator 113 with the oil tank, the tensioning oil cylinder 111 is unloaded, and the phenomenon that the tensioning mechanism moves towards the hydraulic cylinder at a higher speed under the action of the tension of the tensioning oil cylinder to cause impact damage to the tensioning device is avoided, so that the belt breakage protection is realized.
The defects of the prior art are as follows:
1. when in tensioning, the winch motor moves and the tensioning oil cylinder also moves, and because the speed is influenced by load and the load of the motor and the load of the oil cylinder are different, the operation speeds of the motor and the oil cylinder are difficult to control, and the movement position of the oil cylinder is difficult to accurately control;
2. after the tension force is reduced, the tensioning is carried out through the winch, the winch is switched on and off when the tension force is finely adjusted due to the viscoelastic characteristic of the conveying belt, and the brake is required to be switched on first and then the motor is required to act when the winch acts, so that the difficulty in matching the starting of the brake with the action of the motor is high, and the impact phenomenon is easy to occur;
3. the motor is adopted to finely adjust the tension, the micromotion performance of the motor is not easy to control, and the phenomenon of motor suction is possible; the winch cannot be used for emergency when the oil pump or the motor goes wrong.
Disclosure of Invention
In order to solve the technical problem, the invention provides a tensioning system of a belt conveyor.
The invention is realized by the following technical scheme: a belt conveyor tensioning system is provided,
oil outlets of the constant pressure pump and the emergency pump are isolated by the one-way valve and then are respectively communicated to the two-position three-way valve I, the mechanical three-position four-way valve and the two-position three-way valve III;
the two-position three-way valve I is connected with a speed regulating valve, a two-position two-way proportional valve I and a two-position two-way proportional valve II; the speed regulating valve is connected with a hydraulic control two-position two-way valve II, and the hydraulic control two-position two-way valve II is connected to a first oil inlet of the duplex balance valve II; the two-position two-way proportional valve I is connected with a pressure compensator I, and the pressure compensator I is respectively connected with a first two-position three-way valve II and a second two-position three-way valve II; the first two-position three-way valve II is connected to a first oil inlet of the duplex balance valve II, and the second two-position three-way valve II is connected to a second oil inlet of the duplex balance valve II; the duplex balance valve II is connected between the large cavity and the small cavity of the tensioning oil cylinder, and an oil cylinder built-in length measuring sensor is arranged on the tensioning oil cylinder;
the two-position two-way proportional valve II is connected with a pressure compensator II, and the pressure compensator II is connected with an electric control three-position four-way valve I; the electric control three-position four-way valve I and the mechanical three-position four-way valve are connected to a duplex balance valve I, and the duplex balance valve I is connected to two ends of a winch motor of a winch brake; the winch brake is connected with a one-way throttle valve I, and the one-way throttle valve I is connected to the two-position three-way valve III;
a first oil inlet of the duplex balance valve II is connected with a one-way throttle valve II and a hydraulic control two-position two-way valve I, and the other end of the one-way throttle valve II is connected with an energy accumulator; the hydraulic control two-position two-way valve I and the hydraulic control two-position two-way valve II are connected to an X1 port of the constant pressure pump, and the other end of the hydraulic control two-position two-way valve I is connected with an electric control three-position four-way valve II; and the electric control three-position four-way valve II is connected between an X1 port and an X2 port of the constant pressure pump.
It further comprises the following steps: and a first oil inlet of the duplex balance valve II is respectively connected with a pressure sensor, an electric proportional overflow valve II and a two-position two-way valve III, and the electric proportional overflow valve II and the two-position two-way valve III return oil to an oil tank.
An oil outlet of the constant pressure pump is connected with a first one-way valve I; and an oil outlet of the emergency pump is connected with a second one-way valve I.
The hydraulic control two-position two-way valve II is connected to a first oil inlet of the duplex balance valve II through a first one-way valve V; and the second two-position three-way valve II is connected to a first oil inlet of the duplex balance valve II through a second one-way valve V.
And the second two-position three-way valve II is connected with an overflow valve in parallel.
One oil port of the electric control three-position four-way valve I is connected with a first one-way valve II, the first one-way valve II is connected to a first oil inlet of the duplex balance valve I, the other oil port of the electric control three-position four-way valve I is connected with a second one-way valve II, and the second one-way valve II is connected to a second oil inlet of the duplex balance valve I;
one oil port of the mechanical three-position four-way valve is connected to a first oil inlet of the duplex balance valve I, and the other oil port of the mechanical three-position four-way valve is connected to a second oil inlet of the duplex balance valve I;
one end of the electric proportional overflow valve I is connected with a first one-way valve IV and a second one-way valve IV respectively, the first one-way valve IV is connected to a first oil inlet of the duplex balance valve I, and the second one-way valve IV is connected to a second oil inlet of the duplex balance valve I; the other end of the electric proportional overflow valve I is connected with a first check valve III, a second check valve III and an oil tank respectively, the first check valve III is connected to a first oil inlet of the duplex balance valve I, and the second check valve III is connected to a second oil inlet of the duplex balance valve I.
Compared with the prior art, the invention has the beneficial effects that:
1. a constant pressure system is adopted, and the controllability of the composite action of the winch system and the tensioning oil cylinder is improved by using a form of a proportional valve and a pressure compensator;
2. when the winch is started and stopped, according to the load pressure and the pressure impact of the system, the overflow pressure of the electric proportional overflow valve is controlled in real time, the impact is reduced in real time, and the stability of the system is improved;
3. oil is supplemented to the system in real time through back pressure, so that a cavity of a winch motor is prevented from being sucked to be empty under the action of load; when the belt is broken, the energy accumulator is unloaded on one hand; on the other hand, an electric control three-position four-way valve II of the oil pump variable control mechanism is switched to the left side function, so that the displacement of the pump becomes zero.
Drawings
FIG. 1 is a schematic structural diagram of an embodiment of the present invention;
in the figure: 21-a constant pressure pump; 22-emergency pump; 23 a-a first one-way valve I; 23 b-a second one-way valve I; a 24-position three-way valve I; 234-speed regulating valve; 25, a two-position two-way proportional valve I; 26 a pressure compensator I; 27-two-position two-way proportional valve II; 28-pressure compensator ii; 29 a-a first two-position three-way valve II; 29 b-a second two-position three-way valve II; 232-hydraulic control two-position two-way valve II; 210-an overflow valve; 230 a-first one-way valve v; 230 b-second one-way valve v; 222-a duplex balance valve II; 223-a length measuring sensor is arranged in the oil cylinder; 224-tensioning cylinder;
227-a pressure sensor; 228-electric proportional relief valve II; 229-two-position two-way valve iii;
211-an electrically controlled three-position four-way valve I; 212-mechanical three-position four-way valve; 215 a-first non return valve ii; 215 b-a second non return valve ii; 216 a-first check valve iii; 216 b-second check valve iii; 217 electric proportional relief valve I; 218 a-a first one-way valve iv; 218 b-a second one-way valve iv; 219 a duplex balancing valve I; 220-winch motor; 221 a winch brake;
214-two-position three-way valve III; 213-one-way throttle valve I;
233-electric control three-position four-way valve II; 231 a hydraulic control two-position two-way valve I; 226-one-way throttle valve II; 225-an accumulator;
FIG. 2 is a schematic diagram of the hydraulic system of an automatic tensioning system of the prior art;
in the figure: 11-a variable displacement pump; 12-electric proportional relief valve; 13 two-position two-way valves I and 114-two-position two-way valve II; 14 three-position four-way valve I, 116-three-position four-way valve II; 15-two-position three-way valve III; 16-a balancing valve; 17 one-way throttle valve I, 18-one-way throttle valve II; 19-winch motor; 110-a winch brake; 111-tensioning oil cylinder; 112 pressure gauge II, 115-pressure gauge I; 113-an accumulator; 117-pilot operated check valve.
Detailed Description
The following is a specific embodiment of the present invention, which will be further described with reference to the accompanying drawings.
Referring to fig. 1, in the belt conveyor tensioning system, an oil outlet of a constant pressure pump 21 is connected with a first one-way valve I23 a, and an oil outlet of an emergency pump 22 is connected with a second one-way valve I23 b. The first check valve I23 a and the second check valve I23 b are communicated to a two-position three-way valve I24, a mechanical three-position four-way valve 212 and a two-position three-way valve III 214 respectively after being converged.
The two-position three-way valve I24 is connected with the speed regulating valve 234, the two-position two-way proportional valve I25 and the two-position two-way proportional valve II 27;
the speed regulating valve 234 is connected to a hydraulic control two-position two-way valve II 232, and the hydraulic control two-position two-way valve II 232 is connected to a first oil inlet of the duplex balance valve II 222 through a first one-way valve V230 a;
the two-position two-way proportional valve I25 is connected to a pressure compensator I26, and the pressure compensator I26 is connected to a first two-position three-way valve II 29a and a second two-position three-way valve II 29b respectively. The second two-position three-way valve II 29b is connected to a first oil inlet of the duplex balance valve II 222 through a second one-way valve V230 b; the second two-position three-way valve II 29b is connected to a second oil inlet of the duplex balance valve II 222, and the second two-position three-way valve II 29b is connected with an overflow valve 210 in parallel;
the duplex balance valve II 222 is connected between the large cavity and the small cavity of the tensioning oil cylinder 224, and the tensioning oil cylinder 224 is provided with an oil cylinder built-in length measuring sensor 233. And a first oil inlet of the duplex balance valve II 222 is respectively connected with a pressure sensor 227, an electric proportional overflow valve II 228 and a two-position two-way valve III 229, and the electric proportional overflow valve II 228 and the two-position two-way valve III 229 return oil to an oil tank.
The first oil inlet of the duplex balance valve II 222 is connected with a one-way throttle valve II 226 and a hydraulic control two-position two-way valve I231, and the other end of the one-way throttle valve II 226 is connected with an energy accumulator 225. The hydraulic control two-position two-way valve I231 and the hydraulic control two-position two-way valve II 232 are connected to an X1 port of the constant pressure pump 21, and the other end of the hydraulic control two-position two-way valve I231 is connected with an electric control three-position four-way valve II 233. An electrically controlled three-position four-way valve II 233 is connected between the ports X1 and X2 of the constant pressure pump 21.
The two-position two-way proportional valve II 27 is connected with a pressure compensator II 28, and the pressure compensator II 28 is connected with an electric control three-position four-way valve I211. The electric control three-position four-way valve I211 and the mechanical three-position four-way valve 212 are connected with a winch motor 220 of a winch brake 221 through a duplex balance valve I219, the winch brake 221 is connected with a one-way throttle valve I213, the one-way throttle valve I213 is connected with a two-position three-way valve III 214, and the two-position three-way valve III 214 is connected with an oil tank;
specifically, the method comprises the following steps:
an oil port of the electric control three-position four-way valve I211 is connected with a first check valve II 215a, the first check valve II 215a is connected to a first oil inlet of a duplex balance valve I219, the other oil port of the electric control three-position four-way valve I211 is connected with a second check valve II 215b, and the second check valve II 215b is connected to a second oil inlet of the duplex balance valve I219;
one oil port of the mechanical three-position four-way valve 212 is connected to a first oil inlet of the double balance valve I219, and the other oil port of the mechanical three-position four-way valve 212 is connected to a second oil inlet of the double balance valve I219;
one end of the electric proportional relief valve I217 is connected with a first check valve IV 218a and a second check valve IV 218b respectively, the first check valve IV 218a is connected to a first oil inlet of a duplex balance valve I219, and the second check valve IV 218b is connected to a second oil inlet of the duplex balance valve I219. The other end of the electric proportional overflow valve I217 is connected with a first check valve III 216a, a second check valve III 216b and an oil tank respectively, the first check valve III 216a is connected to a first oil inlet of a duplex balance valve I219, and the second check valve III 216b is connected to a second oil inlet of the duplex balance valve I219.
The working principle is as follows:
1 starting phase
After a starting button of the tensioning system is pressed by an operator, Y21a of the electric control three-position four-way valve II 233 is electrified, Y22 of the two-position three-way valve I24 is electrified, and the constant pressure pump 21 is started in an idle load mode. The system pressure is set to be starting pressure by the electric proportional overflow valve I217 and the electric proportional overflow valve II 228, the first two-position three-way valve II 29a, Y23a and Y25 of the two-position three-way valve III 214 are electrified, Y24a of the electric control three-position four-way valve I211 is electrified, Y21b of the electric control three-position four-way valve II 233 is electrified, and simultaneously currents of YP21 and YP22 of the two-position two-way proportional valve I25 and the two-position two-way proportional valve II 27 are slowly increased; the winch brake 221 is released and opened and the winch motor 220 is rotating forward to tighten the rope while charging the tension slack cylinder 224. When the tension reaches the tension required by starting, the brake is closed, the Y25 power-off winch motor stops rotating, the variable pump runs in an idle mode, and meanwhile a signal is sent out to start the conveyor motor.
In the embodiment, a constant pressure system is adopted, and the controllability of the composite action is improved by using the form of a proportional valve and a pressure compensator; in the embodiment, a length measuring sensor is arranged in the tensioning oil cylinder to detect the displacement of the oil cylinder in real time; when the position of the oil cylinder is adjusted, the oil cylinder extends outwards in a differential telescopic mode, namely, when the oil cylinder extends outwards, oil in a small cavity of the telescopic oil cylinder enters a large cavity, and the extending speed is increased; when the position of the oil cylinder is finely adjusted, differential expansion is not carried out, and the micro-motion property of the oil cylinder control is improved;
according to the invention, when the winch is started and stopped, the overflow pressure of the electric proportional overflow valve I217 is controlled in real time according to the load pressure and the pressure impact of the system, so that the impact is reduced in real time, and the stability of the system is improved. After the electric control three-position four-way valve I211 of the winch system is powered off, the duplex balance valve I219 is switched on and off at the same time, a middle position Y-shaped function is adopted, but the oil liquid of the system is prevented from flowing back to an oil tank from a middle position of the electric control three-position four-way valve I211 when emergency use is required, and a high-voltage isolation mode is adopted. In order to prevent a cavity of the winch motor from being sucked empty under the action of load, the designed system can supplement oil for the system in real time through back pressure;
according to the invention, different levels of anti-failure designs are adopted, and when an electric control three-position four-way valve I211 of a winch system fails, a mechanical three-position four-way valve 212 is adopted to control the winch to act; if the constant pressure pump fails, the emergency pump is adopted to provide power for the system, and when the emergency pump is adopted to provide power, the electric control can be carried out in the same mode as the conventional mode, and the action of the winch can also be manually controlled.
2 starting to Normal operation phase
When the speed measuring device detects that the conveyor reaches a constant-speed stable operation state, the two-position three-way valve I24 recovers to be in a normal Y22 power-off state, the electric proportional overflow valve I217 and the electric proportional overflow valve II 228 set the system pressure to be in a normal operation pressure, the Y25 of the two-position three-way valve III 214 is electrified, the winch brake is released and opened, the Y24b of the electric control three-position four-way valve I211 is electrified, the Y21b of the electric control three-position four-way valve II 233 is electrified, and simultaneously the YP21 and YP22 currents of the two-position two-way proportional valve I25 and the two-position two-way proportional valve II 27 are slowly increased; and (3) reversely rotating the motor to loosen the rope, wherein the tension reaches the tension when the winch works normally, the brake of the winch brake is closed, the constant pressure pump 21 runs in a no-load mode, and the hydraulic system stops working.
After the motor is started to be normal in the prior art, the motor is adopted to finely adjust the tension, and the micro-motion performance of the motor is not easy to control. This embodiment adopts the constant pressure system, utilizes the form of proportional valve + pressure compensator, promotes slightly mobile.
3 tension detection and pressure maintaining stage
In the normal operation process of the conveyor, due to the reasons of leakage of a hydraulic system, reduction of cargo load or looseness of a conveying belt, the tension is generally 0.95 times lower than that in the normal operation process, the pressure in an energy accumulator is also reduced, the two-position three-way valve I24 is not electrified, the hydraulic control two-position two-way valve I231 is in a through-flow state under the action of a spring, the hydraulic control two-position two-way valve II 232 is also in the through-flow state, the constant pressure pump starts to work, when the pressure of the energy accumulator reaches a certain value, the hydraulic control two-position two-way valve I231 resets under the action of the spring, the outlet of the constant pressure pump is decompressed, the hydraulic control two-position two-way valve II 232 is also reversed, and the constant pressure pump stops working. The above process will be repeated thereafter, keeping the tension substantially constant. According to the detection of the length measuring sensor arranged in the oil cylinder, if the retraction displacement of the piston rod of the tensioning oil cylinder reaches the limit value, tensioning is carried out through the winch, the action process is already introduced at the starting stage, and the description is omitted.
In the prior art, after the tension force is reduced, the tensioning is carried out through a winch, the winch is switched on and off when the tension force is finely adjusted due to the viscoelastic characteristic of a conveying belt, and the brake is required to be switched on first and then the motor is required to act when the winch acts, so that the difficulty in matching the starting of the brake with the action of the motor is high, and the impact phenomenon is easy to occur;
in the embodiment, the tension is improved by mainly adjusting the pressure of the energy accumulator in the pressure maintaining stage, when the tension is lower than the tension in normal operation, the pressure of the energy accumulator is also reduced, the hydraulic control two-position two-way valve I231 and the hydraulic control two-position two-way valve II 232 are automatically reversed under the action of the spring instead of an electric control mode, the reliability of the system is improved, and the energy accumulator is automatically pressurized. The tensioning force is adjusted by the winch unless the tensioning oil cylinder reaches the limit position and cannot be adjusted, so that the use times of the winch are reduced. The embodiment adopts a constant pressure system, and improves the responsiveness of pressurization and winch action.
4 braking phase
When the conveyor sends a stop signal, the electric proportional overflow valve II 228 sets the system pressure to be the stop pressure, the 22 of the two-position three-way valve I24Y is electrified, the Y21a of the electric control three-position four-way valve II 233 is electrified, and the constant pressure pump 21 is started in an idle load mode. The electric proportional relief valve I217 sets the system pressure to be starting pressure, Y25 of the two-position three-way valve III 214 is electrified, Y24b of the electric control three-position four-way valve I211 is electrified, Y21b of the electric control three-position four-way valve II 233 is electrified, Y22 current of the two-position two-way proportional valve II 27 is slowly increased, a winch brake 221 is released and opened, and the hydraulic motor 220 reversely rotates to release the rope; y23a and Y23b of the first two-position three-way valve II 29a and the second two-position three-way valve II 29b are electrified, YP21 current of the two-position two-way proportional valve I25 is slowly increased, and the tensioning oil cylinder rapidly extends out by using a differential circuit until the tension of the conveying belt is adjusted to be a stopping tensioning force; then the winch brake is closed, and the constant pressure pump 21 runs in no-load; all the electromagnetic valves are powered off, and the hydraulic system stops working.
The prior art only uses winches for unloading to reduce tension. In the embodiment, a differential system is adopted to enable the tensioning oil cylinder to rapidly extend out to reduce the tensioning force, and meanwhile, a winch is adopted to unload to reduce the tensioning force.
5 Belt breakage protection
When the conveying belt is suddenly broken due to some reason, the tension of the conveying belt is changed to 0, the electric proportional overflow valve II 228 adjusts the system pressure to be the pressure when the belt is broken, and sends a signal to stop the constant pressure pump 21, the winch brake is closed, the Y26 of the two-position two-way valve III 229 is electrified, the energy accumulator 225 is connected with the oil tank, and the tensioning oil cylinder 224 is unloaded; meanwhile, the two-position three-way valve I24 is electrified, the Y21a of the electric control three-position four-way valve II 233 is electrified, and the constant pressure pump 21 is unloaded. The tensioning device is prevented from being impacted and damaged by the fact that the tensioning mechanism moves towards the hydraulic cylinder at a high speed under the action of tension of the tensioning cylinder, and accordingly belt breakage protection is achieved.
The embodiment unloads the energy accumulator on one hand; and on the other hand, an electric control three-position four-way valve II 233 for controlling the variable mechanism of the oil pump is switched to the left side function, so that the displacement of the pump becomes zero.
Claims (6)
1. A belt conveyor tensioning system characterized in that:
oil outlets of the constant pressure pump (21) and the emergency pump (22) are isolated by a one-way valve and then are respectively communicated to a two-position three-way valve I (24), a mechanical three-position four-way valve (212) and a two-position three-way valve III (214);
the two-position three-way valve I (24) is connected with a speed regulating valve (234), a two-position two-way proportional valve I (25) and a two-position two-way proportional valve II (27); the speed regulating valve (234) is connected with a hydraulic control two-position two-way valve II (232), and the hydraulic control two-position two-way valve II (232) is connected to a first oil inlet of the duplex balance valve II (222); the two-position two-way proportional valve I (25) is connected with a pressure compensator I (26), and the pressure compensator I (26) is respectively connected with a first two-position three-way valve II (29 a) and a second two-position three-way valve II (29 b); the first two-position three-way valve II (29 a) is connected to a first oil inlet of the duplex balance valve II (222), and the second two-position three-way valve II (29 b) is connected to a second oil inlet of the duplex balance valve II (222); the duplex balance valve II (222) is connected between the large cavity and the small cavity of the tensioning oil cylinder (224), and an oil cylinder built-in length measuring sensor is mounted on the tensioning oil cylinder (224);
the two-position two-way proportional valve II (27) is connected with a pressure compensator II (28), and the pressure compensator II (28) is connected with an electric control three-position four-way valve I (211); the electric control three-position four-way valve I (211) and the mechanical three-position four-way valve (212) are connected to a duplex balance valve I (219), and the duplex balance valve I (219) is connected to two ends of a winch motor (220) of a winch brake (221); the winch brake (221) is connected with a one-way throttle valve I (213), and the one-way throttle valve I (213) is connected to the two-position three-way valve III (214);
a first oil inlet of the duplex balance valve II (222) is connected with a one-way throttle valve II (226) and a hydraulic control two-position two-way valve I (231), and the other end of the one-way throttle valve II (226) is connected with an energy accumulator (225); the hydraulic control two-position two-way valve I (231) and the hydraulic control two-position two-way valve II (232) are connected to an X1 port of the constant pressure pump (21), and the other end of the hydraulic control two-position two-way valve I (231) is connected with an electric control three-position four-way valve II (233); and the electric control three-position four-way valve II (233) is connected between an X1 port and an X2 port of the constant pressure pump (21).
2. A belt conveyor tensioning system as claimed in claim 1, wherein: and a first oil inlet of the duplex balance valve II (222) is respectively connected with a pressure sensor (227), an electric proportional overflow valve II (228) and a two-position two-way valve III (229), and the electric proportional overflow valve II (228) and the two-position two-way valve III (229) return oil to an oil tank.
3. A belt conveyor tensioning system as claimed in claim 1, wherein: an oil outlet of the constant pressure pump (21) is connected with a first one-way valve I (23 a); an oil outlet of the emergency pump (22) is connected with a second one-way valve I (23 b).
4. A belt conveyor tensioning system as claimed in claim 1, wherein: the hydraulic control two-position two-way valve II (232) is connected to a first oil inlet of the duplex balance valve II (222) through a first one-way valve V (230 a); the second two-position three-way valve II (29 b) is connected to a first oil inlet of the duplex balance valve II (222) through a second one-way valve V (230 b).
5. A belt conveyor tensioning system as claimed in claim 1, wherein: and the second two-position three-way valve II (29 b) is connected with an overflow valve (210) in parallel.
6. A belt conveyor tensioning system as claimed in claim 1, wherein: an oil port of the electric control three-position four-way valve I (211) is connected with a first check valve II (215 a), the first check valve II (215 a) is connected to a first oil inlet of the duplex balance valve I (219), the other oil port of the electric control three-position four-way valve I (211) is connected with a second check valve II (215 b), and the second check valve II (215 b) is connected to a second oil inlet of the duplex balance valve I (219);
an oil port of the mechanical three-position four-way valve (212) is connected to a first oil inlet of the duplex balance valve I (219), and the other oil port of the mechanical three-position four-way valve (212) is connected to a second oil inlet of the duplex balance valve I (219);
one end of the electric proportional overflow valve I (217) is connected with a first check valve IV (218 a) and a second check valve IV (218 b) respectively, the first check valve IV (218 a) is connected to a first oil inlet of the duplex balance valve I (219), and the second check valve IV (218 b) is connected to a second oil inlet of the duplex balance valve I (219); the other end of the electric proportional overflow valve I (217) is connected with a first check valve III (216 a), a second check valve III (216 b) and an oil tank respectively, the first check valve III (216 a) is connected to a first oil inlet of a duplex balance valve I (219), and the second check valve III (216 b) is connected to a second oil inlet of the duplex balance valve I (219).
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| CN202110102679.5A CN112623643B (en) | 2021-01-26 | 2021-01-26 | Tensioning system of belt conveyor |
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| CN202110102679.5A CN112623643B (en) | 2021-01-26 | 2021-01-26 | Tensioning system of belt conveyor |
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